A SUBSTITUTE DIESEL ENGINE FUEL COMPOSITION, A DEVICE FOR DETACHING A COMPRESSION IGNITION ENGINE AN

专利摘要:
surrogate diesel engine fuel composition, process for starting a compression ignition engine and power generation system The present invention relates to diesel engine fuel composition comprising methanol at a level of at least 20% by weight of fuel; water at a level at least 20% by weight of the fuel; a water to methanol ratio of 20:80 to 80:20; a total amount of water and methanol of at least 60% by weight of the fuel composition, and one or more additives, in a total amount of at least 0.1% by weight of the fuel, wherein the sodium chloride level, if present as an additive, it is between 0 to 0.5% by weight of the fuel, and the flavoring level, if present as an additive, is between 0 and 1.5% of the composition, is provided. Also provided is a process for starting a compression ignition engine using a fuel comprising methanol and water, including inlet air preheating, and associated systems and uses of the fuel composition.
公开号:BR112013013034B1
申请号:R112013013034-2
申请日:2011-11-25
公开日:2019-06-18
发明作者:Greg Morris；Michael John Brear；Ronald Andrew Slocombe
申请人:Gane Energy & Resources Pty Ltd；
IPC主号:

专利说明:

Invention Patent Descriptive Report for SUBSTITUTE DIESEL ENGINE FUEL COMPOSITION, PROCESS FOR STARTING A COMPRESSION IGNITION ENGINE AND ENERGY GENERATION SYSTEM.
[001] The present invention relates to a new fuel composition and process for starting a type of compression ignition of an internal combustion engine.
[002] The present patent application claims priority for Australian patent applications AU2010905226 and AU2010905225. This patent application is also related to an international patent application entitled "Fuel and process for starting a compression ignition engine" filed by the same Claimant on this day with a common priority claim. The related international patent application report is hereby incorporated by reference.
BACKGROUND OF THE INVENTION [003] The search for fuel alternatives to conventional fossil fuels is driven primarily by the need for a 'clean' emissions fuel coupled with low production costs and wide availability. Much attention is paid to the environmental impact of fuel emissions. Research for alternative fuels focuses on fuels that will reduce the amount of particulate matter and oxides produced by fuel combustion as well as fuels that will reduce emissions of unburned fuel and CO2 and other combustion products. [004] The commitment to environmentally friendly fuel compositions for transportation applications has focused on ethanol. Biomaterials such as organic vegetable substance can be converted into ethanol, and the ethanol produced by such processes has been used
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2/106 as a partial replacement of fuels for spark ignition engines. Although this reduces confidence in non-renewable resources for fuels, the environmental results that arise from using these fuels in engines have not been substantially improved in a general sense, with cleaner combustion being offset by the continued use of such fuels in ignition engines at lower efficiency spark, and negative environmental impact associated with the use of energy, farmland, fertilizers and irrigation water to create fuel.
[005] Other fuel alternatives for complete or partial replacement of traditional fuels have not become widely used.
[006] A major disadvantage with the complete replacement of traditional fuels, and in particular fuels for compression ignition engines (diesel fuels), with a renewable replacement fuel, concerns the perceived problems associated with the low cetane number such fuels. Such fuels have problems achieving ignition in the manner required for efficient engine operation.
[007] Applicants present also recognized that in some locations or remote environments, water is a scarce resource, and in such locations there may be a demand for power generation (such as through diesel engine electricity generation) coupled with capture water by-product for reuse in the local community. In addition, moving energy en masse through the liquid pipeline is a long-lasting and cost-effective technique for moving large amounts of energy over long distances with minimal visual impact compared to overhead transmission lines. [008] Applicants present also recognized a need in some locations for the heat generated in such
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3/106 industrial processes are captured and reused in the local community. In some circumstances, this need is coupled with the need for capturing water for reuse, mentioned above.
[009] In summary, there is a continuing need for alternative fuels for use in internal combustion engines. Fuels that can reduce emissions are of interest, particularly where the improved emission profile is obtained without a major adverse impact on fuel efficiency and / or engine performance. There is also a need for methods of starting compression ignition engines that allow such engines to be operated in place of diesel fuel not traditionally containing components believed to be suitable for use in such applications. In addition, there is a need for diesel engine fuels and engine operating methods that are suitable for use in remote locations, or in environmentally sensitive environments (such as in high latitude marine environments particularly in port areas in terms of emissions) or other areas such as remote dry but cold interior areas that can make maximum use of all by-products of engine operation, including, for example, heat and water by-products. These objectives are preferably dealt with at the lowest possible penalty for fuel efficiency and engine performance.
SUMMARY OF THE INVENTION [0010] In accordance with the present invention, a diesel engine fuel composition is provided comprising:
- methanol at a level of at least 20% by weight of the fuel;
- water at least 20% by weight of the fuel;
- a water to methanol ratio of between 20:80 to 80:20;
- a total amount of water and methanol of at least
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4/106
60% by weight of the fuel composition, and
- one or more additives, in a total amount of at least 0.1% by weight of the fuel, where the level of sodium chloride, if present as an additive, is between 0 to 0.5% by weight of the fuel, and the level of flavoring, if present as an additive, is between 0 to 1.5% of the composition.
[0011] In accordance with the present invention, a process is also provided for starting a compression ignition engine using a fuel comprising methanol and water, including: [0012] preheating an intake air stream, introducing the preheated air in an engine combustion chamber and compress the preheated air; and [0013] introduce the fuel into the combustion chamber and ignite the fuel / air mixture to start the engine.
[0014] The invention can result in simplification and a lower fuel manufacturing cost and reduced environmental impact by eliminating the need for production of high purity components and by-product components, by accepting a mixture of such components in a fuel according to with the methods described here. Environmental cost and benefit can also arise from using fuel in cold climates, since the fuel freezing point can easily satisfy any low temperature environment likely to be encountered.
[0015] The exhaust resulting from the combustion of the fuel may contain low impurities, making it ideal for subsequent processing. As an example, CO2 can be converted back to methanol to directly reduce greenhouse gas CO2 or high purity CO2 can be used for organic growth such as algae for multiple end uses including methanol making, using energy sources that can include renewable sources, including solar.
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5/106 [0016] According to one modality, the additive comprises ether, at a level of up to 20% by weight of the fuel. The ether can be dimethyl ether.
[0017] In some modalities, the water generated during the combustion of the fuel can be recovered, which is a main advantage for remote areas where water is scarce. In other circumstances, the heat generated by operating the diesel engine can be used for heating requirements in the local area. Some modalities as described below consequently provide systems for power generation through the operation of a diesel engine that uses the water and / or heat produced from the engine in an appropriate manner.
[0018] According to the present invention, a power generation system is also provided comprising:
[0019] start a compression ignition engine using a methanol-water fuel to generate power;
[0020] preheat an inlet air stream of the compression ignition engine, and / or fumigate the inlet air stream with an ignition intensifier;
[0021] treat the engine's exhaust gas to recover the exhaust heat and / or water from the engine, and redirect the heat and / or water to another use.
[0022] In some modalities, heat and / or water can be recycled back to the motor for reuse. Alternatively or in addition, heat and / or water can be redirected locally for use elsewhere. In one example, heat can be supplied through a hot water duct to a nearby community to provide the community with energy in the form of heat, for example to heat domestic or commercial properties. The engine in this example could be used to generate electricity for the community,
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6/106 which can be especially beneficial to remote communities. [0023] In other modalities, the system can be adapted to start vehicles, including rail and marine vehicles. In these applications, the exhaust is treated to remove particulates, and recover heat and water for reuse in the engine and for other use as required in the rail and marine vehicle.
[0024] In accordance with the present invention, there is further provided a method of transporting a two-part pre-fuel composition comprising methanol and ether, including transporting the pre-fuel from a first location to a second remote location from the first location, and separating the ether from the methanol to yield a first part of fuel comprising methanol, and a second part of fuel comprising ether.
[0025] According to the present invention, there is further provided a pre-fuel composition comprising methanol and up to 10% by weight of an ether.
[0026] In accordance with the present invention, the use of the diesel fuel composition described above in the process or power generation system described above is further provided. BRIEF DESCRIPTION OF THE DRAWINGS [0027] The modalities of the present invention will now be described by way of example with reference to the accompanying drawings, in which: [0028] Figure 1 is a flow chart illustrating a process for starting an ignition ignition engine compression according to an embodiment of the present invention;
[0029] Figure 2 is a graph of the% by weight of dimethyl ether (DME), as an ignition intensifier, to be fumigated in an engine (compared to the weight of the fuel), represented in graph versus the temperature change of the mixture of fuel / fumigant / air
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7/106 compressed, for three fuel compositions (100% methanol, 70% methanol: 30% water and 40% methanol: 60% water). The diagram refers to a method that can be used in defense of the ignition intensification techniques described below;
[0030] Figure 3A is a flow chart illustrating a process for starting a compression ignition engine and for treating engine exhaust, with residual heat used as a separate heating source through a hot water duct;
[0031] Figure 3B is a flow chart similar to Figure 3A, but excluding the step of fumigating the engine intake air;
[0032] Figure 4A is a more detailed view in the flowchart of Figures 3A and 3B of the exhaust treatment;
[0033] Figure 4B is a view similar to Figure 4A, but without a final exhaust air exchange condenser;
[0034] Figure 5A is a flow chart that illustrates a process for starting a compression ignition engine to drive a rail vehicle and treat the engine exhaust;
[0035] Figure 5B is a flow chart similar to Figure 5A, but excluding the step of fumigating the engine intake air;
[0036] Figure 6A is a flow chart illustrating a process for starting a compression ignition engine to drive a marine vehicle and treat the engine's exhaust;
[0037] Figure 6B is a flow chart similar to Figure 6A, but excluding the step of fumigating the engine intake air;
[0038] Figure 7 is a graph illustrating the Thermal Brake Efficiency of a compression ignition engine with DME fumigation using fuels containing varying amounts of water and amounts of methanol, DME and DEE in the liquid phase;
[0039] Figure 8 is a graph that illustrates the thermal efficiency of a compression ignition engine using fuels
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8/106 containing varying amounts of ether as an ignition enhancer, and using DME as a fumigant;
[0040] Figure 9 is a graph that illustrates the NO exhaust outlet of a compression ignition engine using fuels containing varying amounts of water and using DME as a fumigant;
[0041] Figure 10 is a schematic diagram of the process and instrumentation of the testing facility used to obtain the results of Example 1;
[0042] Figure 11 is a graph that illustrates the reduction in NO exhaust output from a compression ignition engine by increasing the amount of water in the methanol-water fuel. DETAILED DESCRIPTION [0043] The fuel and process described here are suitable for starting compression ignition (CI) engines. In particular, the fuel and process are very suitable, but not limited, for CI engines operating at low speeds such as 1000 rpm or less. The engine speed can be even 800 rpm or less, for example 500 rpm or less. The engine speed can be even 300 rpm or less, for example 150 rpm or less.
[0044] The fuel is therefore suitable for larger diesel engines such as those operating on ships and trains, and in plants generating electric power. The slower speeds on the larger CI engines allow sufficient time for combustion of the selected fuel composition to be completed and for a sufficiently high percentage of the fuel to be vaporized to achieve efficient operation.
[0045] However, it is understood that the fuel and process described here could operate with smaller CI engines operating in
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9/106 higher speeds. In fact, preliminary test work was conducted on a small CI engine operating at 2000 rpm and 1000 rpm, demonstrating that the fuel is also capable of starting such higher speed engines. In some circumstances, adjustments can help fuel and process use in smaller CI engines (higher rpm), and some of these are elaborated below. FUEL COMPOSITION [0046] The fuel composition for the process comprises methanol and water. Fuel is a compression ignition engine fuel that is a diesel engine fuel.
[0047] So far, methanol has not found commercial application in compression ignition engines. The disadvantages with using methanol as a pure or mixed engine fuel are evidenced by its low cetane number which is in the range of 3 to 5. This low cetane number makes methanol difficult to burn in an engine of CI. Mixing water with methanol still reduces the fuel's cetane number making combustion of the methanol / water mixture fuel even more difficult, and therefore it would have been considered counterintuitive to combine water with methanol for use in CI engines. The effect of water following fuel injection is to cool down as the water heats and evaporates, further decreasing the effective cetane.
[0048] However, it has been found that a methanol-water fuel combination can be used in a compression ignition engine in an efficient manner and with cleaner exhaust emissions, as long as the intake air stream introduced into the exhaust chamber. combustion engine is sufficiently preheated. Other factors elaborated below also contribute to maximize the effective operation of a CI engine with this fuel. As a secondary measure, the intake air flow can be
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10/106 additionally fumigated with a fumigant comprising an ignition intensifier.
[0049] The fuel can be a homogeneous fuel, or a single-phase fuel. The fuel is typically not an emulsion fuel comprising separate organic and aqueous phases emulsified together. The fuel can therefore be emulsifier-free. The accommodation of additive components in the fuel is aided by the dual solvency properties of methanol and water that will allow the dissolution of a wider range of materials over the various water ratios: methanol that can be used.
[0050] Surprisingly, it has been discovered that a particular new fuel composition based on methanol and a relatively high water level can be used as the fuel for compression ignition engines. The fuel can be referred to as diesel fuel. Although some fuel compositions based on methanol and water have been previously described, fuels of this type containing high water levels have not been shown to be able to operate a compression ignition engine. Specifically, methanol fuels with a water component have only been described for use as a heating or cooking fuel where the fuel is burned to generate heat. The principles that apply to diesel engine fuels are very different, since the fuel has to ignite under compression in the compression ignition engine. Very little, if any, can be added to the references regarding the use of methanol and other components in cooking / heating fuels. However, the techniques described here allow the new fuels described here to operate a compression ignition engine.
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11/106 [0051] A new diesel fuel composition comprises:
- methanol at a level of at least 20% by weight of the fuel;
- water at least 20% by weight of the fuel;
- a water to methanol ratio of between 20:80 to 80:20;
- a total amount of water and methanol of at least 60% by weight of the fuel composition, such as at least 70%, at least 80% or at least 85% by weight of the fuel composition, and
- one or more additives, in a total amount of at least 0.1% by weight of the fuel, where the level of sodium chloride, if present as an additive, is between 0 to 0.1% by weight of the fuel, and the level of flavoring, if present as an additive, is between 0 to 1.5% of the composition.
[0052] According to one modality, the additive comprises ether, at a level of up to 20% by weight of the fuel. The ether can be dimethyl ether or diethyl ether.
[0053] The water level can be above 20% by weight of the fuel composition in some modalities. The minimum water level for some modalities is described below. For example, the minimum water level can be greater than 25%, greater than 30%, greater than 35%, greater than 40%, greater than 45%, greater than 50%, greater than 55%, greater than 60%, greater than 65% or even greater than 70% by weight of the fuel.
[0054] Such methanol-water diesel fuel compositions of high water content have not so far been established to be able to operate a compression ignition engine. However, these high water content methanol-water fuel compositions described here can operate a compression ignition engine,
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12/106 particularly when the engine is operated according to the process described here. This may involve preheating the air inlet, or fumigating the intake air with a fumigant.
[0055] All quantities referred to in this document are by weight, unless otherwise specified. Where a percentage amount of a component in the main fuel composition is described, this is a reference to the percentage of that component by weight of the fuel composition. When a fumigant is used, it is not considered to be part of the fuel composition itself, so the fuel composition in this context is read as excluding the fumigant.
[0056] Although this specific new diesel fuel composition forms an aspect of the present invention, and can be used in operating the process of the present invention, methanol-water fuels containing lower water levels can also be used in the process. In the following, the characteristics of the more general methanol-water fuels are described. It is noted that the characteristics of these fuels may be present in the new diesel fuels claimed in this specification.
[0057] In general, the relative amount of water to methanol in the fuel composition can be in the range of 0.2: 99.8 to 80:20 by weight. According to some modalities, the minimum water level (with respect to methanol) is 1:99, as well as a minimum ratio of 2:98, 3:97, 5:95, 7:93, 10:90, 15: 95, 19:81; 21:79. The upper limit of water (with respect to methanol) in the composition according to some modalities is 80:20, such as 75:25, 70:30, 60:40, 50:50 or 40:60. The relative amount of water in the composition can be considered to be in the “low to medium water” level range, or a “medium to high water” level range. The “low to medium water” range covers the range of any of the minimum levels indicated
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13/106 above for a maximum of 18:82, 20:80, 25:75, 30:70, 40:60, 50:50 or 60:40. The “medium to high water” range covers the range of 20:80, 21:79, 25:75, 30:70, 40:60, 50:50, 56:44 or 60:40 to a maximum one of the upper limits indicated above. A low / medium water level range is 2:98 to 50:50, and a typical medium / high water level range is 50:50 to 80:20. A typical low water level range is 5:95 to 35:65. A typical mid-range water range is 35:65 to 55:45. A typical high water level range is 55:45 to 80:20. The new high water content diesel fuel of the present invention can contain the relative amounts of water and methanol above, as long as the fuel contains the previously described fuel characteristics (such as a minimum water content of 20%).
[0058] Considered in terms of the percentage of water in the entire (main) fuel composition by weight, the relative amount of water in the main fuel composition can be a minimum of at least 0.2%, at least 0.1%, at least 1%, at least 2%, at least 3%, at least 4%, at least 5%, at least 6%, at least 7%, at least 8%, at least 9%, at least 10%, at least 11%, at least 12%, at least 13%, at least 14%, at least 15%, at least 16%, at least 17%, at least 18%, or at least 19%, at least 20% at least 22% by weight, at least 25%, at least 30%, at least 35%, at least 40%, at least 45%, at least 50%, at least 55%, at least 60%, at least 65% or at least 70% water by weight of the fuel composition. As the weight of water in the main fuel composition increases, it is increasingly surprising that the fumigation of the intake air with a fumigant overcomes the water penalty in the fuel in terms of combustion, with smooth operation in terms of VOC from IMEP and producing power useful. The amount
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14/106 maximum water in the fuel composition can be 68%, 60%, 55%, 50%, 40%, 35%, 32%, 30%, 25%, 23%, 20%, 15% or 10% in weight. Any of the minimum levels can be combined with a maximum level without limitation, unless the minimum level is below the maximum water level.
[0059] Based on the test results reported in the Examples, for a desirable brake thermal efficiency (BTE), the amount of water in the fuel composition in some embodiments is between 0.2% and 32% by weight. The optimum zone for a peak in Thermal Brake Efficiency for a compression ignition engine methanol-water fuel is between 12% and 23% of water in the main fuel composition, by weight. The range can be incrementally narrowed from the widest to the narrowest of these two ranges. In some embodiments, this is combined with an amount of ignition intensifier in the fuel composition that is not more than 15% by weight of the main fuel composition. Details of ignition intensifiers are set out below.
[0060] Based on other test results reported in the Examples, for a maximum reduction in NOx emissions, the amount of water in the fuel composition in some modalities is between 22% and 68% by weight. The optimum zone for a maximum reduction in NOx emissions is between 30% and 60% of water by weight of the main fuel composition. The range can be incrementally narrowed from the widest to the narrowest of these two ranges. Since NO is the main component of NOx emissions, reference can be made to NO emissions as the largest proportion, or indicative, of the overall extent of NOx emissions.
[0061] In some embodiments, for a desirable balance of fuel and emissions properties, the fuel composition comprises between 5% and 40% of water by weight of the composition of
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15/106 main fuel, such as between 5% and 25% water, between 5% and 22% water. These levels are based on the combination of the test results reported in the Examples.
[0062] In general fuels for use in the process described here, the amount of methanol in the total fuel composition is preferably at least 20% by weight of the fuel composition. According to some modalities (such as the new methanol-water diesel fuel composition with high water content), the amount of methanol in the fuel composition is at least 30%, at least 40%, at least 50%, at least 60% or at least 70% of the fuel composition. In general fuels for use in the process described here, the amount of water in the total fuel composition can be at least 0.2%, at least 0.1%, at least 1%, at least 2%, at least 3% at least 4%, at least 5%, at least 6%, at least 7%, at least 8%, at least 9%, at least 10%, at least 11%, at least 12%, at least 13% at least 14%, at least 15%, at least 16%, at least 17%, at least 18%, at least 19%, at least 20%, at least 25%, at least 30%, at least 35% at least 40%, at least 45%, at least 50%, at least 55%, at least 60%, at least 65% and at least 70%. For the methanol-water diesel fuel composition of high water content of the new modality, the water level is at least 20% by weight of the fuel composition. Ignition of such fuel at higher water levels can be achieved through increased air temperature entering the engine. Further intensification of the ignition properties can be achieved by using a fumigant that can ignite in front of the fuel injection, thus creating favorable conditions for a higher temperature after the fuel is injected, for ignition to occur. As the weight of water
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16/106 in fuel composition increases It is increasingly surprising that the ignition intensification techniques outlined above have overcome the water penalty in the fuel.
[0063] The combined amount of methanol and water in the total fuel composition can be at least 75%, such as at least 80%, at least 85%, or at least 90% by weight of the fuel composition. The fuel composition can comprise one or more additives, in a combined amount of up to 25%, or up to 20% or up to 15% or up to 10% by weight of the fuel composition. In some embodiments, the level of total or combined additives is no more than 5% of the fuel composition. In some embodiments, such as the new high water content diesel fuel composition, the additive constitutes at least 0.1% by weight of the fuel. In the new high water content diesel fuel composition, if sodium chloride is present, the level of this additive is present at a level of no more than 0.1% by weight of the fuel, and if a flavoring is present, the flavor level is no more than 1.5% of the composition.
[0064] Methanol for use in the production of the fuel composition can come from any source. As an example, methanol can be manufactured or residual methanol, or thick or semi-refined methanol, or unrefined methanol. Coarse or residual or semi-refined methanol can typically contain mainly methanol, with the balance being water and amounts of higher alcohols, aldehydes, ketones or other hydrogen and carbon oxygen molecules that arise during the normal course of methanol manufacture. Residual methanol may or may not be suitable depending on the degrees and types of contamination. The references in the sections above for methanol and water ratios, or amounts of methanol in the fuel composition by weight, refer to the amount of
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17/106 methanol itself in the methanol source. Thus, where the methanol source is crude methanol containing 90% methanol and other components, and the amount of this crude methanol in the fuel composition is 50%, then the current amount of methanol is considered to be 45% methanol . The water component in the methanol source is taken into account when determining the amount of water in the fuel composition, and the other impurities are treated as additives when evaluating the relative quantities of the components in the products, unless otherwise specified. Higher alcohols, aldehydes and ketones that may be present in crude methanol can function as soluble fuel extender additives.
[0065] According to some modalities, the fuel comprises crude methanol. The term "crude methanol" encompasses low-purity methanol sources, such as methanol sources containing methanol, water and can be up to 35% non-water impurities. The methanol content of crude methanol can be 95% or less. Crude methanol can be used directly in the fuel without further refinement. Typical non-water impurities include higher alcohols, aldehydes, ketones. The term "crude methanol" includes residual methanol, coarse methanol and semi-refined methanol. It is a particular advantage of this modality that crude methanol containing impurities at higher levels can be used directly in the fuel for a CI engine without expensive refinement. In this case, the levels of additives (ie impurities in crude methanol and other fuel composition additives excluding water) can be up to 60% of the fuel composition (including impurities in crude methanol). For fuel compositions using a high-purity methanol (such as 98% wt or higher% pure methanol) as the source, the total additive level may be lower, such as no more than 25%, no more than 20%, no more than 15% or no more than 10%.
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18/106 [0066] Any water of adequate quality can be used as the source of water for the production of the fuel composition. The water source can be water included as part of coarse undistilled methanol, or recycled water, or raw or contaminated water (for example, sea water containing salts) purified by reverse osmosis, purified by activated substances such as activated carbon, or other chemical treatment, deionization, distillation or evaporative techniques. The water can come from a combination of these sources. As an example, the water source may be water recovered from the water-rich exhaust from the combustion ignition engine. This water can be recovered through heat exchangers and spray chambers or other similar operations. This recovery and reuse technique allows cleaning of exhaust emissions. The water in this case is recycled back to the engine with or without any captured unburned fuel. Hydrocarbons or particulates or other combustion products are returned to the engine and recycled to extinction through loop combustion steps, or treated by known means of purification. The water may in some embodiments be salt water, such as sea water that has been purified to remove salt. This modality is suitable for marine applications, such as in marine IC engines, or for the operation of CI engines in remote island locations.
[0067] Water quality will impact corrosion through the supply chain to the point of injection into the engine and deposition characteristics of the engine, and proper fuel treatment with anti-corrosion additives or other methods may be required in these circumstances.
[0068] The amount of additives included in the fuel can take into account any dilution effects downstream caused by the addition of water (for example) to the fuel.
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19/106 [0069] Additives that may be present in the fuel composition can be selected from one or more of the following categories, but not exclusively:
[0070] 1. Ignition improving additives. These can also be referred to as ignition enhancers. An ignition enhancer is a component that promotes the combustion principle. Molecules of this type are inherently unstable, and this instability leads to the “auto-start” reaction that leads to the combustion of the other fuel components (for example, methanol). The ignition enhancer can be selected from materials known in the art to have ignition enhancing properties, such as ethers (including C1-C6 ethers such as dimethyl ether), alkyl nitrate, alkyl peroxides, volatile hydrocarbons, oxygenated hydrocarbons , and mixtures thereof.
[0071] In addition to the typical ignition enhancers, finely dispersed carbohydrate particles present in the combustion zone following the evaporation of the liquid fuel components before ignition may or may not have a role as combustion initiators, however such species may contribute to more combustion complete and rapid mixing of air / total fuel.
[0072] Although additional ignition enhancers can be incorporated into the fuel, the techniques described here facilitate ignition throughout the engine's operating range without such additions. Thus, according to some modalities, the fuel is free of ignition enhancing additives. In other embodiments, the fuel is DME-free (although it may contain other ignition enhancers). In the case of dimethyl ether as an ignition enhancer, according to some modalities, less than 20%, less than 15%, less than 10%, less than 5%, less than 3%, less than 1%, or none dimethyl ether is present in the composition of
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20/106 fuel. In some embodiments, the amount of ether (of any type, such as dimethyl or diethyl ether) in the main fuel composition is less than 20%, less than 15%, less than 10%, less than 5%.
[0073] In some embodiments, at least 80% of the ignition intensifier present in the fuel composition is supplied by one or at most two specific chemicals, examples being dimethyl ether and diethyl ether. In one embodiment, an ignition intensifier with a simple chemical identity is present in the main fuel composition. In one embodiment, at least 80% of the ignition intensifier in the fuel composition consists of an ignition intensifier with a simple chemical identity. In each case, the single ignition intensifier that constitutes the ignition intensifier, or> 80% ignition intensifier component, may be dimethyl ether. In other embodiments, the ignition intensifier comprises a mixture of three or more ignition intensifiers.
[0074] The amount of ignition intensifier in the fuel composition, in some modalities, is not more than 20%, as well as not more than 10% or not more than 5% of the fuel composition. [0075] 2. Fuel extender. A fuel extender is a material that provides heat energy to drive the engine. Materials used as fuel extenders may have this purpose as the primary purpose for their inclusion in the fuel composition, or an additive material may provide this function and another function.
[0076] Examples of such fuel extenders are:
a) Carbohydrates. Carbohydrates include sugars and starch. Carbohydrate can be included for fuel extender purposes, although it can also function as an ignition enhancer, and / or a combustion enhancer. Carbohydrate is
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21/106 preferably water / soluble methanol, with higher water levels that accommodate greater dissolution of sugar in the fuel. A water-enriched (single-phase) fuel composition allows for the dissolution of carbohydrate, such as sugar, but as the liquid solvent (water / methanol) in the fuel composition evaporates in the engine, the carbohydrate solute can form suspended fine particles of high LEL composition surface (lower explosive limit) that will decompose / react under engine conditions, improving the ignition capacity of the fuel mixture. To achieve improvement in the combustibility of the mixture, an amount of at least 1%, preferably at least 1.5% and more preferably at least 5% of this carbohydrate additive is preferred. A higher level of no more than 20% of the fuel composition is preferred.
b) Soluble Fuel extender additives. Fuel extender additives are combustible materials. These additives can be added as separate components or they can be part of an undistilled methanol used to produce the fuel composition. Such additives include C2-C8 alcohols, ethers, ketones, aldehydes, fatty acid esters and mixtures thereof. Fatty acid esters such as fatty acid methyl esters may have a biofuel origin. These can be sourced through any biofuel sources or processes. Typical processes for their production involve transesterification of plant-derived oils, such as dutola, palm or soy oil, among others.
[0077] There may be an opportunity to economically increase the level of fuel extender in the fuel composition itself for particular markets where such additive can be produced or grown and consumed locally, reducing the need for import of base fuel and / or additives. Under such conditions
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22/106 an amount, or treatment rate, of up to 30%, or up to 40%, or up to 50% of the fuel composition is preferred, however concentrations of up to 60% of total additives including such fuel extender additives can be considered particularly where the methanol source is crude methanol.
[0078] 3. Combustion intensifiers. These can also be referred to as combustion enhancers. An example of a combustion intensifier is a compound of nitrated ammonium, for example, ammonium nitrate. At 200 ° C, mononium nitrate breaks down into nitrous oxide according to the following reaction:
NH4NO3 = N2O + 2H2O [0079] The nitrous oxide formed reacts with the fuel in the presence of water in a similar way to oxygen, for example, CH3OH + H2O = 3H2 + CO2
H2 + N2O = H2O + N2
CH3OH + 3N2O = 3N2 + CO2 + 2H2O [0080] Other nitrated ammonium compounds that can be used include ethylammonium nitrate and triethylammonium nitrate as examples, however these nitrates can also be considered as ignition enhancers (cetane) instead of intensifiers combustion as its main function in fuel is intensification of ignition.
[0081] Other combustion enhancers may include metallic or ionic species, the latter forming by dissociation under pre- or post-combustion environments.
[0082] 4. Oxygen-absorbing oil. The oxygen-absorbing oil is preferably one that is soluble in water / methanol mixtures. Oxygen-absorbing oils have a low auto-ignition point and also have the ability to absorb oxygen directly before combustion, in amounts of, for example, 30%
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23/106 by weight of the oil. This rapid condensation of oxygen from a hot gaseous phase in the oil / solid phase after evaporation of the surrounding water will heat up the oil particle causing ignition of the surrounding evaporated and overheated methanol more quickly. An ideal oil ideally suited for this role is flaxseed oil, in a concentration of about 1-5% in the fuel mixture. If this additive is used in the fuel composition, the fuel mixture should be stored under a blanket of inert gas to minimize decomposition of the oil through oxygen. Flaxseed oil is an oil containing fatty acid. Other oils containing fatty acid can be used in place of or in addition to flaxseed oil. Preferred oils are those that dissolve in the methanol phase or are miscible in methanol, to produce a homogeneous, single-phase composition. However, in some embodiments, the oils are not miscible with water / methanol can be used, particularly if an emulsifying additive is also present in the fuel composition. [0083] 5. Lubricity additives. Examples of lubricity additives include diethanolamine derivatives, fluorotensive agents, and fatty acid esters, such as biofuels that are to some extent soluble in water / methanol mixtures whose fuel composition is based.
[0084] 6. Product coloring additives. Coloring additives help to ensure that the fuel composition cannot be confused with a liquid drink such as water. Any water-soluble dyes can be used, such as a yellow, red, blue dye or a combination of these dyes. Dyes can be a standard accepted by the liquid dye industry.
[0085] 7. Fire color additives. Non-limiting examples include sodium, lithium, calcium or strontium carbonates or acetates. Fire color additives can be selected to achieve the color of the product
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24/106 is preferred and pH stability of the final product. Engine deposition considerations, if any, can be taken into account by selecting the additive to be used.
[0086] 8. Anti-corrosion additives. Non-limiting examples of anti-corrosion additives include amines and ammonium derivatives.
[0087] 9. Biocides. Although biocides can be added, they are generally not required because the high alcohol content (methanol) in the fuel prevents biological growth or biological contamination. Thus, according to some modalities, the fuel is biocide free.
[0088] 10. Depressive freezing point. Although freezing point depressants can be incorporated into the fuel, methanol (and optional additives such as sugar, added for other purposes) depresses the freezing point of water. Thus, according to some modalities, the fuel is free of an additional dedicated freezing point depressant.
[0089] 11. Deposit reducer. Non-limiting examples include polyolether and triethanolamine.
[0090] 12. Denaturing, if necessary.
[0091] 13. pH controlling agent. An agent that raises or lowers the pH to a suitable pH can be used that is compatible with the fuel.
[0092] Additives, and particularly those identified under items 1 and 2 above, can either be added to the fuel as a product marketed by industry standard (ie in a refined form) or as a semi-processed aqueous solution (ie in an unprocessed form) refined, semi-refined, or crude). The latter option potentially reduces the cost of the additive. A condition of using such raw additive sources is that impurities in the raw forms of such
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25/106 additives, such as crude sugar solution, or sugar syrup, as an example, do not adversely affect fuel injectors or engine performance.
[0093] According to some modalities, the fuel comprises at least one additive. According to some modalities, the fuel comprises at least two different additives.
[0094] The fuel of some modalities can comprise from 20% to 80% of water, and not more than 20% dimethyl ether, by weight of the fuel composition. The dimethyl ether content of some embodiments can be 15% or less, 10% or less, or 5% or less.
[0095] Ethers are noted above as being examples of ignition enhancers and soluble fuel extender additives. Regardless of the intended function, in some embodiments, the ether may be present in total at a level of less than 20%, less than 15%, less than 10%, less than 5%, less than 3%, or less than 1% fuel composition. The amount can be greater than 0.2%, 0.1%, 1%, 2%, 3%, 4%, 5%, 6%, 7%, 8%, 9%, 10%, 12%. The lower and upper limits can be combined without limitation, as long as the lower limit is below the selected upper limit. [0096] The fuel composition comprises an ether in an amount of between 0.2% and 10% in some embodiments, by weight of the main fuel composition. The ether is preferably a single ether or a combination of two ethers.
[0097] Through the use of an ether or as an ignition enhancer and / or soluble fuel extender, in a methanol-based fuel, a complete process for the production, transportation and use of a fuel composition has been developed. Methanol-based fuel can be a
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26/106 water-free fuel or methanol-water fuel in this circumstance. This is described in more detail below.
[0098] Fuel additives of some modalities may include:
- a product coloring additive of up to 1% by weight, and
- a fire-colored additive, up to 1% by weight of the fuel.
ENGINE OPERATION DETAIL FOR INTAKE AIR PRE-HEATING MODALITIES [0099] Figure 1 illustrates a flowchart that outlines the process of using a methanol / water mixture fuel 11 in a CI 10 engine. The process includes pre- heat an intake air stream 12 and then introduce the preheated air into the combustion chamber of the engine 10 before introducing the fuel 11 into the combustion chamber and ignite the fuel / preheated air mixture by compression ignition to start the engine.
[00100] Intake air 12, which can be preheated by a variety of techniques, is injected into the combustion chamber before or during the initial stage of the engine's compression stroke to compress air before fuel is injected into the chamber combustion. Air compression raises the temperature in the combustion chamber to provide favorable ignition conditions for the fuel when it is sprayed into the chamber during the last stage of compression.
[00101] Preheating the intake air 12 provides a higher temperature base at the start of the compression stroke, resulting in the temperature at the fuel injection point being higher than if the air was not preheated and therefore more fuel. The required preheating level depends on the temperature required in the combustion chamber at the fuel injection point which is
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27/106 required to ignite a water / methanol fuel mixture. This, in turn, depends on the relative proportions of water to methanol in the fuel.
[00102] Examples of preheated air temperature levels are shown in the Examples that follow, but in general it has been observed that for fuels with a low to medium water level, suitable preheated intake air temperatures are at least 50 ° C, or at least 100 ° C, such as about 100 ° C-150 ° C, for example about 130 ° C. For fuels with a medium to high water level, preheating temperatures are in the range of at least about 150 ° C, such as 150 ° C-300 ° C or higher.
[00103] Preheating of the intake air compensates for the poor cetane characteristic of the methanol / water fuel, particularly those having a medium to high water level. Preheating can be achieved through several means.
[00104] In the embodiment shown in Figure 1, the intake air 12 is preheated by capturing the hot exhaust material 22, which comprises combusted gases and unburned fuels and other particulates, and passing the exhaust material through a heat exchanger. heat 20 which heats an air stream 15 that enters the heat exchanger and cools the exhaust material 22. A fan in line with the intake air 12 could be provided to optimize the intake air pressure profile through the motor. [00105] Techniques for preheating include any or a combination of the following heating methods:
1. Residual heat preheater - for the use of a heat exchanger as discussed above in relation to the modality of Figure 1,
2. Fumigating air intake - fumigating the air intake flow with an ignition intensifier to encourage
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28/106 temperature rise in the combustion chamber - described in more detail below.
3. Supercharger / fan - or other means of compressing air driven by the engine to force induction of intake air into the combustion chamber, and heating the intake air through an increase in air pressure.
4. Turbocharger - or other air compression mechanism driven by engine exhaust or other residual heat to force induction of intake air into the combustion chamber, and heating the intake air through an increase in air pressure.
5. Direct heating - using direct methods to heat the air, such as electrically heating by means of elements or combustion of fuel to generate the required temperature rise. Such methods can be useful during starting and low engine loads.
6. Candles (or hot bulbs) - directing heat to the engine cylinders, this category including external heaters in line with the intake air to directly heat the intake air. [00106] Residual heat passing from the engine exhaust through a heat exchanger (option 1 above, without a fan) will result in a lower power output from the engine due to a lower mass flow of air (compared to options 3 to 4 , where the mass air flow is not reduced). However, this maximum power loss can be compensated in part by higher combustion efficiency in the hottest conditions at the fuel injection point and a lower excess air requirement compared to petroleum based diesel fuels. An exhaust pressure compensation fan, or otherwise, can compensate for the reduced mass air flow under conditions of increased air temperature.
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29/106 [00107] Alternatively, a turbocharger or supercharger could be used alone or in combination with an engine exhaust heat exchanger to derive high combustion efficiency as well as more power.
[00108] In another embodiment, heating the fuel according to known techniques can help the ignition process. [00109] The preheating option in combination with medium to high water fuel / low methanol changes the engine cycle from being a “constant” volume cycle during the ignition and combustion and initial expansion phase, for directionally more than a constant temperature expansion (where the heat from methanol is in the evaporating water of a significant part) in a more suitable period to maximize the performance of the engine.
[00110] The process illustrated in Figure 1 includes an exhaust treatment and recycling component to collect and integrate the exhaust material back into the fuel. In particular, treatment includes the recovery and integration of water, unburned fuels, hydrocarbons, carbon dioxide and other small amounts of emissions.
[00111] In fuels that have a medium to high water level, but not excluding lower water levels, the water-rich exhaust can be a source of fuel water and small levels of exhaust pollutants can be captured and returned to the engine. Recovery of water from the exhaust material involves cooling and condensing the exhaust material and collecting the condensed water.
[00112] Figure 1 shows that after the exhaust material 22 is cooled by heat exchange with the intake air 12 in the heat exchanger 20, the cooled exhaust is then passed through a condenser 25 through which the water can be collected and returned
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30/106 as recycled fuel 32 for engine 10.
[00113] A second heat exchanger 34 in the final stage of the treatment process helps with condensation and additionally includes an arrangement of spray chambers using water that may have been purified and may contain additives to capture and purify any unburned methanol or other hydrocarbons in fuel, soot and other particulates. These particulates are returned to the engine for disposal through a 'recycling for extinction' process with recycled fuel 32, while the purified clean exhaust 33 can be released into the atmosphere containing almost no pollutants. The water used in the spray chamber can be from a range of alternative sources, and can be purified or deionized. The water can contain optional additives. Optional additives should be consistent with the combustion process.
[00114] The 354 heat exchanger can be a water / salt water heat exchanger as shown in Figure 1 that captures salt water through an inlet 36 and expels the salt water through an outlet 37. Such a heat exchanger it is suitable for use in exhaust treatment, for example, on ships where the availability of sea water in the sea is abundant and easily obtainable.
[00115] Additional exhaust treatment steps using condensate or other means can also be taken to reduce the target pollutants to low levels in the exhaust gas to the atmosphere. In another embodiment, components such as any unburned fuel can be adsorbed onto an active surface and then desorbed using standard techniques, and included as a fuel or fumigant component to further reduce pollution. Alternatively, a catalyst can be employed to catalytically react any oxidizable species such as fuels
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31/106 not burned, increasing the exhaust temperature and providing an additional heat source that can be used.
[00116] Additionally, if multiple engines are operating, for example, to produce electricity, the aggregate exhaust gas can be treated as a simple flow to be treated / condensed with the recycle fuel from the exhaust being directed to one or more such engines.
[00117] A purge (38) may be required in the case of water recirculation back to the engine, to ensure that any persistent species that may be present do not accumulate. In this event, the water removed can be made through additional condensation of the exhaust if available, or if not available through replacement water (39) of adequate quality. It is intended that by selecting the appropriate feed streams and additives, purging can be almost eliminated, but solids can also enter the system, for example, through dust in the air which may require purging from time to time.
[00118] An advantage of using a fuel with a medium to high water level is that the resulting exhaust contains almost no impurity, which is ideal for the post-combustion process. Impurities that are present in the exhaust material can be treated and recycled for extinction.
[00119] For example, carbon dioxide as an exhaust product from the combustion of a water / methanol fuel is absorbed in the recycled water during the condensation and purification phases. Alternatively, the carbon dioxide in the exhaust material can be recycled into the engine's intake air thereby optimizing the level of oxygen entering the engine, and generating pure carbon dioxide and water vapor escape. The carbon dioxide generated in this way is ideal for further processing, for
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32/106 example, by conversion to methanol and recycling for fuel. [00120] The final exhaust gas 33 from the treatment and recycling process that is emptied into the atmosphere contains almost no emissions of fuel, hydrocarbons, particulates, sulfur oxides and nitrogen oxides.
[00121] Any emissions of nitrogen oxides or sulfur oxides formed in the combustion phase and / or in the absorption of carbon dioxide in water, may result in pH imbalances in the water that returns to the mixture with the fuel. To prevent the formation of such components, a chemical treatment can be added to the fuel to neutralize any imbalances or remove them. ENGINE OPERATION DETAILS FOR FUMIGATION MODALITIES [00122] In some modalities described here, the fumigation of the intake air with a fumigant comprising an ignition intensifier is used. In some embodiments, this is coupled with the preheating of the intake air, and in other embodiments, this is performed without preheating the intake air.
[00123] The option of fumigating the intake air with a fumigant comprising an ignition intensifier can be used according to some modalities as an additional technique of preheating the engine air. Fumigation encourages an additional increase in the temperature of the air being compressed in the combustion chamber making it even more fuel at the fuel injection point due to the pre-combustion of the fumigant material, and the presence of breakdown species that aid the combustion principle of the methanol.
[00124] Fumigation allows pre-combustion to take place in the engine's combustion chamber before fuel injection. This two-stage ignition process, or ‘ignite’ operation, has the course
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33/106 compression of the engine piston to raise the temperature of the fumigated air to the ignition point. This in turn intensifies the ignition conditions in the combustion chamber to provide a sufficiently warm environment for the methanol fuel and water, when injected at the end of the compression stroke, to undergo accelerated ignition under increased temperature conditions, rapidly vaporizing the methanol and evaporating water in the fuel and producing high thermal current efficiency.
[00125] The contribution of temperature per fumigant to the operation of a stable engine at low water levels is 50 to 100 ° C. At the fuel injection point for low water level fuels this contribution results in a combustion chamber temperature comparable to the temperature in known combustion ignition engines. As water levels rise in the fuel, the amount of fumigant can be adjusted to compensate for the cooling effect of the water. The resulting thermal efficiencies are comparable to those of diesel fuels, with net efficiency results being dependent on several factors such as the size of the engine and its configuration.
[00126] Efficient and complete combustion of methanol fuel and water in this way minimizes unburned or modified hydrocarbons and particulates in exhaust emissions resulting in "cleaner" emissions. This is particularly evident in larger CI engines with slower speeds where the efficiency of the combustion process is maximized because sufficient time is allowed for the start and completion of the two steps in an ignited operation.
[00127] The term "fumigation" in relation to the intake air refers to the introduction of a material or mixture, in this case a fumigant comprising an ignition intensifier, in the air stream of
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34/106 intake to form a vapor or gas through which the ignition intensifier is well distributed. In some embodiments, the material is introduced in a small amount, usually by spraying a fine spray of the material into the intake air stream or injected as a gas.
[00128] The ignited operation has the effect of preheating the intake air during the compression stroke.
[00129] The nature of a water-methanol mixture is that less sensitive heat is generated in the reaction products after combustion, the heat being required to evaporate the water present. This means that compared to a diesel engine operating on hydrocarbon fuels more severe engine conditions can be accommodated at the injection point while keeping the engine's design limitations within. These more severe conditions arise through combustion of fumigant or increased air temperature (directly heating the air) and / or increased pressure and temperature through the use of modified engine configurations, such as turbocharging or overcharging.
[00130] The amount of ignition intensifier (s) can be controlled with respect to the methanol to water mixture contained in the fuel to produce conditions within the combustion chamber where the ignition of the fuel is achieved in a timely manner, and thus releases the best possible thermal current efficiency of the motor. Where the ratio of ignition intensifier to fuel mixture is not controlled, combustion could start significantly before TDC, such as 25-30 ° before TDC, and as such the use of an ignition intensifier could have an effect neutral and could have minimal or no contribution to the thermal efficiency of the engine.
[00131] In a preferred operation of the engine, the regulation of the ignition of the fumigant / air mixture is to delay the combustion of this fuel o
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35/106 maximum possible (to avoid working unnecessarily against the engine's power piston) and be consistent with good fuel combustion after injection. This means that the fumigant, which can be referred to as a secondary fuel, should ignite before the fuel injection begins, but not so much before the energy contained in the fumigant makes a minimal, if any, contribution to the thermal efficiency of the fumigant. motor.
[00132] Fuel ignition can be controlled by an ignition control to be as close as possible to optimal regulation using one or a combination of the following ignition controls:
a) Engine intake air temperature control:
The. Control the outlet temperature of an air preheater using heat from:
i. An electric heating device, useful for starting and heating the engine.
ii. A heater using fuel that can be the engine fuel or any fuel suitable for that purpose.
iii. Use residual heat from the exhaust to directly heat the intake air to the engine by means of heat exchange.
iv. Use any other heat source suitable for the purpose.
B. Use engine exhaust energy to start a turbocharger that may not have an intercooler that would reduce the engine's intake air temperature.
ç. Heat the air with a supercharger to increase temperature and pressure
b) Use a fumigant to create an “ignited” combustion of two stages of the fuel.
1. Check the amount of fumigant introduced into the
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36/106 air intake with respect to fuel;
2. Control the ignition intensifier percentages for other components in the fumigant (recognizing that water and other components such as methanol may also be present);
3. Check 1 and 2 above, depending on the engine operating at high loads (50% to 100%) or low loads (below 50%) over the engine's operating range in rpm.
[00133] Although the relative quantities of the fumigant to the main fuel introduced into the engine (either through the air intake, or in the combustion chamber, respectively), will vary, depending on the engine operating conditions that apply, it is generally desired that the amount of ignition intensifier in the fumigant during steady-state operation at medium or high load is a relatively low percentage by weight of the main fuel composition. For a fumigant comprising 100% ignition intensifier (such as DME), the relative amounts of fumigant for main fuel by weight is desirably up to 20% by weight, up to 18%, up to 15%, up to 13%, up to 10% , up to 8%, up to 7%, up to 6%, up to 5%. The fumigant level is preferably at least 0.2%, at least 0.1%, at least 1% or at least 2% by weight of the main fuel composition. These numbers are based on weight, assuming that the fumigant comprises 100% ignition intensifier, and can be proportionally adjusted to a reduced ignition intensifier content in the fumigant by weight. This can be measured with reference to the quantity introduced into the engine in grams per second, or any other corresponding measurement suitable for the size of the engine. An upper limit of around 10% or less (such as 8% or 7%) is additionally advantageous, as a pre-fuel composition
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37/106 containing up to the required amount of ether as an ignition intensifier (such as 10%, 8% or 7% ignition intensifier, respectively) can be released to the location of the compression ignition engine, and the ignition intensifier vaporized and recovered in an amount that corresponds to the needs of the engine operating with fumigation at the same target level. In other embodiments, the fumigant level can be supplemented to a higher level at the engine location (for example, through the separate storage complement of the ignition intensifier, such as ether).
[00134] In relation to paragraph 2 above, the target% of non-water components other than the ignition intensifier in the total fumigant / air flow may not be more than 40%, such as between 5-40% or 10-40% , or 20-40% or 30-40% with the balance being an ignition enhancer, for example, DME (which has a 55-57 cetane). Adjustments can be made to these percentages based on the cetane number of the other ignition intensifiers and specific engine configuration. All percentages are by weight. Water can be present in any amount consistent with the smooth operation of the engine, such water can arise from the fumigant for example if made catalytically from the fuel, or as part of the flow of ambient air into the engine.
[00135] A catalytic reactor can be provided in the process to start the CI engine in which the catalytic dehydration of methanol (taken from a diverted portion of the fuel) to DME is performed. The DME produced is used as an ignition intensifier in the fumigant for fumigating the intake air. Other modalities described here use other techniques to generate dimethyl ether, when used as the fumigant ignition intensifier. In some such modalities, the DME can be generated at the location of generation of
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38/106 methanol, and released as a part of a pre-fuel composition at the engine location.
[00136] Some adjustment for the fuel and process described above may be required to optimize operation and efficiency in smaller CI engines that operate at higher engine speeds, for example at 1000 to 3000 rpm, and above. In addition to preheating the air intake flow using any one or more of the techniques described above, the following operational aspects can be used separately or in combination for engines operating at higher speeds:
• fumigate the air intake with a fumigant comprising an ignition intensifier.
• heat the combustion chamber using, for example, candles.
• preheat the fuel inlet.
• add additives to the fuel and / or fumigant that improve the ignition and combustion of fuels. Some of these additives are discussed above.
• select the appropriate water level in the fuel composition as discussed above, such as a low to medium water level range.
• select the water level in the fumigant to an appropriate level consistent with the engine configuration.
[00137] These options can be additionally used if desired when operating a larger CI engine at lower engine speeds, such as 1000 rpm or less.
FUMIGANT [00138] The fumigant for use in modalities that rely on fumigation comprises an ignition intensifier. The fumigant may further comprise other components, such as one or more
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39/106 methanol, water and any of the additives outlined above in the context of the fuel. For the following description of the use of fumigant, the previously described fuel can be referred to as the "primary fuel" for the compression ignition engine, and the fumigant can be referred to as the "secondary fuel".
[00139] An ignition intensifier is a material that intensifies the ignition of a combustible material. One of the challenges for using methanol as the central fuel component in the main fuel composition for a compression ignition engine is the fact that methanol does not ignite as easily as other fuels. An ignition intensifier is a material that has good ignition properties and can be used to create ignition, following that the methanol in the main fuel composition (and other combustible materials) will combust. The ignition characteristics of a potential fuel component are described by the cetane number (or alternatively cetane number) of that component. The cetane number is a measure of a delay in igniting the materials, the period of time between the start of the injection and the start of combustion, that is, ignition, of the fuel. Suitable ignition boosters can have a cetane of over 40 (such as DME having a cetane of 55-57). The cetane number (s) of the ignition intensifier (s) present in the fumigant should be taken into account when determining the relative quantities of ignition intensifiers for other components in the fumigant. fumigant, and also the amount of fumigant compared to the main fuel composition, load and engine speed. The general cetane of the fumigant will be based on a combination of the proportional contribution, and the cetane property of each component, the relationship is not necessarily linear.
[00140] Some non-limiting examples of
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40/106 ignition that can be included in the fumigant include:
- ethers, such as lower alkyl (C1-C6 ethers being), notably dimethyl ether and diethyl ether,
- alkyl nitrate,
- alkyl peroxides, [00141] and mixtures thereof.
[00142] Dimethyl ether is a preferred high ignition characteristic ignition intensifier suitable for use in the fumigant. Diethyl ether is another example of a suitable ignition intensifier.
[00143] Methanol in the main fuel can be catalytically converted to dimethyl ether. The dimethyl ether can therefore be catalytically generated from a stream of the main fuel composition which is then fumigated separately in the engine to the main fuel composition (with the intake air). Alternatively, a fumigant composition comprising dimethyl ether can be supplied by the fuel supplier to the engine owner as a fumigant composition already made. In another embodiment, a pre-fuel composition comprising methanol and up to 15% by weight of an ether ignition intensifier (such as dimethyl ether) can be produced at one location and transported (for example, via a pipeline) to another location for use in filling a compression ignition engine. In some embodiments, the pre-fuel composition may further comprise water. At the end of the pipeline, part or all of the ether ignition enhancer component in the pre-fuel can be separated from the other components of the pre-fuel composition (notably methanol, but also other components having a higher boiling point than ether) . The separate ether component can then be fumigated in the compression ignition engine as a fumigant, separately for
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41/106 remaining part of the pre-fuel composition, which is used as the main or direct fuel composition (if it contains some water), or with additional adjustment in the composition (for example, adjusting the water content) before the use. The amount of ether ignition enhancer in the pre-fuel can be up to 10% by weight, or up to 9% by weight. The upper limit will depend on the choice of ether and the temperature conditions. More details are set out in the section below detailing CI engine power generation systems.
[00144] The ignition intensifier, such as dimethyl ether, comprises a minimum of 5% of the fumigant or a minimum of 10% of the fumigant appropriately, such as a minimum of 15%, 20%, 30%, 40%, 50% , 60%, 65%, 70%, 75%, 80%, 82%, 84%, 86%, 88% or 90% of the fumigant. There is generally a preference for the ignition intensifier content of the fumigant to be at the upper end of the range, so in some embodiments the ignition intensifier content is above 70% or more. The ignition intensifier can comprise up to 100% of the fumigant, for example, in the case of introducing a pure or original storage component of the separate ignition intensifier recovered from a pre-fuel composition. When converted from the main fuel through a catalytic reaction of the main fuel (which comprises components other than methanol, from which DME is formed) or if the characteristic impure high-ignition component is produced or taken out of storage, the upper limit for that component will be consequently reduced.
[00145] The relative quantities of each component in the fumigant can be kept constant, or can be varied in the period of time the engine is in operation. Factors that impact the relative amounts of components in the fumigant include engine speed (rpm), load level and variability, configuration
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42/106 of the engine, and the specific properties of the individual components of the fumigant. In other embodiments, the fumigant composition can be kept relatively constant, and otherwise the relative amount of fumigant (grams per second fumigated in the engine) compared to the main fuel composition injected into the engine (grams per second) is adjusted during the different stages. engine operation.
[00146] When it is desired to operate the CI engine with different fumigant compositions for different engine operating conditions (speed, load, configuration), the fumigant composition can be varied to adapt by computer control of the fumigant composition, or by any other form of control. The adjustments can be mobile adjustments based on an algorithm that calculates the desired fumigant composition to match the prevailing engine operating conditions, or they can be adjustments in stages. For example, a higher general cetane number fumigant (such as 100% DME) could be fumigated in the engine at a high weight% with respect to the fuel for operation in some conditions, and then the fumigant could be replaced by a second composition containing a lower% DME and some lower cetane number components. In another embodiment, the composition can be stable and the air / fumigant ratio varied.
[00147] The target% of non-water components other than the ignition intensifier or intensifiers and water in the fumigant is not adequately more than 40%, such as between 5-40% or 10-40% or 2040% or 30-40% . Adjustments can be made to these percentages based on the cetane number of other ignition enhancers and fuel components, and specific engine configuration.
[00148] Additionally in some modalities, water may be present in the fumigant as a product of a conversion reaction (for example
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43/106 (methanol for DME) or as a transport of a water containing reactor feed, or added as a separate flow or in combination with an additive.
[00149] Examples of components that may be present in the fumigant in addition to the ignition intensifier include methanol, water, the additives outlined above (in the context of the fuel composition), and the alduct gases (typically straight chain alducts, including lower alducts such as C1-C6 alducts, notably methane, ethane, propane or butane, and longer chain alducts (C6 and above). [00150] In some embodiments, the fumigant comprises at least 60% of a simple component, an example being dimethyl ether The amount of the simple main component of the fumigant can be above 62%, 65%, 68%, 70%, 72%, 75%, 78% or 80%.
[00151] The fumigant, or secondary fuel, can be obtained directly from storage, or it can be supplied as a fumigant to the engine in pure form after processing the main fuel (meanwhile catalytic conversion from methanol to DME, followed by purification to yield a fumigant consisting of DME). Alternatively, the fumigant may comprise an ignition intensifier and other components (i.e., the fumigant is not in pure form) after processing the main or storage fuel. In this case, the additional impurities are compatible with the desired fumigation result, that is, the fumigant may also include water and methanol, or may contain other materials (such as C1-C8 alcohols) that are compatible with the application.
[00152] The main fuel composition and the fumigant can be supplied as a two-part fuel, or can be released as a two-part fuel kit. In this context, the fumigant can be described as a “secondary fuel component” of the two-part fuel, and thus the description
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44/106 of the above fumigant also applies to the second fuel component. The main fuel composition and the secondary fuel component can be pumped into separate storage tanks associated with the compression ignition engine.
[00153] Thus, with a two-part fuel for use in operating a compression ignition engine, the fuel composition comprises:
- a main fuel composition comprising methanol and water and
- a secondary fuel component comprising an ignition intensifier.
[00154] The main fuel in this context may be the new methanol-water diesel fuel with a high water content, or different.
[00155] When using this two-part fuel, the main fuel is introduced into the combustion chamber of the compression ignition engine, and the secondary fuel is fumigated in the air intake of the compression ignition engine.
[00156] A method for filling fuel in a compression ignition engine comprises:
- supplying a main fuel composition comprising methanol and water to a first tank that is in fluid connection to a combustion chamber of the compression ignition engine, and
- supplying a secondary fuel component comprising an ignition intensifier to a second tank that is in fluid connection to an air intake of the compression ignition engine.
[00157] As described above, the secondary fuel can be
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45/106 completely or partially prepared in situ through catalytic conversion of a portion of the main fuel in the ignition intensifier. This is particularly suited to situations where dimethyl ether is the ignition intensifier.
[00158] In one embodiment, the use of a two-part fuel is provided in the operation of a combustion ignition engine, in which the two-part fuel comprises:
- a main fuel composition comprising methanol and water, and
- a secondary fuel component comprising an ignition intensifier.
[00159] The present invention further provides a pre-fuel composition comprising methanol and up to 10% by weight of an ether. The ether can be dimethyl ether. As noted above, the ether component can be separated from the remainder of the pre-fuel composition for use as the secondary fuel component, and the balance of the pre-fuel composition can be used as the main fuel composition. This balance can be used directly as the entire main fuel composition, or the composition can be adjusted to yield the main fuel composition. In this embodiment, therefore, the pre-fuel could contain no water, and water can be added to generate the main fuel composition after removal of the ether. In some embodiments, water may not be required for use in the main fuel composition, when the fuel is used in one of the power generation systems described below.
[00160] The present invention also provides a method of transporting a two-part fuel composition comprising methanol in the first part, and an ether in the second part, from one location to another location, which comprises transporting
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46/106 a pre-fuel composition comprising methanol and ether from one location to a second location, and separating the ether from methanol to yield a first part of fuel comprising methanol, and a second part of fuel comprising ether. Transportation can be via pipeline through an oil pipeline. The first location can be a location of the methanol production plant, and the other location (the second location) is a remote location from the first location. The remote location will typically be at least 1 kilometer distant, and perhaps many kilometers distant. The remote location may be the location of a compression ignition engine for electricity generation, or a port of embarkation, or a train diversion or any other suitable location where two-part fuel is required.
CI ENGINE POWER GENERATION SYSTEMS [00161] Using the methanol / water mixture fuels described here and related systems (also referred to as processes) to start a compression ignition engine, power generation systems and structures can be developed to efficiently generate power at reduced emission levels, and which can also handle engine exhaust to capture and then reuse or redirect the heat and water from the exhaust gases. The reuse, or recycling, of heat and water promotes increased system and waste product efficiencies and reduced overall emissions. Redirection of heat and water can find use in a range of unrelated applications involving heating / cooling locations / regions and the regeneration of water for use by communities or as part of other systems. [00162] Figures 3A to 6B illustrate examples of power generation systems that incorporate the processes and fuels described here
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47/106 to start a compression ignition engine. It is understood that the fuel represented in these processes is a fuel based on methanol that can contain various amounts of water, and can contain water in the amount of 0% to 80%.
[00163] Figures 3A and 3B show a process for producing and supplying a methanol fuel to an IC 111 engine (also referred to as a diesel engine) to produce output power, but also to include an engine exhaust treatment that reduces emissions, takes advantage of the engine exhaust to recycle water and also incorporates a Hot Water (HWL) duct 113a, 113b (see Figures 4A and 4B) to provide heat to a local community. Output power produced by the engine can also be used to serve the location in which the power generating plant is located, and for example, it can be used to generate electricity for a community. Figures 3A and 3B differ in that Figure 3A shows the process using fumigation of air in the engine, while the process shown in Figure 3B omits the step of fumigating the intake air.
[00164] Figures 3A and 3B illustrate a fuel manufacturing plant 101 and the remote provision of that fuel through an electrical network 103. The fuel manufacturing plant may be a conventional methanol manufacturing plant using electricity generated from steam produced from conventional boilers in a large remote coal plant 102. Such a plant produces a profile of incinerated coal emissions. Alternatively, the electricity generation plant 102 could incorporate a combustion engine using a methanol fuel as described here to generate the electricity required to produce the methanol fuel. This would provide a cleaner alternative with lower emissions than those produced by a coal plant.
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48/106 [00165] Methanol-based fuel is manufactured at plant 101 and can largely contain methanol, a methanol-water mixture or a methanol-ether mixture or a methanol-water-ether mixture. In one embodiment, the fuel comprises a mixture of Methanol and DME of "Integral Fuel" in a mixture of 90-99.5% methanol and DME as a non-boiling liquid at atmospheric pressure that can be used directly with the engine 111. DME is supplied in a stable amount suitable for transmission as a liquid in the mixture of methanol and DME, and to prevent ether transition in the gas phase. The amount will depend on the pressure and temperature at which the fuel is transmitted in the pipelines 103, but in general it will be less than 10% of the total fuel quantity, and in the range of 7% -8%.
[00166] Alternatively, fuel having a higher DME ratio under pressurized conditions can be supplied. In another alternative, a fuel containing a high methanol content approaching 100% methanol (for example, chemical type) could be transmitted for conversion of the subsequent part to DME near the demand center (namely the power generation plant) . This form of pre-fuel composition comprising a high% of methanol may contain a water component of around 0.2% or more. In another alternative, the fuel or pre-fuel transmitted in the pipelines can be a methanol-water fuel. The water in the methanol-water fuel can be associated with methanol, such as in crude methanol, or it can be the source of an excess of water in the manufacturing area that can be used cost effectively for this purpose. Some addition of lubricity additive and corrosion enhancer can be included in the fuel transmitted depending on the construction materials in the transmission network and to intensify the operation of the
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49/106 engine / process.
[00167] Transmitting large amounts of energy in flammable liquids over long distances to pipelines in regional networks is an established technology. Such infrastructure as pipelines 103 can also be used to release methanol fuel safely to distant locations and cost effectively.
[00168] After being transmitted through pipelines 103, the fuel arrives at a power generating plant including the compression ignition engine 111, a preprocessing stage 104 and exhaust treatment 113, 115, 116 118. The fuel can be used on engine 111 immediately as it is, or optional pre-treatment of the fuel can be performed to ensure safe and reliable operation across the plant's operating range. Storage of a starting and shutdown fuel can also be contemplated for reasons of system integrity, for example, an ether component could be stored.
[00169] In the pre-processing stage 104, the fuel can be divided by vaporizing sharply into two rich phases, one rich in methanol 107 and one rich in ether 105, such as DME. DME is particularly suitable for this sudden vaporization process due to its low boiling point. Low level residual heat from the engine exhaust from a hot water stream having a temperature of 50 ° C-60 ° C can be used to vaporize sharply by separating the low boiling DME from methanol. In some embodiments, the methanol-rich phase may include low amounts of DME, with most DME being vaporized. In other embodiments, a high proportion of DME can be retained in the liquid phase with just enough DME to ensure good and complete combustion being vaporized and used as a fumigant 105. For
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50/106 example, if the fuel from the manufacturing plant includes 7% DME, 5% of these can be retained in the liquid phase with 2% being used as a fumigant 105 to add to the heated combustion air 110 entering the engine 111.
[00170] Pre-processing may include a conversion option to supplement the provision of DME or other fumigant. Alternatively, the required amount of ignition enhancing agent, such as DME, can be obtained from storage. Other such agents are also possible such as DEE and other ignition enhancers described herein.
[00171] The pre-processing stage may also include processing part of the transmitted fuel to not only separate DME to be used as a fumigant, but also to produce excess DME for use as a liquid fuel ingredient for other processes. For example, excess DME could benefit a nearby community by providing excess heat to HWL. Alternatively or additionally, the DME could be integrated with the processes of the generating plant. Methanol fuel, either before or after processing, can also be removed from the power generating system and used for local chemical manufacturing.
[00172] Transmission to the crude methanol generating plant is also possible, saving capex and opex costs in an upstream manufacturing plant. Such a fuel supply to the power generating plant would suit the above option of vaporizing part of the raw methanol for the production of DME, with the remaining fuel being directed to the engine. In terms of energy and capex, this option would replace a distillation unit in manufacturing plant 101 with most of the product being distilled and going “on top” with a much smaller unit in the power generating plant with a relatively low amount that will “ on the top".
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51/106
This option will also make the local DME available close to the demand centers, and close to the power generating plant. [00173] The pre-treatment of fuel in the preprocessing stage 104 can also heat the methanol fuel 107 before entering the engine using hot water, derived from the venturi decontaminant return pipe 115. Water leaving the pre-processing stage Process 104 comes out as irrigation grade water 106, chilled irrigation grade water 106 can mix with condensate from condenser 116, and if necessary a cooler could be used to ensure acceptable effluent temperature.
[00174] In the example shown for power generation with an HWL, the diesel engine would be used to generate power of 1 MW and above. This does not exclude power below 1 MW that could serve smaller users and could have a low NOX, SOX and particulate result. A diesel engine is particularly suited to post combustion treatment because it provides the driving force of air pressure necessary to move the exhaust through cleaning and heat exchange equipment at only a small cost in engine efficiency.
[00175] The nature of some of the fuel mixtures described here means that large diameter pistons are preferred over smaller pistons due to the thermal benefits inherent in the size of the engine that is increased. Larger pistons also reduce the risk of fuel injected into the piston walls, ensuring that the fuel burns correctly and does not interfere with the lubricant film.
[00176] Although the experiments mentioned below demonstrate fuel tested in an engine operating above 1000 rpm, as previously suggested the fuel can be quite well
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52/106 used on slower speed engines, normally only operating below 100 rpm up to 1000 rpm, which is the range normally described as being the low to medium speed range. This speed range allows more time for volatile ignition enhancers to enter the vapor space as vapor and start their chemical reactions with hot compressed air during the compression stroke. This longer time allowance during the combustion phase will allow for more complete combustion of the fuel and will reduce the level of unburned fuel and other components in the engine exhaust. The allowance for a longer time will also allow more time to completely combust the fuel in the cylinder through the contact of the water and oxygen molecules, allowing to use lower lambda and thus increasing the concentration of water in the engine exhaust.
[00177] Power is generated in engine 111 by a mixture of methanol 107 and water 108 entering engine 111 together with air 100 that can be preheated and in the example shown in Figures 3A and 3B it is preheated by exhaust gases from the engine through capacitor 116. A suitable preheated temperature could be between 40 ° C and 50 ° C. Water in the fuel can be from a water storage or water recycled from the exhaust gas through condenser 116 (explained in more detail below).
[00178] Exhaust gas treatment includes passing the engine exhaust through a 112 catalytic converter using catalysts that target CO2 and oxygen compounds. This will cause marginal heating of the exhaust gas where that heat may be available for HWL, or for other processes described below in relation to Figures 5A, 5B, 6A and 6B. The catalytic converter 112 also reduces any fuel or combustion products to an appropriate level. An end-stage activated carbon or
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A similar 53/106 can optionally be used for cleaning. In addition, the methanol fuel described here burns clean with low soot, which improves the performance of the catalyst.
[00179] HWL carries heat to a location-based destination such as a residential community via a pumped-water pipeline. Figures 4A and 4B illustrate the supply pipe of HWL 113a and return pipe 113b in the heat exchanger of HWL 113. Utilization of the heat by-product of the power generation process can be used to provide low-cost heating for residential and commercial rooms . The water pumped through the HWL is heated through an HWL 113 heat exchanger downstream from the catalytic converter 112. The heat exchanger 113 is a standard unit operating at a temperature of 40 ° C at the HWL return with a discharge temperature of 80 ° C design for HWL. The return temperature of the relatively cooled HWL and the efficient changer design in terms of the required surface area will ensure sufficient exhaust cooling.
[00180] Exhaust treatment additives are added to the caustic injector 114 which injects any caustic chemicals and other suitable acid neutralizing agents into the exhaust gas for a desired result. For example, to eliminate acidic compounds from the final exhaust, a low dose of a basic liquid (for example, 50% caustic coolant and water) will be injected into the exhaust stream, used to cancel trace acids and control the pH of the irrigation water flowing from the plant. Final pH will be controlled to a level that best meets local conditions.
[00181] A venturi decontaminant 115, or other suitable mixing device, is illustrated downstream of the HWL 113 changer. This unit has several functions, the first being intimately mixing the exhaust gases with a circulating water flow, the effect of
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54/106 water flow being to cool the exhaust from 85-90 ° C of the HWL changer to about 55-60 ° C of the venturi discount. Such cooling will create condensed water from the exhaust gas and collect particulates that can be treated using known methods, or ultimately form part of the final irrigation water that leaves the plant to return to the ground. The de-acidified and clean exhaust leaving decontaminant 115 produces a leak of higher purity outside the final condenser.
[00182] The water is pumped between the venturi decontaminant 115 and a 100 vane fan heat exchanger. The vane fan heat exchanger, or other suitable equipment, is another gas / liquid exchange that removes heat from the exhaust gas through the venturi decontaminant and expels that heat to the air which is directed to flow through the heat exchanger 100 by one or more fans. An advantage of heat rejection in this way is that heat is rejected at low temperature, and therefore, does not have a major impact on the overall efficiency of the process.
[00183] Alternative to expel heat in the atmosphere, heated air from the exhaust fan vane can be used directly in the engine as the heated combustion air 110 in which case some pressure can be applied from the fan to compensate for the heating effect in the flow of air mass. Another alternative for expelling heat in the atmosphere is to dissipate heat through a cooling pond or other water system capable of dissipating a large amount of heat in a responsible and environmentally acceptable manner.
[00184] Figure 4A illustrates a large exhaust gas / exhaust gas changer, namely condenser 116 which recovers water in high water recovery systems. In systems where high water recovery is not required, condenser 116 is not
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55/106 included. Figure 4B illustrates an average water recovery system similar to that in Figure 4A but omitting condenser 116. [00185] The final condenser (optional) 116 cools the venturi 115 decontaminant exhaust from approximately 50-60 ° C to within about 5-20 ° C of room temperature. By decreasing the temperature to this amount, the produced water recovered from the plant is increased significantly. In addition to producing water for irrigation, or reuse outside the power generation plant, condensate from condenser 116 can optionally be useful within the power generation process.
[00186] The condensate can be injected with pre-processed fuel to reduce the formation of NOX and associated acidity problems in the downstream equipment, such as in the HWL changer. The condensate can also form a water source to be used in the particular fuel combustion mixture as an alternative or in addition to the stored water. In addition, the higher type water from the condenser can still be treated in drinking water, or can be added to the irrigation quality water produced by the venturi decontaminant and to recirculate between the venturi decontaminant 115 and the fan heat exchanger fin 100.
[00187] The heat from cooling the exhaust is not lost, but can be exchanged with the intake air in the engine 111. Apart from the benefit that recycling waste heat and water makes the required fuel and the emissions produced in the process, water recovery and heat also tends to stabilize the engine's operation. The cooler intake air for the engine allows more heat to be recovered.
[00188] Figure 3B differs from Figure 3A in that it illustrates the process for producing and supplying methanol fuel to engine 111 without fumigating the intake air with an ignition enhancer.
[00189] Methanol fuel from manufacturing plant 101 is
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56/106 transported through pipeline infrastructure 103 for direct use with engine 111, where the intake air 110 is preheated. This methanol stream can contain low water levels, such as at least 0.2% water. Pre-processing to abruptly separate an ether from the transported fuel is not required any more than the fumigant is required. However, pre-processing can still take place to prepare the fuel for combustion and / or to separate the ethers for separate use outside the power generation plant. It is also understood that in relation to Figure 3A, the step of preheating the intake air with exhaust heat is not essential and could be omitted. However, it is useful to use exhaust heat and recycle exhaust particles to improve engine efficiency and reduce emissions.
[00190] Alternatively, water could be used from the venturi decontaminant to the vane fan in principle for the purpose of heating the intake air.
[00191] In the process illustrated in Figure 3B, the intake air can be preheated by various means including using the heat transferred from the exhaust gas, for example through condenser 116 or the heat taken earlier from the exhaust in the exhaust process. post-combustion as in the catalytic conversion stage. Alternatively, the intake air is preheated using other techniques described here including direct heating with the electric heating elements, candles, and indirect heating such as via superchargers or turbochargers.
[00192] Figures 5A and 5B illustrate how the concept of power generation using the technology and fuel described here can be applied to start a rail vehicle. The reference numbers in Figures 5A and 5B correspond to the same numbers and items used in relation to Figures 3A and 3B. Any pre
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57/106 fuel processing 104 and fuel use through engine 111 are the same. The exhaust air is cooled after leaving the catalytic converter 112 through a first heat exchanger
120 which uses ambient air to cool the exhaust and heat combustion air 110.
[00193] Exhaust treatment in a rail vehicle differs from that of the HWL process in separating water from other exhaust material. The exhaust gas leaving the catalytic converter is passed through an activated Alumina water absorption cycle
121 and an activated Alumina water evolution cycle 122 to produce clean hot and dry exhaust in the atmosphere with the recapture of exhaust gas water through a water condenser 123. The recaptured water can be supplied back to the pre-process or used for non-potable use of the rail vehicle. The cooler dry exhaust coming out of the activated alumina cycles can be used via a second heat exchanger 124 to provide heating or cooling on the rail vehicle.
[00194] The manufacture of fuel at the 101 methanol plant would lead, in one embodiment, to potentially two components being stored in the rail vehicle: (1) a water-methanol mixture designed to provide the correct NOX / performance result, and (2) a fumigant component in separate pressurized storage. Rail weight penalties are not large compared to boarding weight penalties.
[00195] Figure 5B, similar to Figures 3B, illustrates the process of power generation of rail vehicles without the use of fumigant, and with only preheating. The same comments on the merits of the HWL process without fumigant apply to the process described in relation to Figure 5B.
[00196] Figures 6A and 6B illustrate the concept of the generation process
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58/106 of power used for marine purposes, and for example, on a ship. Similar to the example of the HWL power generation process, a ship-sized methanol manufacturing plant can be provided on the ship to supply methanol-based fuel to one or more 111 engines that power the ship. Similar to the examples above, Figure 6A illustrates a process using fumigant ignition intensifier in the intake air while Figure 6B illustrates the process without fumigant. The process otherwise could include no preheating or preheating of the intake air.
[00197] A first heat exchanger 120 in the marine vehicle cools the exhaust air using cooler ambient air. A portion of that exhaust air can be recirculated back to become heated combustion air 110. The remaining cooled exhaust air is then passed to a misaligner 125 and other heat exchange equipment to maximize recovery of exhaust heat for vehicle needs such as tank and vehicle heating. The misaligner makes use of sea water readily available for marine vehicles.
[00198] The general advantage associated with the processes and fuels described here when used in the applications described above is that it allows the simultaneous release of various benefits to communities and regions restricted in energy and resources. Specific advantages include:
• Development of remote resources that may otherwise remain undeveloped due to inadequacy (for example, high sulfur).
• Provide uninterrupted options for efficient biomass coprocessing to reduce CO2.
• More premature biomass would extend the life of existing resources.
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59/106 • The integration of another renewable medium is also a possibility, such as wind and sun.
• Supply electricity to demand centers on a combined heat and power (CHP) or combined heat and power (CCHP) basis.
• Eliminate virtually all non-CO2 pollutants that arise from the electrical energy production stage.
• Capture hydrogen from resources to the maximum extent possible and convert these resources to water for use by demand centers (1 part of hydrogen converts under reaction with oxygen to 9 parts of water by weight). Under such arrangements, a fossil fuel resource can also be considered in part as a water resource with a potential “free shipping” effect, as the fuel release mechanism will in any case absorb its own distribution costs. This water will be treated with activated alumina or other suitable adsorption material or technology to remove breakthroughs that pass through the catalytic converter that treats the exhaust of the hot engine.
• Supply residual heat to local communities through a hot water duct (HWL) by cooling the exhaust and exchanging this main source of heat energy with local heat demand centers for heating or cooling purposes. The clean exhaust using the technology described here allows proximity to power generation to commercialize, a feature not normally available for coal power generation in particular.
• Efficiently recover water and heat. Other heat transfer approaches can be used, with increased recovery meanwhile at a higher cost, and the combustion air can also optionally be heated, for example, by circulating water
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60/106 before the vane fan cooler (in the example of Figures 3A and 3B).
• High water recovery can be achieved, around 0.7 to 1 ton of irrigation water per ton of methanol consumed, or higher if justified for economic and engineering reasons.
• Provide pH neutral irrigation water for direct use by local communities.
• Provide a water-washed exhaust that neutralizes acids and removes particulates to low levels. Other pollutants such as SOX and hydrocarbons in the exhaust will also be low.
[00199] The technology described here with water production, HWL heat integration and emission results will come at a cost in terms of engine efficiency, but this aspect is in many cases expected to be outweighed by the benefits of the supply chain and the benefits mentioned above.
EXAMPLES
EXAMPLE 1: EXPERIMENTAL PROGRAM TO INVESTIGATE METHANOL-WATER FUEL COMPOSITIONS FOR COMPRESSION IGNITION ENGINES
1.1 SUMMARY [00200] This report summarizes the results obtained during an experimental program undertaken by the University of Melbourne on performance and off-engine emissions of different fuels based on methanol in a compression ignition engine.
[00201] The fuels tested were mixtures of methanol, water, dimethyl ether (DME) and diethyl ether (DEE). Since methanol is not normally a compression ignition fuel, two ignition promoter systems were used. The first consisted of a pre
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61/106 intake air heater. By heating the engine's intake air to 150 degrees C (an imposed safety limit), higher temperatures are reached near the end of the compression stroke at which point the main fuel load is injected. In some cases, these temperatures were high enough that compression ignition of the injected fuel occurred.
[00202] The second system to promote ignition involved the continuous injection (that is, fumigation) of gaseous dimethyl ether (DME) into the engine inlet port. Because DME has a relatively low ignition temperature and a high cetane number, DME auto-ignites as the air / fumigant mixture is compressed during the compression stroke, thereby releasing thermal energy which, in turn, can ignite the charge of main fuel.
[00203] The tests were conducted on a single cylinder diesel engine, modified from Hatz 1D81 mounted on an internally built engine / absorption dynamometer facility. In its unaltered state, this naturally aspirated engine produces up to 10kW of shaft power from a single cylinder of about 670cc in volume. It is very likely that the absolute performance of all tested fuels will be better on larger engines, as it is commonly known in the engine community that peak engine efficiency increases with engine size due to fundamental physical laws.
[00204] As such, it is considered that the performance of the engine for non-diesel fuels in the current test program should be seen in relation to the result fueled with diesel in this same engine. Specifically, if comparable or better performance is achieved with an alternative fuel given in relation to diesel in this engine, it is likely that this relative performance can also be achieved in a larger engine. Of course, maximizing performance
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62/106 absolute of a given fuel in a given engine requires more optimization, and that should improve the performance of the engine.
[00205] The general observations of this experimental program are as follows.
1. Fumigated engine tests [00206] These results show that in the most efficient operating conditions, the fumigated engine produced comparable efficiency, lower NO emissions and much lower particulate emissions than the diesel engine.
2. Heated intake air tests [00207] These results show that NO emissions outside the engine are comparable to the diesel engine. As the fumigated engine runs, particulate emissions much lower than the diesel engine have been observed again. More work is required to improve the efficiency of the engine in this mode of operation.
1.2 Experimental Methods [00208] The tests were conducted on a modified 1D81 Hatz diesel engine, mounted on an internal built engine / absorption dynamometer facility. Figure 10 shows an Instrumentation Process and Diagram for the facility. The unchanged engine specifications are detailed in Table 1 below. These specifications were not changed during engine testing. [00209] The modifications made to the engine consisted of the following.
• Replacement of the mechanical fuel injector and fuel pump with a solenoidly driven injection system and separate fuel pump and injection system.
[00210] An electronically controlled common rail diesel injector was used to supply the system. This injector (Bosch, model 0 445 110 054-RE) released a volume flow rate significantly higher than the injector in the engine unchanged, so
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63/106 that fuels containing higher water content in Table 2 could be released still reaching the same air / fuel ratio as pure diesel and methanol fuels.
[00211] This injector is huge for this engine, and so it should even result in a significant reduction in engine performance when operating on the same diesel fuel as the engine unchanged. As a result, the appropriate reference for testing alternative fuels listed in Table 2 is the same modified system operating on diesel, the results of which are listed in Tables 3, 4 and 5. It is anticipated that further testing, specifically of fuels with the content of lower water, will allow the use of a smaller injector and thereby significant improvements in engine performance.
[00212] As Figure 10 shows, the fuels were mixed in a pressurized storage vessel so that the DME did not transition into the gas phase before injection into the engine. This vessel was always between 0.50 to 1 MPa (5 and 10 bars) during the test. The liquid fuel leaving this vessel was then pressurized by a Haskel, air-driven pump, up to 80 MPa (800 bars) before being injected into the engine. A high pressure accumulator was used to ensure that the pressure in the fuel line remained constant during the tests.
[00213] The flow rate of the fuel was measured by suspending the pressurized storage vessel in a load cell, and measuring the rate of change in the mass of the vessel during each test.
• Extension of the inlet piping.
[00214] This was done to connect the intake air preheater and the DME fumigation inlet. Both systems were used as ignition promoters for the main fuel charge.
• Exhaust pipe extension to connect
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64/106 all emission analysis systems.
• A Kistler piezoelectric pressure transducer.
[00215] Installed on the cylinder head of the engine to register the pressure inside the cylinder.
• Use of Shell Helix Racing 10W60 oil for all tests. [00216] This is a synthetic oil.
[00217] Exhaust emissions were analyzed using several independent systems.
• A MAHA particulate meter.
[00218] This device gives a gravimetric measurement of the particulate substance in the engine exhaust.
• A Bosch UEGO sensor.
[00219] This is a production device that measures the ratio of fuel to fuel. Although it was developed for hydrocarbon fuels, comparison with the measured air-to-fuel ratio of the ADS9000 emissions bank demonstrated that it worked well for all fuels tested other than those with more than 50% water content (Figure 4).
• An ADS9000 issuance bank.
[00220] This device measured NO emissions outside the engine. Prior to sampling, the exhaust sample is passed through unheated pipes and a water trap, so the water content of the sampled gases should be close to ambient conditions. The ADS9000 was calibrated before and during the test program using calibration gases for all measured quantities and a gas divider.
• An FTET emissions analyzer from Gasmet.
[00221] This device was calibrated using appropriate calibration gases and zeroed with high purity nitrogen according to the supplier's instruction.
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65/106 [00222] Each fuel was tested at a steady state speed of 2000 rpm and a lambda value of 2 (that is, 100% excess air). The unchanged engine operated at a lambda of about 1.5. The weakest operation was chosen since the first tests on lambda 1.5 with pure methanol resulted in seizure of the engine due to a super advanced injection in one circumstance. No engine seizing was done in lambda 2.
[00223] The general procedure of the engine under test was as follows.
1. Heated entry operations.
[00224] The intake air was first increased to 150 degrees C. [00225] The injection duration was adjusted by the lambda value of 2, and the start of the injection adjusted to top-dead-center.
[00226] The heater controller then reduced the inlet temperature while the motor was operating, until the positive torque of the motor was no longer sustained. The heater inlet controller then adjusts the inlet temperature enormously higher than when the operation ceased.
[00227] The injection start was then advanced with the dynamometer controller keeping the motor speed constant, until the motor torque reached the so-called 'maximum brake torque (MBT)'. MBT is the most efficient operating condition at constant engine speed and air / fuel ratio.
[00228] The resulting injection regulation (start and duration) and other measured quantities were recorded in this operational condition.
2. Fumigated inlet operations.
[00229] The engine was established in a smooth operating condition with a high DME flow rate.
[00230] The duration of the main fuel injection was adjusted by the lambda value of 2 and the start of the injection regulation was adjusted
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66/106 in top-dead-center.
[00231] The DME flow rate was later reduced at the same time by increasing the main fuel flow rate to keep the lambda constant, until the brake torque reached a maximum.
[00232] The start-of-injection regulation was then advanced until the MBT regulation was achieved, still continuing to adjust the main fuel flow rate to maintain the lambda, if necessary.
[00233] The resulting injection regulation (start and duration) and other measured quantities were recorded in this operational condition.
3. Diesel engine operation.
[00234] The start-of-injection regulation has been advanced to MBT while keeping the lambda at 2 through the duration of the injection.
[00235] The fuel specifications were as follows.
• Methanol, 99.8% + purity, • Deionized water, 99.8% + purity, • Dimethyl ether (DME), 98% + purity • Diethyl ether (DEE), 98% + purity
1.3 RESULTS [00236] The results of the test work are presented in the tables below.
Technical Data Units 1D81 Number of Cylinders1 Gauge x stroke [mm] 100 x 85 Displacement [L] 0.667 Average piston speed at 300 rpm [m / s] 8.5 Compression ratio20.5
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Table 1: Unchanged engine specifications
With FumigationWith Heater Main fuel composition (% by volume)Main fuel composition (% by volume) MeOH Water DME DEEMeOH Water DME DEE 100 0 0 0100 0 0 0 95 5 0 085 15 0 0 90 10 0 077.5 22.5 0 0 70 30 0 070 30 0 0 50 50 0 050 50 0 0 35 65 0 035 65 0 0 95 0 5 095 0 5 0 90 5 5 080 15 5 0 85 10 5 072.5 22.5 5 0 65 30 5 065 30 5 0 45 50 5 045 50 5 0 30 65 5 030 65 5 0 90 0 10 090 0 10 0 85 5 10 075 15 10 0 80 10 10 067.5 22.5 10 0 60 30 10 060 30 10 0 40 50 10 040 50 10 0 25 65 10 025 65 10 0 80 0 20 080 0 20 0 75 5 20 065 15 20 0 70 10 20 057.5 22.5 20 0 50 30 20 050 30 20 0 30 50 20 030 50 20 0 15 65 20 015 65 20 0 90 0 0 1090 0 0 10 85 5 0 1075 15 0 10 80 10 0 1067.5 22.5 0 10 60 30 0 1060 30 0 10 40 50 0 1040 50 0 10 25 65 0 1025 65 0 10
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Table 2: Scheme of the tested fuels (those in bold did not produce liquid work even with intake air at 150 degrees C)
Dies elPerformance Data LHVTint. Text. Time toInjection Inj duration. Lambd a Velocity Torq Potency Air flow Principle fuel DME smoke BTE (MJ / kg)° C ° C DBTDC CAD - rpm Nm kW g / s g / s g / s % 4322.4 401 4 10 2.13 1975 22.1 4.6 13.1 0.46 0 23.0%
Table 3: Diesel Performance Data
Maha and ADS 9000 issues (calculated net) Particulate AT THE AT THE Lambda mg / m ^A 3 PPm g / kWh - 140 440 4.9 1.9
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Table 4: ADS9000 Diesel Emission Data
With FumigationPerformance Data Main fuel composition (% by volume)LHVTint. Text. Inj time. Inj duration. Lambda Velocity Torque PotencyThe Current and air Main Fuel DME BTE MeOH Water DME DEEMJ / kg° C ° C CAD BTDC CAD UEGO rpm Nm kW g / s g / s g / s % 100 0 0 020.027 339 6 16 2.1 1977 18.4 3.8 12.8 0.69 0.168 20.3% 95 5 0 018.826 318 6 18 2.1 1981 18.8 3.9 12.9 0.74 0.168 20.9% 90 10 0 017.527 327 6 19 2.1 1985 17.9 3.7 12.9 0.75 0.168 20.7% 70 30 0 013.026 301 6 22 2.1 1984 16.4 3.4 12.9 0.89 0.210 19.3% 50 50 0 08.825 241 10 26 2.2 1984 12.5 2.6 12.9 1.01 0.252 16.0% 35 65 0 06.025 191 28 34 2.1 1982 10.0 2.1 12.9 1.32 0.280 12.9% 95 0 5 020.427 367 8 21 2.1 1981 20.1 4.3 12.9 0.77 0.168 20.7% 90 5 5 019.127 349 12 21 2.1 1984 20.9 4.3 12.9 0.80 0.168 21.5% 85 10 5 017.926 337 12 22 2.1 1980 20.0 4.1 12.9 0.80 0.168 21.7% 65 30 5 013.324 296 16 28 2.1 1977 18.7 3.9 12.8 1.03 0.182 20.3% 45 50 5 09.124 251 20 33 2.1 1979 14.8 3.1 12.8 1.20 0.238 17.2% 30 65 5 06.224 194 30 34 2.0 1980 10.4 2.2 12.8 1.32 0.252 13.9% 90 0 10 020.824 354 10 21 2.0 1979 21.7 4.5 12.8 0.80 0.168 20.9% 85 5 10 019.524 352 12 23 2.0 1977 22.1 4.6 12.8 0.85 0.168 21.4% 80 10 10 018.223 335 16 21 2.0 1977 21.7 4.5 12.8 0.83 0.168 22.3% 60 30 10 013.624 294 18 25 2.0 1979 18.6 3.9 12.8 0.98 0.182 20.8% 40 50 10 09.424 258 20 30 2.0 1983 15.6 3.2 12.9 1.18 0.238 18.0% 25 65 10 06.424 180 30 32 2.3 1976 8.3 1.7 12.8 1.19 0.266 11.2% 80 0 20 021.624 353 10 19 2.0 1980 22.0 4.6 12.8 0.72 0.210 21.1% 75 5 20 020.226 352 10 19 2.1 1981 21.1 4.4 12.9 0.69 0.210 21.8% 70 10 20 019.024 327 10 18 2.1 1977 19.6 4.1 12.8 0.73 0.210 20.3% 50 30 20 014.223 300 16 23 2.1 1976 17.4 3.6 12.8 0.86 0.238 18.9% 30 50 20 09.923 271 18 30 2.0 1978 15.0 3.1 12.8 1.09 0.266 16.8% 15 65 20 06.922 204 30 46 2.2 1978 10.7 2.2 12.8 1.27 0.308 12.6%
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With FumigationPerformance Data Main fuel composition (% by volume)LHVTint. Text. Inj time. Inj duration. Lambda Velocity Torque PotencyThe Current and air Main Fuel DME BTE MeOH Water DME DEEMJ / kg° C ° C CAD BTDC CAD UEGO rpm Nm kW g / s g / s g / s % 90 0 0 1021.333 377 6 16 2.1 1987 19.2 4.0 12.9 0.69 0.168 20.4% 85 5 0 1020.132 381 6 20 2.0 1986 19.5 4.1 12.9 0.74 0.168 20.6% 80 10 0 1018.831 344 10 20 2.1 1987 19.1 4.0 12.9 0.77 0.168 20.6% 60 30 0 1014.130 313 12 24 2.1 1987 17.9 3.7 12.9 0.93 0.182 20.2% 40 50 0 109.930 279 16 32 1.9 1985 16.6 3.4 12.9 1.34 0.224 17.4% 25 65 0 107.030 210 30 38 2.1 1989 11.3 2.4 12.91 1.34 0.266 13.8%
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Table 5: Performance data with DME fumigation
With HeaterPerformance Data Main fuel composition (% by volume)LHVTint. Text. Inj time. Inj duration. Lambda Velocity Torque PotencyThe Air current Main Fuel DME BTE MeOH Water DME DEEMJ / kg° C ° C CADBTDC CAD UEGO rpm Nm kW g / s g / s g / s % 100 0 0 020.0100.0 377 10 16 2.01 1988 12.2 2.5 10.4 0.73 0 17.5 85 15 0 016.4107.5 334 14 18 2.08 1992 10.6 2.2 10.3 0.79 0 17.2 77.5 22.5 0 014.6126.1 307 16 19 2.10 1991 7.4 1.5 9.8 0.84 0 12.5 95 0 5 020.4106.8 357 10 14 2.10 1987 10.6 2.2 10.3 0.61 0 17.7 80 15 5 016.7108.3 348 12 18 2.04 1983 10.6 2.2 10.2 0.74 0 17.7 72.5 22.5 5 015.0120.1 339 16 20 1.94 1981 9.5 2.0 9.9 0.83 0 15.8 90 0 10 020.8114.0 381 10 17 1.99 1988 11.1 2.3 10.1 0.65 0 17.2 75 15 10 017.0113.6 333 12 17 2.13 1987 10.1 2.1 10.1 0.72 0 17.1 67.5 22.5 10 015.28105.9 347 14 20 2.03 1989 11.2 2.3 10.3 0.86 0 17.8 80 0 20 021.6113.4 378 10 15 2.10 1989 10.6 2.2 10.1 0.60 0 17.1 65 15 20 017.7106.5 337 14 18 2.11 nineteen ninety 10.7 2.2 10.3 0.71 0 17.7 57.5 22.5 20 015.9117.8 336 16 20 2.05 1991 9.5 2.0 10.0 0.78 0 16.0 90 0 0 1021.3100.7 365 10 16 2.04 1984 12.0 2.5 10.4 0.67 0 17.5 75 15 0 1017.6111.9 327 12 17 2.15 nineteen ninety 9.9 2.1 10.1 0.72 0 16.3 67.5 22.5 0 1015.9124.6 320 14 18 2.03 1988 8.4 1.8 9.8 0.76 0 14.6
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Table 6: Performance data with heated intake air
With FumigationMaha and ADS 9000 emissions (calculated wet) Main fuel composition(% by volume)Particulate AT THE AT THE Lambda MeOH Water DME DEEmg / m ^A 3 ppm g / kWh - 100 0 0 01 106 1.5 2.0 95 5 0 01 89 1.2 2.0 90 10 0 01 37 0.1 2.0 70 30 0 01 12 0.2 2.1 50 50 0 01 11 0.2 2.2 35 65 0 01 18 0.1 2.2 95 0 5 01 57 0.7 1.9 90 5 5 01 14 11.7 1.9 85 10 5 01 83 1.1 2.0 65 30 5 01 19 0.3 2.0 45 50 5 01 19 0.4 2.1 30 65 5 01 21 0.6 2.3 90 0 10 01 99 1.2 1.9 85 5 10 01 97 1.1 1.9 80 10 10 01 192 2.3 1.9 60 30 10 01 17 0.2 2.0 40 50 10 01 12 0.2 2.1 25 65 10 01 28 0.9 2.4 80 0 20 01 111 1.3 1.9 75 5 20 01 153 1.8 1.9 70 10 20 01 88 1.1 2.0 50 30 20 01 54 0.8 2.0 30 50 20 01 9 0.2 2.0 15 65 20 01 15 0.4 2.2 90 0 0 101 92 1.2 1.9 85 5 0 101 72 0.9 1.9 80 10 0 101 65 0.9 1.9 60 30 0 101 21 0.3 2.0 40 50 0 101 15 0.2 2.0 25 65 0 101 20 0.1 2.2
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Table 7: MAHA and ADS 9000 emissions (calculated wet) with DME fumigation
With HeaterMaha and ADS 9000 emissions (calculated wet) Main fuel composition (% by volume)Particulate AT THE AT THE Lambda MeOH Water DME DEEmg / m ^A 3 PPm g / kWh - 100 0 0 01 355 5.93 2.0 85 15 0 01 158 3.02 2.0 77.5 22.5 0 01 85 2.27 2.1 95 0 5 01 356 6.65 2.1 80 15 5 01 146 2.79 2.0 72.5 22.5 5 01 100 2.09 2.0 90 0 10 01 371 6.55 2.0 75 15 10 01 136 2.67 2.1 67.5 22.5 10 01 106 1.94 2.1 80 0 20 01 358 6.54 2.1 65 15 20 01 249 4.68 2.0 57.5 22.5 20 01 139 2.90 2.0 90 0 0 101 290 4.89 2.0 75 15 0 101 187 3.73 2.1 67.5 22.5 0 101 139 3.20 2.1
Table 8: MAHA and ADS 9000 emissions (calculated wet) with heated intake air
With FumigationCombustion Analysis Main fuel composition (% by volume)IMEP PMEP PP LPP PPRR LPPRR CoV MeOH Water DME DEEkPa kPa kPa DATDC kPa / g HERE % 100 0 0 0717.5 -28.0 8466.5 6.5 357.4 -12.4 2.33% 95 5 0 0723.3 -28.6 9195.1 5.3 390.1 -2.2 3.93% 90 10 0 0701.9 -27.9 8277.2 5.9 355.4 -12.5 2.39% 70 30 0 0666.2 -27.2 8194.6 6.4 388.3 -12.9 4.10% 50 50 0 0577.2 -27.1 9624.9 3.3 490.6 -14.3 3.82% 35 65 0 0535.3 -25.5 10573.9 2.9 430.2 -6.0 3.67% 95 0 5 0776.4 -29.3 8457.0 5.7 319.4 -11.5 3.75% 90 5 5 0773.3 -29.0 9387.6 5.1 465.8 -0.8 4.16%
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With FumigationCombustion Analysis Main fuel composition (% by volume)IMEP PMEP PP LPP PPRR LPPRR CoV MeOH Water DME DEEkPa kPa kPa DATDC kPa / g HERE % 85 10 5 0756.3 -28.5 9340.8 4.9 431.3 -1.1 4.66% 65 30 5 0740.4 -28.9 9931.3 4.2 483.6 -1.4 3.46% 45 50 5 0670.0 -27.7 9767.1 4.8 395.5 -12.9 4.29% 30 65 5 0570.1 -26.9 10951.5 2.5 466.6 -4.5 4.37% 90 0 10 0775.3 -29.4 9003.2 5.5 344.9 -9.3 3.94% 85 5 10 0771.7 -29.0 9320.6 4.9 405.6 -1.7 3.47% 80 10 10 0781.8 -28.5 10387.8 4.0 548.1 -5.3 4.24% 60 30 10 0708.4 -25.1 10361.1 3.3 580.2 -4.0 3.73% 40 50 10 0656.1 -25.2 10675.0 2.5 502.5 -4.5 2.41% 25 65 10 0583.6 -26.8 10161.1 4.1 373.3 -11.5 2.92% 80 0 20 0796.8 -29.3 9159.7 5.4 352.4 -10.3 2.93% 75 5 20 0802.3 -29.9 9286.8 5.4 366.5 -12.5 3.09% 70 10 20 0755.6 -27.9 9425.7 5.2 394.6 -13.1 4.05% 50 30 20 0* 30 50 20 0* 15 65 20 0 _* 90 0 0 10738.6 -30.2 7752.5 5.7 345.2 -13.0 4.62% 85 5 0 10747.2 -29.9 8036.1 5.6 334.5 -12.9 3.67% 80 10 0 10738.3 -28.5 8916.7 5.4 344.0 -9.3 3.24% 60 30 0 10708.2 -28.3 9197.5 4.7 365.3 -8.1 3.90% 40 50 0 10664.7 -26.6 9777.8 3.7 417.9 -14.2 3.90% 25 65 0 10572.4 -24.5 10794.8 2.9 468.6 -3.8 4.35%
* These inputs were unavailable due to the failure of the pressure transducer during the test.
Table 9: Combustion analysis data with DME fumigation
With HeaterCombustion Analysis Main fuel composition (% by volume)IMEP PMEP PP LPP PPRR LPPRR CoV MeOH Water DME DEEkPa kPa kPa DATDC kPa / g HERE % 100 0 0 0523.4 -21.5 7614.1 5.9 373.2 -0.4 4.72% 85 15 0 0517.1 -21.3 7900.8 5.7 481.3 0.1 4.42% 77.5 22.5 0 0431.0 -17.0 7420.6 5.6 390.8 0.0 4.11% 95 0 5 0531.3 -20.4 7402.2 6.4 370.7 0.9 4.36%
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With HeaterCombustion Analysis Main fuel composition (% by volume)IMEP PMEP PP LPP PPRR LPPRR CoV MeOH Water DME DEEkPa kPa kPa DATDC kPa / g HERE % 80 15 5 0556.3 -21.7 7440.1 5.8 382.4 1.6 5.22% 72.5 22.5 5 0505.6 -19.8 7963.9 4.9 524.1 -1.1 3.90% 90 0 10 0528.6 -20.3 7391.3 6.0 381.6 1.7 5.22% 75 15 10 0505.3 -20.3 7408.9 5.7 399.9 0.9 4.20% 67.5 22.5 10 0486.5 -19.4 7595.2 5.6 440.6 0.1 4.64% 80 0 20 0535.7 -19.9 7089.4 5.9 328.3 -0.8 4.08% 65 15 20 0554.7 -20.2 7807.8 5.8 466.6 -0.3 4.17% 57.5 22.5 20 0489.6 -18.8 7861.2 4.7 509.5 -1.4 4.54% 90 0 0 10557.2 -21.6 7493.1 6.5 384.3 1.6 3.75% 75 15 0 10511.9 -20.9 7585.1 6.6 406.1 2.8 4.66% 67.5 22.5 0 10478.7 -20.3 7636.8 5.2 464.9 -0.9 3.50%
Table 10: Combustion analysis data with heated intake air
1.5 Other test work [00237] Another test work was conducted to explore combinations of fuel and additional fumigant, and the results of those tests are summarized in Tables 11 and 12 below. Of note is the following:
• In general, engine efficiencies at 1000rpm are lower than for the same or similar fuels at higher engine speeds. This is based on the fact that the unchanged Hatz engine had peak efficiency at about 2000 rpm, and would be expected. When used on larger engines designed for peak efficiency at a lower rpm, efficiencies using fuels would be improved.
• NO emissions using the ADS9000 device are not displayed due to the failure of this sensor during this test program.
• The fuel injector failed during test number 25. The data recorded for this test still seemed to be reasonable,
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76/106 since the failure was late in the test, and so is included in this Addendum. Of note is the comparative performance of operations 25 and 27, which have a very similar main fuel composition, different from additives.
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Fumigated Operation No. Principal% by Volume Weight AdditivesMain fuel composition with additives (% by mass)MeOH EthOH Water DME DEE Formal. Aspro. OtherMeOH EthOH Water DME DEE Formal. Aspro. Other 22 70 0 30 0 0 0 0 064.9 0.0 35.1 0 0 0 0 0 23 70 0 30 0 0 0 0 064.9 0.0 35.1 0 0 0 0 0 24 70 0 30 0 0 0 0 064.9 0.0 35.1 0 0 0 0 0 25 - - - 0 0 0 2.5 0.493.2 0.0 3.9 0 0 0 2.5 0.4 27 - - - 0 0 2 0 0.493.7 0.0 3.9 0 0 2 0 0.4 28 - - - 0 0 0 0 0.479.7 0.0 19.9 0 0 0 0 0.4 29 - - - 0 0 0 0 040 0.0 60.0 0 0 0 0 0.0 30 - - - 0 0 0 0 093 0.0 7.0 0 0 0 0 0.0 4rep 70 0 30 0 0 0 0 064.9 0.0 35.1 0 0 0 0 0
90L / ZZ
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Table 11: Performance data with DME fumigation
Performance data Operation No. Tint. Text. Time toInjection Lambda Velocity Torquand Wattage Air current FuelMain DME BTEdegrees C degrees C CAD BTDC UEGO rpm Nm kW g / s g / s g / s % 22 39 209 0 2.1 1000 9.1 1.0 6.3 0.41 0.047 14.4% 23 56 214 0 2.0 998 8.3 0.9 5.9 0.41 0.039 13.4 24 81 216 0 2.1 999 4.8 0.1 5.5 0.38 0.032 8.6 25 32 228 0 2.0 992 12.1 1.3 6.4 0.31 0.05 17.5% 27 26 233 0 2.1 994 12.3 1.3 6.5 0.32 0.043 17.6% 28 26 220 0 2.1 993 10.8 1.1 6.5 0.34 0.056 16.0% 29 26 193 0 2.1 990 7.0 0.7 6.5 0.12 0.102 10.2% 30 78 339 0 2.1 1978 11.1 2.3 11.0 0.67 0.106 14.7% 24rep 83 224 0 2.0 995 5.9 0.6 5.5 0.39 0.031 10.4%
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Table 11 (cont.): Performance data with DME fumigation
Maha and ADS 9000 emissions (calculated wet) Operation Particulate AT THE AT THE Lambda No. mg / m ^A 3 PPm g / kWh - 22 1 - - 2.1 23 1 - - 2.2 24 1 - - 2.1 25 1 - - 1.9 27 1 - - 2.1 28 1 - - 2.1 29 1 - - 2.1 30 1.2 - - 2.124rep 1 - - 2.0
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Table 11 (cont.): Performance data with DME fumigation
WithHeaterOption Principal% by Volume Weight AdditivesMain fuel composition with additives (% by mass) No. MeOH EthOH Water DME DEE Formal. Aspro. OtherMeOH EthOH Water DME DEE Formal. Aspro. Other 3 70 0 30 5 0 0 0 061.7 0.0 33.3 5 0 0 0 0 6 70 0 30 0 8 0 0 059.7 0.0 32.3 0 8 0 0 0 7 70 0 30 0 20 0 0 051.9 0.0 28.1 0 20 0 0 0 8 70 0 30 20 0 0 0 051.9 0.0 28.1 20 0 0 0 0 11 70 0 30 0 0 4 0 062.3 0.0 33.7 0 0 4 0 0 18 70 0 30 0 0 1 0 064.3 0.0 34.7 0 0 1 0 0 21 20 50 30 5 0 0 0 017.5 44.3 33.2 5 0 0 0 0
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Table 12: Performance data with heated intake air
Performance data Operation No. Tint. Text. Time toInjection Lambda velocity Torque Wattage Air current Main Fuel DME BTEdegrees C degrees C CAD BTDC UEGO rpm Nm kW g / s g / s g / s % 3 141.1 229.2 0 2.06 995 3.4 0.4 4.7 0.41 - 6.5% 6 154.7 229 0 2.08 993 2.0 0.2 4.6 0.33 - 4.2% 7 155.4 237 0 2.09 991 2.3 0.2 4.5 0.29 - 4.7% 8 149.6 244 0 2.02 996 3.2 0.3 4.6 0.32 - 6.3% 11 didn't burn 18 didn't burn 21 150.8 246 0 2.03 994 3.2 0.3 4.6 0.28 - 7.0%
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Table 12 (cont.): Performance data with heated intake air
Maha and ADS 9000 emissions (calculated wet) Operation Particulate AT THE AT THE Lambda No. mg / m ^A 3 ppm g / kWh - 3 1 - - 2.0 6 1 - - 2.2 7 1 - - 2.2 8 1 - - 2.1 11 - - - - 18 - - - - 21 1 - - 2.1
Table 12 (cont.): Performance data with heated intake air
1.5 Comparison tables between% by volume and% by mass in fuel compositions [00238] The tables in the test results outlined in 1.1 to 1.4 above are based on the relative quantities of the components in the main fuel composition measured by volume. The following tables 13 and 14 allow a conversion to be made between% volume and weight for the fuel compositions.
With Fumigation Main fuel composition (% by volume)Main fuel composition (% by mass) MeOH Water DME DEEMeOH Water DME DEE 100 0 0 0100.0 0.0 0.0 0.0 95 5 0 093.8 6.2 0.0 0.0 90 10 0 087.7 12.3 0.0 0.0 70 30 0 064.9 35.1 0.0 0.0 50 50 0 044.2 55.8 0.0 0.0 35 65 0 029.9 70.1 0.0 0.0 95 0 5 095.8 0.0 4.2 0.0 90 5 5 089.5 6.3 4.2 0.0
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With Fumigation Main fuel composition (% by volume)Main fuel composition(% in large scale) MeOH Water DME DEEMeOH Water DME DEE 85 10 5 083.4 12.4 4.1 0.0 65 30 5 060.7 35.4 3.9 0.0 45 50 5 040.0 56.2 3.8 0.0 30 65 5 025.8 70.6 3.6 0.0 90 0 10 091.4 0.0 8.6 0.0 85 5 10 085.2 6.3 8.5 0.0 80 10 10 079.1 12.5 8.3 0.0 60 30 10 056.4 35.7 7.9 0.0 40 50 10 035.8 56.6 7.6 0.0 25 65 10 021.6 71.1 7.3 0.0 80 0 20 082.6 0.0 17.4 0.0 75 5 20 076.4 6.4 17.2 0.0 70 10 20 070.3 12.7 16.9 0.0 50 30 20 047.7 36.2 16.1 0.0 30 50 20 027.3 57.4 15.3 0.0 15 65 20 013.2 72.1 14.8 0.0 90 0 0 1090.9 0.0 0.0 9.1 85 5 0 1084.7 6.3 0.0 9.0 80 10 0 1078.7 12.4 0.0 8.9 60 30 0 1056.1 35.5 0.0 8.4 40 50 0 1035.6 56.3 0.0 8.0 25 65 0 1021.5 70.7 0.0 7.8
Table 13: Comparison tables between% by volume and% by mass - Fumigation
With Heater Main fuel composition (% by volume)Main fuel composition (% by mass) MeOH Water DME DEEMeOH Water DME DEE 100 0 0 0100.0 0.0 0.0 0.0 85 15 0 081.8 18.2 0.0 0.0 77.5 22.5 0 073.2 26.8 0.0 0.0 95 0 5 095.7 0.0 4.3 0.0
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With Heater Main fuel composition (% by volume)Main fuel composition (% by mass) MeOH Water DME DEEMeOH Water DME DEE 80 15 5 077.6 18.3 4.1 0.0 72.5 22.5 5 069.0 27.0 4.0 0.0 90 0 10 091.4 0.0 8.6 0.0 75 15 10 073.3 18.5 8.2 0.0 67.5 22.5 10 064.7 27.2 8.1 0.0 80 0 20 082.6 0.0 17.4 0.0 65 15 20 064.5 18.8 16.8 0.0 57.5 22.5 20 055.9 27.6 16.4 0.0 90 0 0 1090.9 0.0 0.0 9.1 75 15 0 1072.9 18.4 0.0 8.8 67.5 22.5 0 1064.3 27.1 0.0 8.6
Table 14: Comparison tables between% by volume and% by mass - Preheating of the intake air
1.6 Observations on the test results reported in sections 1.1 to 1.5 [00239] DME water and ether plus fumigant:
[00240] The work reported above demonstrates that water has some fundamental properties that make it a useful addition to a methanol fuel:
[00241] 1. If injected with methanol fuel, to some extent, it does not decrease efficiency, but otherwise it increases to an optimum point, and then decreases as the proportion of water continues to rise. It has been postulated by the applicants that the increase in efficiency may be due to a combination of factors such as the following factors:
The. the spectral properties of water such as emissivity and absorption coefficient are superior to methanol on the other side of the heating band (for example, infrared IR) which helps in absorbing radiant heat in the droplets
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85/106 of mixed fuel and water while methanol evaporates from the droplet at an accelerated rate, since methanol would share this higher rate of heat absorption and vaporize first.
[00242] The emissivity of water is reported in the literature to be between 0.9 and 1.0 that is, almost a black body for infrared radiation, while methanol is less than half of that value close to 0.4.
B. The thermal conductivity of water is greater than methanol
ç. The thermal diffusivity of water is greater than methanol.
d. Points b. and c. above would lead to greater heat transfer within a droplet with water present, again accelerating the conversion of methanol from liquid to gas as the methanol concentration decreases as the droplets shrink:
Thermal diffusivity mm ² / s Thermal conductivity W / Km 100% methanol 0.103 0.199 75% methanol 0.102 0.250 50% methanol 0.106 0.340 25% methanol 0.118 0.470 100% water 0.149 0.605
[00243] Taken from Thermochimica Acta 492 (2009) pgs. 95-100 [00244] 2. The work reported above provides evidence of the viability of a water-methanol fuel by demonstrating its smooth operation when operating even at high water levels with an adequate amount of ignition aid in terms of fumigant. From the data presented in Figure 7, which are derived from the work reported above, it is shown that there is a peak thermal efficiency at rupture achieved when the water content is in the range of about 12% to 23% by weight of the main fuel composition . The improved BTE zone is for water content between 2% and 32%, with an optimum being achieved in the region of around 16-18% with DME fumigant. This was an amazing result. It was unexpected that injecting such
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86/106 high water levels in the combustion chamber would allow a compression ignition engine to operate with acceptable operation in terms of IMEP VOCs. (coefficient of variation of the average effective pressure indicated).
[00245] From the experimental data reported above, an under-rated BTE performance in most cases was undiluted methanol, with good performance obtained by mixtures that included DME in the 4-9% weight range.
[00246] As the water content went beyond about 30% by weight in fuels that contained the previously mentioned amounts of DME, efficiency dropped back to levels that were consistent with fuels being combusted without water present.
[00247] It was noted that the fuels of about 70% of water burned in the engine, although in half the efficiency due in part to the higher exhaust water content.
[00248] Figure 8 provides a graphical representation of the ether content of the main fuel, in% by weight, and the consequent BTE of the fuel. The key (}) is used to mark the points related to the use of diethyl ether as the ether component in the fuel composition, while the ether used at the other points represented in the graph was dimethyl ether. Figure 8 indicates an increase in BTE of little 1.5% by introducing 4% DME in the liquid phase in approximately 16% water content, compared to the case of undiluted methanol. In general, the results provided through the use of an amount of ether inside the box shown by a dotted line provide advantages over the main fuel composition. Increasing the ether content above the 10% level (that is, outside the box to the right of the figure) adds additional cost without an improvement in the corresponding process or advantage.
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87/106 [00249] At low water levels, the benefits of 16% DME compared to 4% were small, and 4% DME exceeded 16% DME in water contents higher than about 6%.
[00250] Approximately 8% DME by weight had BTE slightly higher than 4% DME over the water content range, the difference ranging from about 0.3% to a maximum of about 36% of water in fuel .
[00251] Diethyl ether (DEE, points between braces) in fuel showed a weaker BTE in the lower water ranges where the performance was similar to pure methanol, however when the water content in the fuel rose above about 25% DEE to about 8% improved their performance to match that of DME.
[00252] In terms of Thermal Efficiency the DEE Brake could not be selected ahead of DME in a methanol-water fuel unless other reasons such as volatility or vapor pressure prevail.
[00253] Effect of water and fumigant on NO:
[00254] In a fumigated environment where a coolant such as water is applied, it could not be predicted that a NO reduction would be achieved and the extent of NOA reduction could not be predicted. The test work shows that the NO reduction was quite dramatic as the water levels increased, showing a vat of 0.2 gram / kw-h at 36% by weight of water, as shown in Figure 9.
[00255] Figure 10 provides another illustration of the effect that increasing water content has using NOX in the exhaust. The DME lines of 4% and 8% showed the best response even for NOX formation at high intake air temperatures. The same trend can be seen in the case of fumigation, where NOX decreases as water levels increase 16.5% DME and 8.8%
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DEE showed higher levels of NO compared to low cases of DME. All heated operations without water produced NO higher than diesel fuel without preheating.
[00256] From the data and Figures above attached it is evident that an operational merit zone involves the use of a main fuel composition comprising methanol and 20-22% by weight water and 4-6% w. DME in the main fuel composition, with fumigation. This fuel would achieve good efficiency and low NO. The desirable fuel operation zone can be further expanded with acceptable operation of the CI engine, as described in detail in other sections of this patent application.
[00257] Diesel fuel in the same engine in contrast reached 4.9 grams / kw-h in lambda 2 and 2000 rpm (the lambda and the speed of all the fumigation tests in these charts) [00258] Fumigant:
[00259] The use of a fumigant (or fumigation) has not previously been considered with complex fuel compositions, particularly with fuel compositions comprising water and methanol, and optionally with other additives such as DME. There has certainly been no report of commercial acceptance of such techniques. This may be due to the fact that such a fuel could have been considered unlikely to work well, given the low heating value of methanol which is further impaired by mixing it with a high latent heat diluent such as water. The use of a fuel containing a large water component is also counterintuitive since water is normally used to put out a fire instead of helping to burn.
[00260] To investigate this space, a single cylinder engine with similar capacity to that of a cylinder of a 5-liter 8 V engine was used, with larger injectors installed to overcome the value of
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89/106 low heating per liter of some of the fuels to be tested.
[00261] These larger injectors had the effect of reducing the efficiency of the engine, however as a comparison between the fuels, the inverted conditions provided were applied, the validity of the comparisons was recognized by the engine test professionals.
[00262] Huge injectors were required under the specific operating conditions of the test, and the engine was operated at high rpm due to the small engine size, but more work would allow modification of these factors, this with a consequent reduction in the relative amount of fumigant (fuel intensifier). ignition) injected into the engine intake air. The experimental work carried out to support this application was carried out at 2000 rpm and 1000 rpm, the latter being the lowest operable speed of the Hatz engine used for the program.
EXAMPLE 2: FUEL 70% METHANOL: 30% WATER WITH METHOD OF HEATING THE AIR INTAKE AND FUMIGANT OPERATION [00263] A fuel containing 70% methanol and 30% water is introduced into the combustion ignition engine schematically represented in Figure 1.
[00264] During different stages of engine operation (start, steady state at low load, steady state at 50% -100% full load, idle, and so on), the engine can be operated in different modes, and in combinations of modes.
[00265] During operation at 0-50% of engine load, the intake air is preheated to between 150-200 ° C without a smoker present. The loss of air flow to the engine at high temperature is compensated for by the engine that is under low load.
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90/106 [00266] In the case of 50% for full load operation, the preheating of the intake air level can be reduced, and in addition a fumigant comprising 95% DME, 3% methanol and 2% water can to be used.
[00267] Fumigant is injected into the intake air, in an amount of 5% p. total fuel intake. This level of fumigation can be decreased when the full charge is approached.
[00268] At the start, the intake air can be preheated, and in addition a greater% by weight of fumigant with respect to the main fuel is fumigated at the air intake. A fumigant suitable for this stage of operation is 20% -50% of a fumigant comprising 100% DME.
[00269] In idle state after the engine is run, the fumigation can be discontinued.
[00270] Preheating the air inlet, with periodic fumigation assistance (subject to engine rpm and load), allows the engine operation to overcome the presence of water at the level of 30% in the main fuel composition.
EXAMPLE 3: 95% METHANOL FUEL: 5% WATER, WITH HEATING AND NO FUMIGATION [00271] Example 2 is repeated but with a fuel composition of 95% methanol and 5% water. Inlet air is preheated to between 150 ° C and 200 ° C. Such an arrangement may include a turbocharger and exhaust / inlet heat exchanger.
EXAMPLE 4: 26% METHANOL: 74% WATER WITH
HEATING AND FUMIGATION [00272] Example 3 is repeated but with a fuel composition of 26% methanol, 74% water. This fuel composition may be suitable for use in marine applications
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91/106 to operate IC ship engines. In this case, sea water can be used as the heat collector if necessary to obtain the required level of exhaust gas condensation. To ensure safety in enclosed spaces through the presence of a non-flammable vapor phase under spillage, the water level in the fuel composition is about 74% in a marine situation, (or more), with 26% (or less) of the fuel being methanol. This high water content avoids the risk of ignition that causes sparks in the engine space.
[00273] The fuel is the Example that can be pumped into the main fuel storage tank in a ready-to-use composition (ie, with 74% water in the methanol composition). Alternatively, a premix having a lower water level (compared to the engine usage composition) can be pumped into the storage tank, and the water level increased by diluting water from the final premix between storage and charging for the engine. The water source can be any source of water, and it can be, for example, recycled water, or desalinated water. This option has advantages with respect to the weight of the fuel composition continued in the vessel.
[00274] Ignition of this fuel requires heating methods as described above. Steam or spray of DME fumigated at the air inlet provides sufficient means to ignite the fuel.
[00275] The amount of water in the exhaust gas can be estimated to be between about 30-50%. This is based on the original water in the fuel and water that comes from combustion of methanol, and DME, as well as water in the intake air. This surprisingly high result arises from the high hydrogen content of methanol (containing more hydrogen on a volume basis than cryogenic liquid hydrogen), combined with the high water content in the fuel, water vapor in the air intake and
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92/106 water combustion of fuels (methanol and DME).
[00276] With this combustion reaction there will be an excess of water generated and the opportunity exists to capture a portion of it for recycling and mixing it with a premix fuel with a lower water content stored in the storage tank. In some modalities, it is advantageous to reduce the supply chain logistics costs associated with the presence of water in the fuel by transporting a base fuel with a higher methanol content, and satisfying the engine's target quality at higher water levels by capturing engine exhaust water.
[00277] A heat exchange and spray chamber arrangement using pure water with optional additives to remove the selected species in the final stage can be configured to ensure that non-CO2 pollution from methanol combustion is low. In addition, a final cleaning of the exhaust gas can be achieved by adsorption, for example, of unburned methanol on the activated surfaces, for further desorption and recycling to the engine within the process using known techniques, or to incorporate as part of the fumigant. or main fuel.
[00278] In terms of SOX, the exhaust gas in this case can have the following analysis:
SOX <0.1 ppm.
[00279] In general, emissions of other pollutants such as NOX particulates will be much lower compared to diesel fuels based on oil.
[00280] Any small amounts of NOX and SOX formed in the combustion phase, and the absorption of CO2 in the water phase, can result in weak acidification of the water returning to the mixture with the fuel. The return water mixture may need chemical treatment or mechanical adjustment to compensate for this weak acidification.
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93/106 [00281] The exhaust gas resulting from such cleaning has improved emissions compared to diesel fuel in terms of fuel, hydrocarbon, particulate, NOX and SOX emissions, which is environmentally advantageous.
[00282] CO2 recovery [00283] The exhaust resulting from the high water fuel contains almost no impurity, making it ideal for further processing. In particular, CO2 is converted back to methanol to directly reduce greenhouse gas CO2 or high purity CO2 can be used for organic growth such as algae for multiple end uses including methanol making, using energy sources that can include renewable sources, such as solar, and so on.
[00284] Separation or purification of the oxygen level in the air, nitrogen can be reduced or eliminated from the engine with the reduction or elimination resulting from the NOX potential of nitrogen oxidation. Recycling the exhaust CO2 for the intake of O2 in the engine afterwards will allow optimization of the level of oxygen entering the engine and the generation of a vastly pure CO2 water vapor exhaust. This enriched CO2 is ideal for further processing with methanol or the above applications if desired.
EXAMPLE 5: 90% METHANOL FUEL: 5% WATER: 15% DME, WITH HEATING AND NO FUMIGATION [00285] Example 2 is repeated, but with DME added to the main fuel methanol-water fuel composition. Inlet air is preheated to between 50 ° C and 150 ° C. Such an arrangement may include a turbocharger and exhaust / intake air heat exchanger. The degree of preheating required can be low or zero in the highest load range, with modest preheating
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94/106 required at lower load and lower engine speed.
EXAMPLE 6: FUEL COMPOSITIONS FOR USE WITH HEATING METHODS, WITH OPTIONAL FUMIGANTS [00286] In the following table, examples of methanol / water fuel compositions are outlined for the operation of combustion ignition engines with preheating of the intake air. These methanol / water fuel compositions can be operated with inlet air preheating to a level of at least 50 ° C or at least 100 ° C or at least 150 ° C or at least 200 ° C or at least 250 ° C or at least 300 ° C or higher (depending on prevailing conditions). Fuel compositions can additionally (or alternatively to preheat inlet air) be used in combination with a fumigant, and examples of fumigants suitable for fuels are shown in the second part of the table. The main fuel for each numbered line can be paired with a suitable fumigant on the same numbered line, although pairs between fuels and neighboring fumigants are possible. Regarding the identity of the fuel extenders, lubricants, ignition enhancers and other additives, these are selected from the examples provided in the detailed description above. The% of quantity referred to in the table for these additives refers to the quantity of a simple additive of that description, or the total of additives of that description when a combination of more than one such additive of that class is used. Specific examples use sugar ester or fatty acid as a fuel extender, fatty acid ester or ethanolamine derivative as a lubricity additive, ether as an ignition enhancer, and product color and flame color additives as the additional additive.
[00287] Several fumigants are indicated in the tables, some
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95/106 decrease in their ignition properties than those classified as superior ignition components. The components listed are not exhaustive, other suitable components listed elsewhere in this document and known to those skilled in the art can also be used.
Integral Fuel Base (%P.) Additive class 1 Class ofAdditives 2 Class ofAdditives 3 Class ofAdditives 4 Fuel Extenders Lubricants Ignition Enhancers OtherWater% Methanol% Additions% MAIN FUEL 1. 0.2 91.15 8.65 0.15 1.5 5 2 2. 0.2 89.65 10.15 0.15 3 5 2 3. 0.2 87.65 12.15 0.15 5 5 2 4. 0.2 91.15 8.65 0.15 1.5 5 2 5. 0.2 89.65 10.15 0.15 3 5 2 6. 0.2 81.65 18.15 0.15 5 10 3 7. 0.2 85.15 14.65 0.15 1.5 10 3 8. 0.2 83.65 16.15 0.15 3 10 3 9. 0.2 81.65 18.15 0.15 5 10 3 10. 0.2 85.15 14.65 0.15 1.5 10 3 11. 1 82.85 16.15 0.15 3 10 3 12. 1 94.35 4.65 1.15 1.5 0 2 13. 1 90.85 8.15 2.15 3 0 3 14. 1 88.85 10.15 3.15 5 0 2 15. 1 90.35 8.65 4.15 1.5 0 3 16. 1 88.85 10.15 5.15 3 0 2 17. 1 79.85 19.15 6.15 5 5 3 18. 1 83.35 15.65 7.15 1.5 5 2 19. 1 79.85 19.15 8.15 3 5 3 20. 1 75.85 23.15 9.15 5 5 4 21. 5 73.35 21.65 10.15 1.5 5 5 22. 5 90.35 4.65 1.15 1.5 0 2 23. 5 87.85 7.15 2.15 3 0 2 24. 5 84.85 10.15 3.15 5 0 2 25. 5 82.35 12.65 4.15 1.5 5 2 26. 5 79.85 15.15 5.15 3 5 2
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Integral Fuel Base (%P.) Additive class 1 Class ofAdditives 2 Class ofAdditives 3 Class ofAdditives 4 Fuel Extenders Lubricants Ignition Enhancers OtherWater% Methanol% Additions% MAIN FUEL 27. 5 70.85 24.15 6.15 5 10 3 28. 5 73.35 21.65 7.15 1.5 10 3 29. 5 65.85 29.15 8.15 3 15 3 30. 5 62.85 32.15 9.15 5 15 3 31. 10 55.35 34.65 10.15 1.5 20 3 32. 10 82.85 7.15 1.15 3 0 3 33. 10 84.35 5.65 2.15 1.5 0 2 34. 10 80.85 9.15 3.15 3 0 3 35. 10 73.85 16.15 4.15 5 5 2 36. 10 75.35 14.65 5.15 1.5 5 3 37. 10 68.85 21.15 6.15 3 10 2 38. 10 64.85 25.15 7.15 5 10 3 39. 10 63.35 26.65 8.15 1.5 15 2 40. 10 59.85 30.15 9.15 3 15 3 41. 15 45.85 39.15 10.15 5 20 4 42. 15 77.35 7.65 1.15 1.5 0 5 43. 15 79.35 5.65 2.15 1.5 0 2 44. 15 76.85 8.15 3.15 3 0 2 45. 15 68.85 16.15 4.15 5 5 2 46. 15 71.35 13.65 5.15 1.5 5 2 47. 15 63.85 21.15 6.15 3 10 2 48. 15 59.85 25.15 7.15 5 10 3 49. 15 57.35 27.65 8.15 1.5 15 3 50. 15 54.85 30.15 9.15 3 15 3 51. 20 41.85 38.15 10.15 5 20 3 52. 20 74.35 5.65 1.15 1.5 0 3 53. 20 71.85 8.15 2.15 3 0 3 54. 20 73.35 6.65 3.15 1.5 0 2 55. 20 64.85 15.15 4.15 3 5 3 56. 20 62.85 17.15 5.15 5 5 2 57. 20 59.35 20.65 6.15 1.5 10 3 58. 20 57.85 22.15 7.15 3 10 2 59. 20 48.85 31.15 8.15 5 15 3
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Integral Fuel Base (%P.) Additive class 1 Class ofAdditives 2 Class ofAdditives 3 Class ofAdditives 4 Fuel Extenders Lubricants Ignition Enhancers OtherWater% Methanol% Additions% MAIN FUEL 60. 20 52.35 27.65 9.15 1.5 15 2 61. 25 38.85 36.15 10.15 3 20 3 62. 25 64.85 10.15 1.15 5 0 4 63. 25 66.35 8.65 2.15 1.5 0 5 64. 25 68.35 6.65 3.15 1.5 0 2 65. 25 60.85 14.15 4.15 3 5 2 66. 25 57.85 17.15 5.15 5 5 2 67. 25 55.35 19.65 6.15 1.5 10 2 68. 25 52.85 22.15 7.15 3 10 2 69. 25 43.85 31.15 8.15 5 15 3 70. 25 46.35 28.65 9.15 1.5 15 3 71. 30 33.85 36.15 10.15 3 20 3 72. 30 60.85 9.15 1.15 5 0 3 73. 30 63.35 6.65 2.15 1.5 0 3 74. 30 60.85 9.15 3.15 3 0 3 75. 30 57.35 12.65 4.15 1.5 5 2 76. 30 53.85 16.15 5.15 3 5 3 77. 30 46.85 23.15 6.15 5 10 2 78. 30 48.35 21.65 7.15 1.5 10 3 79. 30 41.85 28.15 8.15 3 15 2 80. 30 37.85 32.15 9.15 5 15 3 81. 40 26.35 33.65 10.15 1.5 20 2 82. 40 38.85 21.15 5.15 3 10 3 83. 40 29.85 30.15 6.15 5 15 4 84. 40 26.35 33.65 7.15 1.5 20 5 85. 50 27.85 22.15 5.15 5 10 2 86. 50 24.35 25.65 6.15 1.5 15 3 87. 50 17.85 32.15 7.15 3 20 2 88. 60 16.85 23.15 5.15 5 10 3 89. 60 18.35 21.65 6.15 1.5 10 4 90. 60 17.85 22.15 7.15 5 5 5 91. 10 55.35 34.65 10.15 1.5 20 3 92. 10 82.85 7.15 1.15 3 0 3
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Integral Fuel Base (%P.) Additive class 1 Class ofAdditives 2 Class ofAdditives 3 Class ofAdditives 4 Fuel Extenders Lubricants Ignition Enhancers OtherWater% Methanol% Additions% MAIN FUEL 93. 10 84.35 5.65 2.15 1.5 0 2 94. 10 80.85 9.15 3.15 3 0 3 95. 10 73.85 16.15 4.15 5 5 2 96. 10 75.35 14.65 5.15 1.5 5 3 97. 10 68.85 21.15 6.15 3 10 2 98. 10 64.85 25.15 7.15 5 10 3 99. 10 63.35 26.65 8.15 1.5 15 2 100. 10 59.85 30.15 9.15 3 15 3 101. 15 45.85 39.15 10.15 5 20 4 102. 15 77.35 7.65 1.15 1.5 0 5 103. 15 79.35 5.65 2.15 1.5 0 2 104. 15 76.85 8.15 3.15 3 0 2 105. 15 68.85 16.15 4.15 5 5 2 106. 15 71.35 13.65 5.15 1.5 5 2 107. 15 63.85 21.15 6.15 3 10 2 108. 15 59.85 25.15 7.15 5 10 3 109. 15 57.35 27.65 8.15 1.5 15 3 110. 15 54.85 30.15 9.15 3 15 3 111. 20 41.85 38.15 10.15 5 20 3 112. 20 74.35 5.65 1.15 1.5 0 3 113. 20 71.85 8.15 2.15 3 0 3 114. 20 73.35 6.65 3.15 1.5 0 2 115. 20 64.85 15.15 4.15 3 5 3 116. 20 62.85 17.15 5.15 5 5 2 117. 20 59.35 20.65 6.15 1.5 10 3 118. 20 57.85 22.15 7.15 3 10 2 119. 20 48.85 31.15 8.15 5 15 3 120. 20 52.35 27.65 9.15 1.5 15 2 121. 25 38.85 36.15 10.15 3 20 3 122. 25 64.85 10.15 1.15 5 0 4 123. 25 66.35 8.65 2.15 1.5 0 5 124. 25 68.35 6.65 3.15 1.5 0 2 125. 25 60.85 14.15 4.15 3 5 2
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Integral Fuel Base (%P.) Additive class 1 Class ofAdditives 2 Class ofAdditives 3 Class ofAdditives 4 Fuel Extenders Lubricants Ignition Enhancers OtherWater% Methanol% Additions% MAIN FUEL 126. 25 57.85 17.15 5.15 5 5 2 127. 25 55.35 19.65 6.15 1.5 10 2 128. 25 52.85 22.15 7.15 3 10 2 129. 25 43.85 31.15 8.15 5 15 3 130. 25 46.35 28.65 9.15 1.5 15 3 131. 30 33.85 36.15 10.15 3 20 3 132. 30 60.85 9.15 1.15 5 0 3 133. 30 63.35 6.65 2.15 1.5 0 3 134. 30 60.85 9.15 3.15 3 0 3 135. 30 57.35 12.65 4.15 1.5 5 2 136. 30 53.85 16.15 5.15 3 5 3 137. 30 46.85 23.15 6.15 5 10 2 138. 30 48.35 21.65 7.15 1.5 10 3 139. 30 41.85 28.15 8.15 3 15 2 140. 30 37.85 32.15 9.15 5 15 3 141. 40 23.85 36.15 10.15 3 20 3 142. 40 50.85 9.15 1.15 5 0 3 143. 40 53.35 6.65 2.15 1.5 0 3 144. 40 50.85 9.15 3.15 3 0 3 145. 40 47.35 12.65 4.15 1.5 5 2 146. 40 43.85 16.15 5.15 3 5 3 147. 40 36.85 23.15 6.15 5 10 2 148. 40 38.35 21.65 7.15 1.5 10 3 149. 40 31.85 28.15 8.15 3 15 2 150. 40 27.85 32.15 9.15 5 15 3 151. 50 13.85 36.15 10.15 3 20 3 152. 50 40.85 9.15 1.15 5 0 3 153. 50 43.35 6.65 2.15 1.5 0 3 154. 50 40.85 9.15 3.15 3 0 3 155. 50 37.35 12.65 4.15 1.5 5 2 156. 50 33.85 16.15 5.15 3 5 3 157. 50 26.85 23.15 6.15 5 10 2 158. 50 28.35 21.65 7.15 1.5 10 3
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Integral Fuel Base (%P.) Additive class 1 Class ofAdditives 2 Class ofAdditives 3 Class ofAdditives 4 Fuel Extenders Lubricants Ignition Enhancers OtherWater% Methanol% Additions% MAIN FUEL 159. 50 21.85 28.15 8.15 3 15 2 160. 50 17.85 32.15 9.15 5 15 3 161. 60 15.85 24.15 10.15 3 8 3 162. 60 30.85 9.15 1.15 5 0 3 163. 60 33.35 6.65 2.15 1.5 0 3 164. 60 30.85 9.15 3.15 3 0 3 165. 60 27.35 12.65 4.15 1.5 5 2 166. 60 23.85 16.15 5.15 3 5 3 167. 60 16.85 23.15 6.15 5 10 2 168. 60 18.35 21.65 7.15 1.5 10 3 169. 60 16.85 23.15 8.15 3 10 2 170. 60 17.85 22.15 9.15 5 5 3 171. 70 18 12 1 3 5 3 172. 70 20.85 9.15 1.15 5 0 3 173. 70 23.35 6.65 2.15 1.5 0 3 174. 70 20.85 9.15 3.15 3 0 3 175. 70 18.35 11.65 4.15 1.5 4 2 176. 70 17.85 12.15 5.15 3 5 3 177. 70 18 12 6.15 5 10 2 178. 70 19 11 7.15 1.5 10 3 179. 70 18 12 8.15 3 15 2 180. 70 18 12 1 5 3 3
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Lower ignition Lower ignition Higher ignition Higher ignition Higher ignition Water Heating Method Methanol Butane LPG DME DEE DIPE Water Fumigant and as a% ofFuelMain % in Fumiga nte % in Fumigant and % in Fumigant and % in Fumigant and % in Fumigant and % in Fumigant andComment1. 0 0 0 0 0 0 0 Yes2. 0 0 0 0 0 0 0 Yes3. 0 0 0 0 0 0 0 Yes 1) 4. 0 0 0 0 0 0 0 Yes5. 0 0 0 0 0 0 0 Yes6. 0 0 0 0 0 0 0 Yes7. 0 0 0 0 0 0 0 Yes8. 0 0 0 0 0 0 0 Yes 2) 9. 0 0 0 0 0 0 0 Yes10. 0 0 0 0 0 0 0 Yes11. 0 0 0 0 0 0 0 Yes12. 0 0 0 0 0 0 0 Yes13. 0 0 0 0 0 0 0 Yes14. 0 0 0 0 0 0 0 Yes15. 0 0 0 0 0 0 0 Yes16. 0 0 0 0 0 0 0 Yes17. 0 0 0 0 0 0 0 Yes18. 0 0 0 0 0 0 0 Yes19. 0 0 0 0 0 0 0 Yes20. 0 0 0 0 0 0 0 Yes21. 0 0 0 0 0 0 0 Yes22. 0 0 0 0 0 0 0 Yes23. 0 0 0 0 0 0 0 Yes24. 0 0 0 0 0 0 0 Yes25. 0 0 0 0 0 0 0 Yes26. 0 0 0 0 0 0 0 Yes27. 0 0 0 0 0 0 0 Yes28. 0 0 0 0 0 0 0 Yes29. 0 0 0 0 0 0 0 Yes30. 0 0 0 0 0 0 0 Yes31. 0 0 0 0 0 0 0 Yes32. 0 0 0 0 0 0 0 Yes
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102/106
Lower ignition Lower ignition Higher ignition Higher ignition Higher ignition Water Heating Method Methanol Butane LPG DME DEE DIPE Water Fumigant and as a% ofFuelMain % in Fumiga nte % in Fumigant and % in Fumigant and % in Fumigant and % in Fumigant and % in Fumigant andComment33. 0 0 0 0 0 0 0 Yes34. 0 0 0 0 0 0 0 Yes35. 0 0 0 0 0 0 0 Yes36. 0 0 0 0 0 0 0 Yes37. 0 0 0 0 0 0 0 Yes38. 0 0 0 0 0 0 0 Yes39. 0 0 0 0 0 0 0 Yes40. 0 0 0 0 0 0 0 Yes41. 0 0 0 0 0 0 0 Yes42. 0 0 0 0 0 0 0 Yes43. 0 0 0 0 0 0 0 Yes44. 0 0 0 0 0 0 0 Yes45. 0 0 0 0 0 0 0 Yes46. 0 0 0 0 0 0 0 Yes47. 0 0 0 0 0 0 0 Yes48. 0 0 0 0 0 0 0 Yes49. 0 0 0 0 0 0 0 Yes50. 0 0 0 0 0 0 0 Yes51. 0 0 0 0 0 0 0 Yes52. 0 0 0 0 0 0 0 Yes53. 0 0 0 0 0 0 0 Yes54. 0 0 0 0 0 0 0 Yes55. 0 0 0 0 0 0 0 Yes56. 0 0 0 0 0 0 0 Yes57. 0 0 0 0 0 0 0 Yes58. 0 0 0 0 0 0 0 Yes59. 0 0 0 0 0 0 0 Yes60. 0 0 0 0 0 0 0 Yes61. 0 0 0 0 0 0 0 Yes62. 0 0 0 0 0 0 0 Yes63. 0 0 0 0 0 0 0 Yes64. 0 0 0 0 0 0 0 Yes
Petition 870190008339, of 01/25/2019, p. 111/158
103/106
Lower ignition Lower ignition Higher ignition Higher ignition Higher ignition Water Heating Method Methanol Butane LPG DME DEE DIPE Water Fumigant and as a% ofFuelMain % in Fumiga nte % in Fumigant and % in Fumigant and % in Fumigant and % in Fumigant and % in Fumigant andComment65. 0 0 0 0 0 0 0 Yes66. 0 0 0 0 0 0 0 Yes67. 0 0 0 0 0 0 0 Yes68. 0 0 0 0 0 0 0 Yes69. 0 0 0 0 0 0 0 Yes70. 0 0 0 0 0 0 0 Yes71. 0 0 0 0 0 0 0 Yes72. 0 0 0 0 0 0 0 Yes73. 0 0 0 0 0 0 0 Yes74. 0 0 0 0 0 0 0 Yes75. 0 0 0 0 0 0 0 Yes76. 0 0 0 0 0 0 0 Yes77. 0 0 0 0 0 0 0 Yes78. 0 0 0 0 0 0 0 Yes79. 0 0 0 0 0 0 0 Yes80. 0 0 0 0 0 0 0 Yes81. 0 0 0 0 0 0 0 Yes82. 0 0 0 0 0 0 0 Yes83. 0 0 0 0 0 0 0 Yes84. 0 0 0 0 0 0 0 Yes85. 0 0 0 0 0 0 0 Yes86. 0 0 0 0 0 0 0 Yes87. 0 0 0 0 0 0 0 Yes88. 0 0 0 0 0 0 0 Yes89. 0 0 0 0 0 0 0 Yes90. 0 0 0 0 0 0 0 Yes91. 1 0100 0 Yes92. 1 495 1 Yes93. 1 1385 2 Yes94. 1 1780 3 Yes95. 1 2175 4 Yes96. 1 2570 5 Yes
Petition 870190008339, of 01/25/2019, p. 112/158
104/106
Lower ignition Lower ignition Higher ignition Higher ignition Higher ignition Water Heating Method Methanol Butane LPG DME DEE DIPE Water Fumigant and as a% ofFuelMain % in Fumiga nte % in Fumigant and % in Fumigant and % in Fumigant and % in Fumigant and % in Fumigant andComment97. 2 2965 6 Yes98. 2 3360 7 Yes99. 1 2 908 Yes100. 1 1 909 Yes101. 1 0100 0 Yes102. 1 495 1 Yes103. 2 1385 2 Yes104. 2 1780 3 Yes105. 2 2175 4 Yes106. 2 2570 5 Yes107. 2 2965 6 Yes108. 2 3360 7 Yes109. 1 2 908 Yes110. 1 1 909 Yes111. 2 0100 0 Yes112. 2 495 1 Yes113. 2 1385 2 Yes114. 2 17 80 3 Yes115. 2 2175 4 Yes116. 2 2570 5 Yes117. 3 2965 6 Yes118. 3 3360 7 Yes119. 2 2 908 Yes120. 2 1 909 Yes121. 2 0100 0 Yes122. 2 495 1 Yes123. 2 1385 2 Yes124. 3 1780 3 Yes125. 3 2175 4 Yes126. 3 2570 5 Yes127. 3 2965 6 Yes128. 3 3360 7 Yes
Petition 870190008339, of 01/25/2019, p. 113/158
105/106
Lower ignition Lower ignition Higher ignition Higher ignition Higher ignition Water Heating Method Methanol Butane LPG DME DEE DIPE Water Fumigant and as a% ofFuelMain % in Fumiga nte % in Fumigant and % in Fumigant and % in Fumigant and % in Fumigant and % in Fumigant andComment129. 2 2 908 Yes130. 2 1 909 Yes131. 3 0100 0 Yes132. 3 495 1 Yes133. 3 1385 2 Yes134. 3 1780 3 Yes135. 4 2175 4 Yes136. 4 25 20 50 5 Yes137. 4 2965 6 Yes138. 4 3360 7 Yes139. 3 2 908 Yes140. 3 1 909 Yes141. 4 0100 0 Yes142. 4 495 1 Yes143. 4 1385 2 Yes144. 5 1780 3 Yes145. 5 2175 4 Yes146. 5 2570 5 Yes147. 6 2965 6 Yes148. 6 3360 7 Yes149. 4 2 908 Yes150. 4 1 909 Yes151. 5 0100 0 Yes152. 5 495 1 Yes153. 5 1385 2 Yes154. 6 1780 3 Yes155. 6 2175 4 Yes156. 7 2570 5 Yes157. 7 2965 6 Yes158. 8 3360 7 Yes159. 5 2 908 Yes160. 5 1 909 Yes
Petition 870190008339, of 01/25/2019, p. 114/158
106/106
Lower ignition Lower ignition Higher ignition Higher ignition Higher ignition Water Heating Method Methanol Butane LPG DME DEE DIPE Water Fumigant and as a% of Main Fuel % in Fumiga nte % in Fumigant and % in Fumigant and % in Fumigant and % in Fumigant and % in Fumigant andComment161. 6 0100 0 Yes162. 7 495 1 Yes163. 7 1385 2 Yes164. 8 1780 3 Yes165. 8 2175 4 Yes166. 9 2570 5 Yes167. 10 2965 6 Yes168. 11 3360 7 Yes169. 7 2 908 Yes170. 7 1 909 Yes171. 9 0100 0 Yes172. 9 495 1 Yes173. 11 1385 2 Yes174. 11 1780 3 Yes175. 12 2175 4 Yes176. 13 2570 5 Yes177. 14 2965 6 Yes178. 15 3360 7 Yes179. 10 2 908 Yes180. 10 1 909 Yes
^Δ % by weight; additional for 100% water / methanol combination by weight of total fuel intake

权利要求:
Claims (29)
[1]
1. Main fuel composition of diesel engine, characterized by the fact that it comprises methanol and from 3% to 40% by weight of water, and one or more additives selected from the group consisting of: ignition enhancers, fuel extenders, combustion enhancers, oxygen-absorbing oil, lubricity additives, product coloring additives, flame dyes, anti-corrosion additives, biocides, freezing point depressants, deposit reducers, denaturants, pH control agents, and mixtures thereof , wherein the fuel composition comprises no more than 20% by weight of dimethyl ether.
[2]
2. Main fuel composition of diesel engine according to claim 1, characterized by the fact that the fuel comprises from 5% to 40% by weight of water.
[3]
3. Main fuel composition of diesel engine according to claim 1, characterized by the fact that it comprises methanol, between 12% and 23% by weight of water, and not more than 20% by weight of additives.
[4]
4. Main fuel composition of diesel engine according to claim 1, characterized by the fact that it comprises methanol, between 20% and 22% by weight of water, and not more than 20% by weight of additives.
[5]
5. Main fuel composition of diesel engine according to claim 1, characterized by the fact that it comprises between 20% and 22% by weight of water, 4-6% by weight of dimethyl ether and methanol.
[6]
Main diesel engine fuel composition according to any one of claims 1 to 5, characterized in that it comprises at least 20% by weight of methanol.
[7]
7. Main fuel composition of diesel engine of
Petition 870190008339, of 01/25/2019, p. 116/158
2/5 according to any one of claims 1 to 6, characterized in that the main diesel fuel composition is a single-phase composition.
[8]
The main fuel composition of the diesel engine according to any one of claims 1 to 7, characterized by the fact that the total water and methanol is at least 80% by weight of the fuel composition.
[9]
9. Main fuel composition of diesel engine according to any one of claims 1 to 8, characterized by the fact that methanol in the diesel fuel composition is crude methanol.
[10]
10. Main fuel composition of diesel engine according to any one of claims 1 to 9, characterized by the fact that the additives comprise:
- a product coloring additive up to 1% by weight, and
- a fire-colored additive, up to 1% by weight of the fuel.
[11]
11. Process for starting a compression ignition engine using a main fuel composition as defined in any one of claims 1 to 10, characterized by the fact that it includes:
preheat a supply air stream, introduce the preheated air into an engine combustion chamber and compress the preheated air; and introduce the fuel into the combustion chamber and ignite the fuel / air mixture to start the engine.
[12]
Process for starting a compression ignition engine according to claim 11, characterized in that it includes preheating the supply air to at least 50 ° C.
[13]
13. Process for starting an ignition engine by
Petition 870190008339, of 01/25/2019, p. 117/158
3/5 compression according to claim 11, characterized by the fact that it includes preheating the supply air to 150 ^o C-300 ° C.
[14]
14. Process for starting a compression ignition engine according to claim 11, 12 or 13, characterized in that it includes passing the exhaust material from the engine through the heat exchanger to preheat the air flow of input of the engine.
[15]
15. Process for starting a compression ignition engine according to claim 14, characterized by the fact that it includes cooling the exhaust material through the heat exchanger, collecting water from the refrigerated exhaust material and recycling at least one portion back into the fuel.
[16]
16. Process for starting a compression ignition engine according to any one of claims 11 to 15, characterized in that it includes condensing the exhaust material, collecting water from the condensed exhaust material and recycling at least a portion back to the fuel.
[17]
17. Process for starting a compression ignition engine according to any one of claims 11 to 16, characterized in that it includes fumigating the supply air with a fumigant containing an ignition enhancer.
[18]
18. Process for starting a compression ignition engine according to any one of claims 11 to 17, characterized in that the fuel has the fuel composition of the diesel engine as defined in any one of claims 1 to 10 .
[19]
19. Power generation system, characterized by the fact that it comprises:
power a compression ignition engine using a main fuel composition as defined in
Petition 870190008339, of 01/25/2019, p. 118/158
Any of claims 1 to 10 for supplying energy;
preheating an incoming air stream from the compression ignition engine, and / or fumigating the inlet air stream with an ignition enhancer;
treat the engine's exhaust gas to recover exhaust heat and / or water from the engine, and redirect heat and / or water for later use.
[20]
20. Power generation system according to claim 19, characterized by the fact that it comprises recycling exhaust heat and / or returning water to the engine.
[21]
21. Power generation system according to claim 19, characterized in that it comprises exchanging the heat of the exhaust gas through a heat exchanger for water in a hot water cycle, and transferring heat from the water through the heating cycle hot water for the environment.
[22]
22. Power generation system according to claim 19, characterized in that the system is adapted to power a railway vehicle, comprising treating exhaust gas to remove particles from the exhaust gas and recovering heat and water to recycle back engine and / or for use on the rail vehicle.
[23]
23. Power generation system according to claim 19, characterized in that the power generation system is adapted to power a marine vehicle, comprising treating exhaust gas in a desalinator to recover heat and water to recycle back to engine and / or redirect for use on the marine vehicle.
[24]
24. Power generation system according to claim 19, characterized in that it comprises mixing exhaust gas from the engine with water in a mixer to cool
Petition 870190008339, of 01/25/2019, p. 119/158
5/5 the exhaust gas and recover water from the condensation of the exhaust gas.
[25]
25. Power generation system according to claim 19, characterized in that it comprises pumping water from the mixer to a gas / liquid heat exchanger to further cool the water.
[26]
26. Power generation system according to any one of claims 19 to 25, characterized by the fact that the fuel has the main fuel composition of the diesel engine as defined in one of claims 1 to 10.
[27]
27. Power generation system according to any one of claims 19 to 26, characterized in that it comprises processing in a pre-processor a pre-fuel composition comprising methanol and ether, and optionally water, in which the pre-processor separates the ether methanol, and uses ether as an ignition enhancer in the fumigation of the incoming stream.
[28]
28. Power generation system according to claim 27, characterized by the fact that the pre-fuel composition comprises 7-10% ether.
[29]
29. Power generation system according to any one of claims 19 to 28, characterized by the fact that it includes preheating the supply air to 150 ^o C-300 ^o C.

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法律状态:
2018-11-21| B07A| Application suspended after technical examination (opinion) [chapter 7.1 patent gazette]|

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2019-04-09| B09A| Decision: intention to grant [chapter 9.1 patent gazette]|

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2019-06-18| B16A| Patent or certificate of addition of invention granted [chapter 16.1 patent gazette]|Free format text: PRAZO DE VALIDADE: 20 (VINTE) ANOS CONTADOS A PARTIR DE 25/11/2011, OBSERVADAS AS CONDICOES LEGAIS. (CO) 20 (VINTE) ANOS CONTADOS A PARTIR DE 25/11/2011, OBSERVADAS AS CONDICOES LEGAIS |

优先权:

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申请号 | 申请日 | 专利标题

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AU2010905226A|AU2010905226A0|2010-11-25|Fuel and process for powering a compression ignition engine|

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AU2010905226|2010-11-25|

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AU2010905225A|AU2010905225A0|2010-11-25|Process for powering a compression ignition engine and fuel therefor|

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AU2010905225|2010-11-25|

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PCT/AU2011/001531|WO2012068634A1|2010-11-25|2011-11-25|Process for powering a compression ignition engine and fuel therefor|

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