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  • 专利说明
  • 权利要求
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    • 专利摘要:
    process and device for heat recovery and its transformation into mechanical potential in a motor vehicle drive system. The present invention relates to a working medium conducted in a working medium cycle, with the aid of at least one evaporator integrated in the working medium cycle, by means of exhaust heat from a combustion engine of the motor vehicle , is evaporated, the generated steam being conducted to an expansion machine, coupled with the combustion engine, and the exhaust steam from the expansion machine will then be recycled in at least one condenser to the liquid phase. according to the invention, in the operating medium cycle, downstream of at least one evaporator (2, 3), at least one valve (17, 23) is integrated in such a way that regulates the control and/or control assembly. regulation, the valve being adjustable and/or commandable, as well as a steam reservoir (21; 30) are integrated in such a way that, especially in the case of activation potential not required by the expansion machine (4, 4'), and /or in a combustion engine not operated in a lit manner, the steam generated, preferably with a blocked expansion machine, (4, 4'), is at least partially fed into a steam reservoir (21;30), with the steam stored from the steam reservoir (21:30) immediately afterwards already in the steam reserve phase, with the triggering potential again required by the expansion machine (4, 4') and/or the combustion engine operated in a lit manner , will be recycled at least partially for the cycle of the working medium to drive the expansion machine (4, 4') .
    公开号:BR102012017039B1
    申请号:R102012017039-6
    申请日:2012-06-20
    公开日:2021-07-13
    发明作者:Gottfried Raab；Josef Klammer
    申请人:Man Truck & Bus Ag；
    IPC主号:
    专利说明:

    Description
    [001] The present invention relates to a mechanical potential for heat recovery in mechanical potential in a drive system for motor vehicles according to the preamble of claim 1, as well as covering a device for carrying out a process of this nature, according to the preamble of claim 9.
    [002] Such a process is generally known. The constructive conformation of the system components, especially the evaporator, the expansion machine (hydrodynamic machine or mobile piston machine) and the condenser, considered a classic use of long-distance traffic on the highway, that is, an almost stationary operation of the engine combustion, and contributes in this operation to an increase in the efficiency of the drive system. As usable heat vehicles, for example, refrigerant or charge air can be used, but especially combustion engine exhaust gas. The less stationary the combustion engine operation is, as eventually in the case of changing slopes and slopes, or in vehicles in distribution traffic, the more the degree of efficiency that can be achieved in the field of heat recovery increases.
    [003] It is the object of the present invention to expand a process for heat recovery and its transformation into mechanical potential in a drive system for motor vehicles, in such a way that also in non-stationary operation a satisfactory degree of effectiveness of the heat system can be achieved. drive. In addition, a device especially suitable for implementing a process for heat recovery and its transformation into mechanical potential in a drive system for motor vehicles should be indicated.
    [004] This task will be solved with the characteristics of independent claims. Advantageous modalities are the object of the cross-referenced dependent claims.
    [005] According to claim 1, a process is proposed for value recovery and its transformation into mechanical potential in a drive system for motor vehicles, in which a working medium that is driven in a working medium cycle, with the help of at least one evaporator that is part of the working environment cycle, using the exhaust heat of a combustion engine of a motor vehicle, it is evaporated, and the generated steam is conducted to an expansion machine coupled with combustion engine and then the exhaust vapor from the expansion machine will be recycled at least to a condenser again in the liquid phase. According to the invention, in the cycle of the working medium downstream of at least one evaporator, at least one adjustable valve is integrated and/or controlled by at least one control and/or regulation assembly, as well as a steam accumulator. such that especially in the case of unnecessary drive potential of the expansion machine and/or especially in the case of the non-operated combustion engine (especially in the thrust or engine braking operating regime), the generated value, preferably with the machine expansion simultaneously blocked, at least in part is fed into the steam tank. The steam reserved in the steam reservoir will, for example, be thereafter - preferably immediately following the steam reserve phase - in the case of required drive potential of the expansion machine and/or in the case of a combustion engine operated in a manner lit at least partially can be recycled in the cycle of working medium to drive the expansion machine. The process according to the invention realizes two essential improvements in non-stationary displacement. The expansion machine whose mechanical potential, especially in the thrust and/or engine braking operation, is not necessary, may be disconnected from the steam supply, at least partially, preferably as a whole, and at the same time the steam is still produced in the system, ie hot steam (via residual heats, inertia in the system, exhaust gas heat in engine braking operation) may be transported to the steam reservoir and/or may be stored. In the event of the expansion machine's triggering potential again needed, that is, with the combustion engine operated again and turned on, the expansion machine can then be subjected directly to the value, i.e. with hot steam, of the steam reservoir and therefore provides almost no delay again the additional potential. In this way, with the non-stationary operation of the combustion engine, an expansion potential supply can be achieved, also in the intensive consumption acceleration phases, which improves its response behavior and reacts to the drop in the degree of efficiency of the non-stationary operation drive system.
    [006] To produce, for example, an especially smooth transition from the reservoir operation of the expansion machine, serviced by the steam reservoir, back to the normal supply of steam through the evaporator, according to an especially preferred and concrete process sequence is proposed that during a heating phase of the working medium cycle which is sequential, preferably immediately to the feeding phase in the steam reservoir, especially of the thrust and/or engine braking operation regime, it produces a connection to one of the steam reservoirs with the expansion machine and, on the other hand, with at least one evaporator (or at least one of several evaporators) with a bypass line that shorts the expansion machine so that this expansion machine can be supplied with steam from the steam reservoir until the working medium of the working medium cycle, by at least one of the evaporators, is again heated to a the set and/or predetermined hot steam temperature. A process of this nature can, moreover, be carried out in a simple way only from the point of view of control, that is, technical regulation and operational safety. In connection with a heating phase of this type it is also proposed that when the defined and/or predetermined hot steam temperature is reached, the steam supply to the steam reservoir is stopped, and, in addition, the bypass line is again blocked and again the expansion machine, in the conventional operation of the expansion machine, is again fed only with steam from at least one evaporator.
    [007] Alternatively or additionally, it can be provided that when the defined and/or predetermined hot steam temperature is reached, the bypass line is again blocked and, therefore, the expansion machine will be powered again, as in the conventional operation of the expansion machine, with steam coming from at least one evaporator, and the steam supply of the steam reservoir will only be stopped when the steam reservoir is totally or up to a defined minimum quantity. In a mixed operation of this nature, it is ensured that the steam reservoir is emptied in the desired way, with the remaining steam in reserve in this mixed regime being, at a suitable point, introduced and fed in front of or into the expansion machine.
    [008] The useful volume of the steam reservoir will be conveniently in an enlargement preferably shaped in such a way that a mass of steam corresponding to operating phases of medium engine brakes can be reserved. An average value of this nature can eventually be in an empirical process and ensures that, for example, after moving down a slope by the engine vehicle, the expansion machine can be fueled for so long with stored steam, i.e., with hot steam, until the evaporation system is again sufficiently ready for service with at least one evaporator. On the other hand, assembly criteria and steam tank charge times must also be taken into account.
    [009] In addition, it is provided, according to another sequence of the process, that when a maximum working pressure of the steam tank is reached, during the steam feeding phase, a bypass line that connects to a short is released and/or opened the expansion machine. This increases operational safety and helps to avoid overpressures in the steam tank. Through the bypass line, with sufficient steam generation, the readiness of systems without cooling lines and functional points and without system overpressure can be preserved and, therefore, can also contribute to an improved response behavior in the transition to the service of drive.
    [0010] Especially preferably during the vapor reserve phase, i.e. during the thrust and/or braking phases of the engine, the exhaust gas system of the combustion engine serves as a source of heat for the minus one evaporation unit, especially when the combustion engine has at least one throttling set in the exhaust gas section for generating the engine's braking potential. These throttling sets (eg exhaust gas flaps, variable gas change valve controls, etc.) make it possible to preserve high exhaust gas temperatures, also in the operating phases of engine braking. Basically, they can also be used alternatively or additionally for an exhaust gas system, other thermal sources especially on the vehicle side, for example an engine coolant and/or charge air just to name two other examples.
    [0011] In an additional advantageous function, the steam, i.e. hot steam accumulated in the steam reservoir, in addition to the blow of elimination of condensed working medium from functional points of the working medium cycle after deactivation of the combustion engine and/or in case of winter temperature, it can be used. In this way, for example, it can react against a control valve or evaporator freezing in the case of external temperatures in the range below the minimum, without the danger of introducing air into the working medium cycle of the heat recovery system. This additional function is especially advantageous in the case of operating medium cycles that are closed to the environment.
    [0012] By means of suitable insulating agents, the vapor reservoir can be coated and thermally insulated. Preferably, however, it is proposed that the steam tank, for example, formed in two shells, is heated by the exhaust gas of the combustion engine and, therefore, without heat loss, it remains effective also for longer periods of time in operation. displacement as a backup medium.
    [0013] According to claim 9, in a particularly advantageous device for implementing a heat recovery process and its transformation into mechanical potential in a drive system for motor vehicles, it comprises a combustion engine as a drive source, a expansion machine operationally coupled with the combustion engine, this expansion machine coupled in at least one evaporator which can be heated by the exhaust heat of the combustion engine, and which is integrated in a working medium cycle with at least one condenser . According to the invention, in the case of an advanced line of the working medium cycle downstream of at least one evaporator, at least one valve controllable and/or adjustable by at least one control and/or regulation assembly, will be arranged whereby, in the case of unnecessary drive potential of the expansion machine and/or in the case of a combustion engine machine not operable in a lit mode, preferably at least the forward line may be joined with a reservoir of steam at least in the thrust and/or braking operation of the motor vehicle engine, and/or the expansion machine can be switched off.
    [0014] The advanced machine can preferably be provided with a multi-way valve, by means of which the expansion machine, in a constructive manner and simple control technique, and/or the steam tank can be joined with at least one evaporator. In addition, in addition to the valve that commands the integration of steam into the steam accumulator, which is preferably a multi-way valve, it may additionally be coupled by a bypass line that shorts the expansion machine, preferably being a bypass line with a throttling valve, provided that through the valve that introduces the steam into the steam reservoir, the steam reservoir and/or the expansion machine and/or the diversion line can be joined, with reduced technical driving effort, with at least one evaporator.
    [0015] In this case, furthermore, the diversion line downstream of a repercussion valve, connected sequentially to the expansion machine, may flow into the exhaust steam line to the condenser. The rebound valve reliably prevents the flow of steam over the diversion line from occurring, which would be detrimental to the operation of the expansion machine.
    [0016] The steam tank can be connected through a separate pressure line, featuring a controllable valve, with the advanced line downstream of the valve that introduces the affixing to the steam tank, that is, a multi-way valve and, upstream of the expansion machine can be with that machine attached. The steam tank may also alternatively be connected via a pressurized line with a controllable valve which may be connected in parallel to the forward line with the expansion machine. In this way, during the expansion of steam, preferably in a reduced pressure region of the expansion compartment, steam can be introduced in a controlled manner with an increase in potential into the expansion machine. This has the special advantage that due to a greater pressure drop, the steam accumulator can be used in greater expansion, ie, in the accumulation operation it can be emptied to a lower pressure.
    [0017] The use of energy from the exhaust gas, at least one evaporator may be correspondingly coupled in the exhaust gas line system of the combustion engine. Eventually, it could also be used as a combustion engine refrigerant or the charge air of a charged combustion engine. This also applies to the steam tank, that is, its housing, which, preferably via the combustion engine exhaust gases, is being heated.
    [0018] In an additional preferred function of the heat recovery system, the steam tank may be coupled through a flow blow line on the inlet side of the evaporator, with the hot steam stored in the steam tank serving to blow in the sense of draining liquefied working medium eventually deposited in the evaporator and in the subsequent conductive system, in order to largely exclude, for example, an evaporator damage by freezing in operation during the period of introduction of air into the system working medium cycle of heat recovery. This additional function is particularly advantageous with closed media cycles in relation to the environment.
    [0019] Another functional improvement of the heat recovery system can be characterized by the fact that the steam reservoir has several chambers that through overpressure valves (fill and discharge valves) are interconnected in such a way that their sequential filling is mutually separated and their emptying can be carried out together. In this way, a variable charge time of the steam tank is achieved with relatively rapid pressure build-up in the different chambers. If a first chamber of the steam vessel reaches the predetermined vessel pressure, then an overpressure valve (fill valve) opens towards the second chamber, and so on. Conversely, during the accumulation operation of the expansion machine all chambers are emptied together by opening the other overpressure valves (discharge valves). Partially filled chambers will only be emptied when all other filled chambers have fallen to the pressure prevailing in the partially filled chamber. The opening, that is, closing of the overpressure valves is controlled according to the pressure conditions inside the chambers.
    [0020] According to an advantageous embodiment of the invention it may also be advantageous that several, for example two evaporators, are coupled to the exhaust gas conducting system of the combustion engine, being joined and concentrating a controlled pipeline or through a valve, in the working medium cycle and in a combined advanced line, they are united and can be subjected through the valves in a controlled and/or regulated way individually, in groups or together with the working medium. Especially it may be convenient when in case of high engine and combustion potential requirements, only one evaporator and in case of a lower potential demand, both evaporators, for example, are actively connected in order to be able to match their respective capacity expansion machine absorption on the one hand and the heat elimination potential of the vehicle's cooling system on the other hand. Eventually, it may also be possible that in the standby operation, with the expansion machine turned off due to the available values of the different heat sources, only one evaporator is turned on active and in the regular operating regime of activation, all are actively turned on, or ie both evaporators.
    [0021] The steam accumulator can, furthermore, be connected at least through a geodesic condensate line, in low position, with the working medium cycle downstream of the condenser, in order to reliably drain eventually accumulated condensate inside the steam tank.
    [0022] Finally, particularly conveniently, in the working medium cycle of the heat recovery system, a feed pump can be provided on the liquid side, which supplies the evaporator from a reserve container, a suction pump positioned upstream of the condenser and transporting to the reserve container, with an interposed filter and a recycling line featuring a pressure limiting valve for the feed pump, being provided towards the reserve container. The working medium in the reserve container can be deionized water or a mixture thereof.
    [0023] Below, an example of the implementation of the invention is being presented with other details and advantages that can be obtained. The attached drawing shows:
    [0024] Figure 1 - As a block diagram a pump operated value recovery device with an expansion machine for the combustion engine in a drive system for motor vehicles, and possibly among others, having two evaporators, a condenser, a steam reservoir and several controllable valves in an adjustable actuation service with steam subject expansion machine
    [0025] Figure 2 - Device according to figure 1, but in the engine thrust and/or braking operation and with activated valves for loading the steam tank
    [0026] Figure 3 - Device according to figure 2 with loaded steam tank and bypass line activated for the expansion machine
    [0027] Figure 4 - Device according to figure 3 in operation immediately after the transition of the thrust and/or engine braking process in the combustion engine drive operation, with open steam accumulator in the direction of the engine. expansion and with bypass line still open for heating the working medium cycle
    [0028] Figure 5 - Device according to figure 4 in a controlled mixing operation, in which the evaporators and the steam reservoir are coupled to the expansion machine
    [0029] Figure 6 - Alternative embodiment of the device according to figures 1 to 5 in which the steam accumulator is formed with several chambers and through a separate pressurized line it can be connected directly with the expansion machine
    [0030] Figure 7 - First exemplified embodiment of a multi-chamber steam accumulator and
    [0031] Figure 8 - Second exemplified embodiment of a multi-chamber steam reservoir.
    [0032] Figure 1 presents as a block diagram a device for heat recovery and its transformation into mechanical potential for a drive system in automotive vehicles, especially utility vehicles such as trucks or buses, with a combustion engine (not shown) as a drive source that has a service medium cycle 1, in which, among others, here by way of example, two evaporators 2, 3, an expanding machine 4 and a condenser 5 are integrated.
    [0033] As a working medium, for example, deionized water is used, which is filled in a reservoir 6 on the underside of which a supply line 7 branches. of a distributor - here two separate pipelines 7a, 7b - and which are coupled on the inlet side to evaporators 2, 3. In the pipelines 7a, 7b an electric proportional-current regulating valve 10 is also shown here as an example. by means of which the mass current of the working medium and, with it, the generation of steam can be controlled.
    [0034] It is coupled to the distributor 9 of a return line 11 with an integrated pressure relief valve 12, with the recycling line 11 opening into the reserve container 6.
    [0035] Furthermore, at the outlet of the condenser 5 there is coupled another return line 13 which also opens into the reserve container 6 and in the direction of flow a condensate suction pump 14 and a filter 15 are integrated.
    [0036] The two evaporators 2, 3 shown here only by way of example, in a manner not shown, are mounted, for example, in the combustion engine suction installation, that is, they are coupled with the exhaust gas installation with heat transfer and in heat exchange they will be subjected to the hot exhaust gas of the combustion engine in order to transfer a liquefied working medium to the vapor phase.
    [0037] The working medium transformed in the evaporators 2, 3 preferably into hot steam, here, by way of example, will be initially conducted through two, and then, through a combined advance line 16, with a defined overpressure, i.e. , predetermined to the expansion machine 4, whereby in the forward line 16, i.e. the precursor line, there is integrated a multi-way valve 17 by means of which the hot steam can be distributed as described below.
    [0038] The expansion machine 4 can, for example, be a flow machine or a mobile piston machine of defined and potential conformation which, preferably, is subjected with steam, i.e. hot steam, in an overpressure regime, driving the combustion engine as an additional direct or indirect drive in the drive direction. The expansion machine 4 can, if necessary, also drive another set of the motor vehicle, for example, an air conditioning system, a compressor, a fan, a generator etc.
    [0039] On the outlet side, an exhaust steam line 18 is coupled to the expansion machine 4, in which, for example, a rebound valve 19 is integrated and which opens the outlet location in the condenser 5 that transfers the medium work by condensation back to the liquid phase.
    [0040] Coupled to the multi-way valve 17, a first pressurized line 20 leads to a steam tank 21, integrated in the vehicle. The steam tank 21, in a manner not shown, is thermally insulated and with respect to its volume, i.e. its storage capacity, it is so shaped that in a full state, over a defined period of time, it can supply the expansion machine 4 with an overpressure, ie a hot steam in system pressure regime.
    [0041] For this purpose, in the steam reservoir 21 a second pressurized line 22 is coupled which opens downstream of the multiway valve 17, however, upstream of the expansion machine 4, in the precursor line 16, that is, in its segment 16a, and in which a controllable valve 23 is integrated, by means of which the pressurized line 22 can be blocked or activated in the direction of the expansion machine 4.
    [0042] Furthermore, a bypass line 25 with an integrated throttle valve 24 is branched from the multi-way valve 17 which is coupled downstream of the repercussion valve 19 in the exhaust steam line 18.
    [0043] From the steam reservoir 21 also extends a flow blow line 25 (shown by dashes and dots) and which can be controlled through a valve 26, which line is coupled to the evaporators 2, 3 on its side and that, for example, at each stoppage of the combustion engine, by quickly opening valve 26, it carries out a corresponding washing of the evaporators 2, 3 and of the valves and subsequent lines by discharging any accumulated condensate with the application of hot steam.
    [0044] Through a condensate line 28 also presented by dashes and dots with a discharge valve 29 also geodetically in a lower position, in the steam reservoir 21, it can eventually be drained, condensate, accumulated, in the reservoir of steam 21, temporarily led to the recycling line 13 upstream of the suction pump 14.
    [0045] The aforementioned valves 17, 23, 26 and 29, as well as the two regulating valves resulting from 10 here, presented by way of example, in the pipelines 7a, 7b are electrically joined through an electronic control device not shown, and as described below, being triggered; the control device may possibly be the combustion engine electronic control device, in which the operating parameters necessary for the control, such as the state of charge of the combustion engine, vehicle speed, engine thrust operation and braking engine temperature, engine temperature, exhaust gas temperature, etc. have already been recorded in any case and, therefore, implementation with relatively little greater effort is feasible. In addition, at least in the steam reservoir 24 and/or precursor line 16, an overpressure pressure sensor (not shown) is provided for, in order to avoid impermissible overpressure, that is, to record the pressure of the system.
    [0046] Figure 1 shows device 1 for heat recovery in the operation of regular displacement (more or less stationary), in which both evaporators 2, 3 are subjected with working medium through the flow regulating valves 10 and produce steam which through the precursor line 16 and the multiway valve 17 is conducted to the expansion machine 4 and by it - correspondingly extended by the application of mechanical actuation potential - through the flow steam line 19 flows to the condenser 5 After the condenser 5 through working the condensate and again liquid flows through a filter 15 back to the reserve container 6.
    [0047] The described cycle will be reserved through the two pumps 8, 14. Depending on the service point of the combustion engine and, therefore, the prevailing wing currents, including the temperature in the different thermal sources, it results from the amount of steam that can be produced and which is regulated by the current regulating valves 10 and by the absorption power dependent on the rotations of the expansion machine, a system pressure downstream of the evaporators 2, 3 may result. The lines 02, 25 that branch from the valve of several lanes 17 are blocked (shown in dashed form). In addition, pressurized line 22 is closed from vapor reservoir 21 to precursor line 16a through valve 23.
    [0048] Figure 2 shows a device 1 with the difference that the motor vehicle is in an engine braking operation, and in the combustion engine and/or in the exhaust gas system (not shown) the choke sets integrated there (gas exchange valves, exhaust gas flaps etc) for the effect of generating an engine braking effect are activated and thus produce high exhaust gas temperatures.
    [0049] In this operational state the multiway valve 17 through the engine control device is initially switched in such a way that now a segment 16a of the precursor line 17 is interrupted (shown in dashed form) and the pressurized line 20 to the reservoir of steam 21 is open. Therefore, the steam reservoir 21 through a time interval of engine brake operation or until a maximum system pressure is reached will be charged with a hot steam.
    [0050] If, eventually, the system pressure, i.e. maximum container, has been reached during engine braking operation, then the multiway valve 17 - as shown in figure 3 - will switch to throttled operation, being the bypass line 25 with the integrated throttle valve 24 is opened and thus transfers the excess hot steam to the steam flow line 18. The throttling operation eventually applied ensures that the system operation upstream of the multi-way valve 17 remains preserved. The hot steam in the steam tank 21, in an overpressure regime, is hermetically blocked by the closed valves 17, 23, 26 and 29.
    [0051] If after the engine cold operation, the combustion engine passes again to the drive system on, then with the throttling operation still continued according to figure 4, valve 23 in the steam reservoir 21 and almost free of delay the expansion machine 4 via pressurized line 22 and precursor line 16a, will be subjected with the reserved hot steam and therefore is immediately available to provide the maximum additional drive potential. At the same time, in the throttling regime, the system upstream of the multiway valves 17 can also be accelerated until when the set or predetermined hot steam temperature is reached, the bypass line is again blocked and therefore the The expansion machine is again fed in the conventional expansion operation regime with steam from at least one evaporator.
    [0052] Finally, Figure 5 shows the region of transition from the reserve operation of the expansion machine to the quasi-stationary operation, in which the multiway valve 17 are again connected in such a way that it joins the evaporators 2, 3, or that is, the precursor line 16, 16a with the expansion machine 4, (according to figure 1), however, the valve 23 in the steam reservoir 21 is still open.
    [0053] This mixed operation will be, for example, convenient when the steam reservoir 21 is still provided with steam pressure that can be used and will then be superimposed on the system pressure in the precursor line 16, 16a. In this way, by comparing the pressure values, the control can be carried out by pressure sensors in the steam tank 21 and in the precursor line 16 on the electronic control device.
    [0054] If the steam reservoir 21 is emptied, i.e. its steam pressure is still too low, then the valve 23 will be closed again in the pressurized line 22 and the regular steam supply of the expansion machine 4 of according to figure 1 directly on evaporators 2 and/or 3.
    [0055] Figure 6 shows an alternative version of the heat recovery device 1, which however is only described to the extent that it differs from figures 1 to 5. Identical components have identical reference numbers.
    [0056] In Figure 6 a steam reservoir 340 is used, the housing 30a of which is double-walled. The steam tank of figure 6 is detailed without the peripheral functional components, that is, interfaces for the working medium cycle 1, 7, 4, 4', 29, 28, 26, 27 in different modalities in figures 7 and 8. The shell 35 between the housing walls can be evacuated to avoid heat loss, it can be filled with air or a suitable insulating material, or in a way not shown, it can, for example, be coupled to the gas system. combustion engine exhaust or can be heated through it.
    [0057] Furthermore, the steam tank 30 by means of partition walls 36 is subdivided into several chambers 30b. These chambers are interconnected in such a way through overpressure valves (filler valves 32 and flow valves 33) in such a way that their filling can occur sequentially, that is, reciprocally separate, and their flow can be done together. Therefore, in the reserve operation, initially, the chamber 30b closest to the pressurized line 20 and after reaching a predetermined vapor pressure, the neighboring chamber 30b, the chamber 30 and so on will be filled. In this way, despite the relatively large volume of the steam tank 30, a sufficient pressure will soon be provided, which then propagates from chamber 30b to chamber 30b and at any time, also with reduced filling duration, ensures an effective clamping of the expansion machine with high pressure.
    [0058] The emptying of the steam tank 30 when changing the thrust and/or braking operation of the engine to the combustion engine drive service is verified in all chambers together by opening valve 23 and, subsequently, by opening the other overpressure valves (discharge valves 33), and the pressurized line is at the outlet, according to the mode of figure 7, it is coupled to a steam collector strip 34. In the alternative mode of figure 8, if the flow of the chambers by the flow valves 33 sequentially. Partially filled chambers will be emptied initially and then when all other filled chambers are dropped to the pressure prevailing in the partially filled chamber. The opening, that is, the closing of the overpressure valves is controlled by the pressure ratios in the chambers.
    [0059] The pressurized line 31 is here also shaped as a separate line, which projects in parallel to the precursor line 16a, and is coupled to a reduced pressure inlet 4a of the expansion machine 4. Expansion 4, for example, another inlet valve (not shown) could be provided, with which the hot steam accumulated in the steam tank 30 is fed directly into the expansion compartment. As the pressures here during the expansion phase are temporarily essentially lower than at the steam inlet of the expansion machine 4', the steam accumulator 30 can be emptied at lower pressures and therefore its capacity can be increased and the steam 20 accumulated can be used more efficiently.
    [0060] In addition, due to the smaller residual amounts of steam that are stored there results a smaller accumulation of condensate in the steam reservoir 30.
    [0061] The operating mode of heat recovery device 1' (figure 6) is furthermore the same as device 1, described in figures 1 to 5 and, therefore, is not being further explained.
    [0062] The steam reservoir 21, 30, also in addition to the described engine braking service (permanent brake) also during the thrust service and in special operational cases also in the motor vehicle on operation by a corresponding switching of the lane valve multiples 17 and simultaneously the power supply to the expansion machine 4, 4' may be interrupted. Numerical List of Components 1 Heat recovery device 2 Evaporator 3 Evaporator 4 Expansion machine 4a Second inlet 5 Condenser 6 Reserve container 7 Water lines 7a Water lines 7b Water lines 8 Water pump 9 Distributor tube 10 Current regulating valves 11 return 12 Pressure relief valve 13 Return line 14 Suction pump 15 Filter 16 Precursor line 16a Precursor line segment 17 Multiway valve 18 Exhaust steam line 19 Repercussion valve 20 Pressurized line 21 Steam accumulator 22 Pressurized line 23 Valve 24 Throttle valve 25 Bypass line 26 Valve 27 Drain blow line 28 Line 29 Drain valve 30 Steam reservoir 30a Housing 30b Chambers 31 Pressurized lines 32 Filler valves
    权利要求:
    Claims (19)
    [0001]
    1. Process for heat recovery and its transformation into mechanical potential in a drive system for motor vehicles, in which a working medium is conducted in a working medium cycle, with the aid of at least one evaporator (2, 3) integrated in the work environment cycle, by means of exhaust heat from a combustion engine of the motor vehicle, is evaporated, and the generated steam is conducted to an expansion machine, coupled with the combustion engine, and the steam from exhaust from the expansion machine (4, 4') will then be recycled in at least one condenser to the liquid phase, where the cycle in the working medium, upstream of at least one evaporator (2, 3), is such integrated mode a valve (17, 23) that can be controlled and/or regulated through a command and/or regulation set, comes as a steam accumulator (21; 30), characterized by the fact that, in the case of Unnecessary drive potential of the expansion machine (4; 4') and/or with motorcycle r combustion not operated in a lit form, the generated steam, at least in part, is fed into the steam reservoir (21; 30), and the steam expected in the steam reservoir (21; 30) will preferably be recycled, with the potential of the required drive of the expansion motor (4; 4') and/or in the case of combustion engine operated in this way lit, at least in part, this recycling being carried out at least in part for the cycle of the working medium to drive the expansion machine (4; 4').
    [0002]
    2. Process according to claim 1, characterized in that in the steam reservoir (21; 30), at least during a thrust service phase that forms the steam feed phase, and/or an operation phase of the vehicle engine braking, the steam will be supplied and correspondingly the steam reservoir (21; 30) will be connected in the flow direction with at least one of the evaporators (2, 3).
    [0003]
    3. Process according to claim 1 or 2, characterized in that in a heating phase that preferably follows directly the steam reserve phase, towards one of the steam accumulators (21; 30) with the expansion machine (4; 4') and, on the other hand, to at least one evaporator (2, 3) or at least one evaporator (2, 3) with a bypass line (25) that shorts the machine of expansion (4; 4'), so that the expansion machine (4, 4') will preferably be alone supplied with steam from the steam reservoir (21; 30) until the working medium of the medium cycle work by means of at least one evaporator (2, 3) is heated to a defined and/or predetermined hot steam temperature.
    [0004]
    4. Process according to claim 3, characterized in that the defined and/or predetermined hot steam temperature will be reached, the steam supply of a steam reservoir (21; 30) is stopped, and in addition the diversion line (25) will be blocked again and finally the expansion machine (4; 4'), in the operating regime of the conventional expansion machine will only be supplied with steam from at least one evaporator (2; 3).
    [0005]
    5. Process according to claim 3 or 4, characterized in that when the defined and/or predetermined hot steam temperature is reached, the bypass line (25) will again be blocked and, therefore, the machine expansion (4; 4') will be fed again, as in the operating regime in the conventional expansion machine, with steam from at least one evaporator (2; 3), with the steam supply from the steam reservoir (21; 30) will only be stopped when the steam tank (21; 30) is completely emptied or until a defined remaining amount.
    [0006]
    6. Process according to any one of claims 1 to 5, characterized in that when a maximum working pressure of the steam accumulator (21; 30) is reached during the steam accumulation phase, a line bypass (25) I short the expansion machine, (4; 4'), will be released and/or opened.
    [0007]
    7. Process according to any one of claims 1 to 6, characterized in that during the thrust and/or engine braking phases, the combustion engine exhaust gas system serves as a heat source for at least one evaporator (2; 3), especially when the combustion engine in the exhaust gas section has at least one throttling set to generate the engine braking potential, and/or the steam accumulator (30) is being heated by the gas exhaust from the combustion engine.
    [0008]
    8. Process according to any one of claims 1 to 7, characterized in that the steam accumulated in the steam reservoir (21; 30), especially in the deactivation of the combustion engine and/or in the case of winter temperatures, is used for blowing and flowing condensing working medium from functional components (2, 3 17, 16, 18) of the working medium cycle.
    [0009]
    9. Device for implementing a process for recovering heat and its transformation into mechanical potential in a drive system for motor vehicles, especially for carrying out a process according to one of the preceding claims process, with a combustion engine as a service source , an expansion machine (4; 4') operationally linked with a combustion motor that is coupled to at least one evaporator (2, 3) that can be heated by the exhaust heat of the combustion engine, which evaporator is integrated in a working medium cycle with at least one condenser (5), characterized in that in a precursor line (16) of the working medium cycle, downstream of at least one evaporator (2, 3), at least one valve (17, 23) that can be commanded and/or regulated in a command and/or regulation set is integrated, whereby, with the unnecessary drive potential of the expansion machine (4; 4') and /or with the com engine buston not operated in a lit form the precursor line (16) can be joined with a steam reservoir (21; 30) and/or the expansion machine (4; 4') can be locked.
    [0010]
    10. Device according to claim 9, characterized in that in the precursor line (16) a multi-way valve (17) is provided by means of which the expansion machine (4; 4') and/or the reservoir of steam (21; 30) can be coupled with at least one evaporator (2, 3).
    [0011]
    11. Device according to claim 9 or 10, characterized in that in the valve (17) that feeds the steam into the steam reservoir (21; 30) especially a multi-way valve (17) which introduces the steam into the reservoir valve (21; 30), this valve, especially multi-way, is additionally coupled with a bypass line (25) which shorts the expansion machine (4; 4'), preferably a bypass line (25) with a throttling valve 24, whereby through the valve (17) which introduces the steam or steam reservoir (21; 30) and/or the expansion machine (4; 4') and/or the bypass line (25) can be joined with the line of travel (16) and therefore with at least one evaporator (2, 3).
    [0012]
    12. Device according to any one of claims 9 to 11, characterized in that a bypass line (25) that shorts the expansion machine (4; 4'), flows downstream of a rebound valve (19) arranged in the exhaust steam line (18), this exhaust steam line (18) extending in the expansion machine (4; 4') towards the condenser (5).
    [0013]
    13. Device according to any one of claims 9 to 12, characterized in that the steam accumulator (21), through a pressurized line (22) that has a controllable valve (23), is joined with the precursor line of a valve (17) which controls the entry of steam into the steam tank (21; 30) especially a multi-way valve, and upstream of the expansion machine (4), being connected thereto.
    [0014]
    14. Device according to any one of claims 9 to 13, characterized in that the steam reservoir (30) through a pressurized line (31) which has a controllable valve (23), is connected in parallel with the precursor line (16a), with a pressure-reducing region (4) of the expansion chamber of the expansion machine (4').
    [0015]
    15. Device according to any one of claims 9 to 14, characterized in that an evaporator (2, 3) is coupled with an exhaust gas system with combustion engine and/or a steam reservoir (30) or the housing (30a) is heated through the exhaust gas conducting system of the combustion engine.
    [0016]
    16. Device according to any one of claims 9 to 15, characterized in that the steam accumulator (21; 30) through a controllable valve (26) and a blow-flow line (27) is coupled to one inlet side of at least one evaporator (2, 3).
    [0017]
    17. Device according to any one of claims 9 to 16, characterized in that the steam accumulator (30) has several chambers (30b) that through overpressure valves, especially filling valves (2) and emptying valves (33) are so intercoupled that their filling is sequentially or reciprocally separated and their emptying occurs sequentially or essentially together and/or the steam reservoir (21; 30) by at least one line of condensate (28) is connected with the working medium cycle downstream of the condenser (5), and/or the usable volume of the steam reservoir (21; 30) is shaped in such a way that a corresponding mass of steam can be reserved. to medium operating stages of braking.
    [0018]
    18. Device according to any one of claims 9 to 17, characterized in that several evaporators (2, 3) are coupled to the combustion engine exhaust gas conducting system, which are connected with a pipeline (7a , 7b) in the cycle of the working medium, the line is adjustable through a flow regulating valve (10) and a precursor line (16) preferably assembled, and that through the current regulating valves (10) in a controlled and/or adjusted individually, in group or together can be subject with the service medium.
    [0019]
    19. Device according to any one of claims 9 to 18, characterized in that the cycle of the working medium on the liquid side is provided for a feed pump (8) that supplies the evaporators (2, 3) from the reserve container (6), an exhaust pump (14) positioned upstream of the condenser (5) and transporting to the reserve container (6), preferably a filter (15) interposed and a pressure limiting valve 12 with a recycle line (11) for the feed pump (8), being provided in relation to the reserve container (6).
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    同族专利:
    公开号 | 公开日
    US9051851B2|2015-06-09|
    MX2012003831A|2012-12-21|
    BR102012017039A2|2015-08-04|
    CN102865155B|2016-08-10|
    US20120324891A1|2012-12-27|
    CN102865155A|2013-01-09|
    EP2660432A1|2013-11-06|
    DE102011105709A1|2012-12-27|
    EP2660432B1|2018-12-26|
    RU2012121569A|2013-11-27|
    RU2618803C2|2017-05-11|
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    法律状态:
    2015-08-04| B03A| Publication of a patent application or of a certificate of addition of invention [chapter 3.1 patent gazette]|
    2018-12-11| B06F| Objections, documents and/or translations needed after an examination request according [chapter 6.6 patent gazette]|
    2019-12-17| B06U| Preliminary requirement: requests with searches performed by other patent offices: procedure suspended [chapter 6.21 patent gazette]|
    2020-12-01| B06A| Notification to applicant to reply to the report for non-patentability or inadequacy of the application [chapter 6.1 patent gazette]|
    2021-05-11| B09A| Decision: intention to grant [chapter 9.1 patent gazette]|
    2021-07-13| B16A| Patent or certificate of addition of invention granted|Free format text: PRAZO DE VALIDADE: 20 (VINTE) ANOS CONTADOS A PARTIR DE 20/06/2012, OBSERVADAS AS CONDICOES LEGAIS. |
    优先权:
    申请号 | 申请日 | 专利标题
    DE102011105709A|DE102011105709A1|2011-06-22|2011-06-22|Method and apparatus for recovering heat and converting it to mechanical power in a drive system for motor vehicles|
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