Combustion furnace for heating fluid in a high temperature range (Machine-translation by Google Tran

专利摘要:
Combustion furnace to heat fluid in a high temperature range, formed by two fluid circuits that are immiscible with each other, with a common separation boundary, which is the thermal transfer surface, through which heat flows from the smoke circuit to the circuit of the heat carrier fluid, which is the object to be heated, in a high temperature range. To keep this range so high, the fumes are recirculated in a certain fraction, inside the combustion chamber, and the fraction of smoke that escapes into the atmosphere yields its heat to the incoming clean air. To make the recirculation viable, air jet pumps are used. (Machine-translation by Google Translate, not legally binding)
公开号:ES2660907A1
申请号:ES201800004
申请日:2018-01-09
公开日:2018-03-26
发明作者:Francesc Martínez-Val Piera
申请人:Francesc Martínez-Val Piera；Juan Martinez-Val Piera；
IPC主号:

专利说明:

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COMBUSTION OVEN FOR PE FLUID HEATING IN A HIGH RANGE OF TEMPERATURES
SECTOR OF THE TECHNIQUE
The invention belongs to the field of thermal engineering, particularly in high temperature applications, such as the heating phases of fluids prior to their expansion in turbines.
TECHNICAL PROBLEM TO BE RESOLVED AND BACKGROUND OF THE INVENTION
The problem is to heat, even more, a fluid that comes hot from a previous process. For example, a heat-carrying fluid has been able to be heated to a given temperature in a field of heliostats of concentration of solar radiation, and in order to achieve greater performance in the thermodynamic cycle in which the captured heat is to be used, the temperature of the fluid rises with some additional heat, coming from the combustion of a chemical fuel, such as methane. This is often called hybridization with methane from a solar thermal plant.
To produce this heating of the carrier fluid, it is conducted inside pipes or ducts, which are heated by the fumes resulting from combustion, as well as by the radiation from the walls, reflecting and re-emitting part of the radiation emitted by the flames. and ultra hot objects.
The problem consists in effecting that heating effectively and efficiently, achieving that a high fraction of the enthalpy released in combustion is spent precisely in heating the carrier fluid; taking into account that said fluid already arrives at an elevated temperature, so that only the smoke that is at a temperature higher than the temperature at which the carrier fluid arrives will serve for that heating.
Examples of furnaces for heating various types of materials are large numbers of them, because the furnaces are possibly the
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oldest technical device devised by Humanity, usually accompanied by the myth of fire, and ultimately, combustion.
Despite this reality of prehistoric precedents, there is a limited bibliography for solving the problem indicated, and direct precedents of the invention proposed here do not seem to exist, or at least are not easily identifiable.
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EXPLANATION OF THE INVENTION
The invention is composed of two separate circuits that share a common boundary, which we will call thermal transfer surface, two fluids flowing through said circuits, which are
- the heat-carrying fluid, which goes inside airtight pipes, except at its entrance and its exit, which is driven by pumps or similar machines, the pipes having a configuration that is selected from the various modalities of heat exchangers. heat, which are essentially tubular-shaped conduits, or conduits of rectangular straight section, the outer part of the conduits being bathed by the fluid of the second circuit being in any case, said bath covering what constitutes the thermal transfer surface; and on the other side of said common border is the second fluid, which is:
- the mixed air flow with combustion products, whose movement is activated or deactivated by the impeller machines, selected from compressors, fans and air jet pumps, which discharge their jets through venturi devices located in the places which are detailed in subsequent explanations; producing a partial recirculation of combustion products in the air and smoke mixture circuit, including not only the molecules resulting from a chemical oxidation-reduction reaction, but the gases
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companions in the inlet flow, whereby the circuit through which the mixture of air and smoke flows consists of the following physical parts:
- the atmospheric clean air intake duct, in whose mouth a driving machine is placed, with discharge inwards;
- the passage of the clean air flow through the heat recuperator, where it is heated with the thermal energy that the smoke mixture carries on the way to the evacuation into the air, through the chimney;
- the air inlet duct to the combustion chamber, where the burners or burners are located, forming a pre-mix flame at the beginning, which is completed with a diffusion flame in the upper part of it, in the area called drawer of flames, of refractory walls, and adiabatic-rerradiants, and that also contains perforations that connect the interior of the drawer of flames with the annular space around it, which is the space of contribution of recirculated flow;
- the air and smoke mixing box, where the flames and the immediate combustion products receive the recirculated smoke fraction, flowing from there all mixed;
- ducting duct of said gas mixture, towards the fundamental body of the oven, which is a heater, which is essentially a heat exchanger where the conduits of the heat-carrying fluid are located, whose flow is separated from that of the air mixture and fumes through the border, common, or thermal transfer area;
- the mixture of air and fumes coming out from the side opposite to the one that has entered the heater;
- branching off at two different flows:
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- a recirculation flow, which is channeled to the annular space around the flame box, with the mixing drawer above it;
- an exhaust flow, which is directed towards the chimney or smoke evacuation device, which are mixed with residual combustion air:
- passing this exhaust flow through a heat exchanger called recuperator, in which part of its enthalpy is transferred to the clean inlet air, which is the one that circulates through the atmospheric clean air intake duct, presented in the first line of the Description of this circuit.
The chemical formula of the fuel, its lower calorific value, the fuel rate, in mass burned in the burners per unit of time, the mass flow of clean air introduced into the oven, measured in excess over the air just to make the combustion according to the stoichiometry of the reaction, and the recirculation fraction, determine the enthalpy balance that allows heating the heat-carrying fluid, as prescribed in the method of materialization of the invention.
The recirculation fraction, and the general movement of the gases, are determined by the pressure profile that is created in the various parts of the smoke and air circuit, thanks to the action of all types of driving machines, such as fans, jet compressors and pumps. These are particularly useful in very high temperature conditions, and are activated by the discharge of a gas, usually clean, previously compressed air, tempered to the temperature required by the case, so that the speed of sound in the fluid acquires the value that desired, and also the appropriate Mach number for a specific application is reached.
A fundamental objective of the invention is to achieve high performance in the transmission of heat from combustion to the carrier fluid, for
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which have to avoid very high temperatures in the products of combustion, because if there were, they would increase the thermal losses.
The indispensable regulation of the recirculation is carried out by activating the jet pump injectors with greater or lesser dynamic pressure, defining said pressure by half the product of the density by the square of the velocity. When the temperature is measured too high in the thermometric sensors located in the mixing drawer, the appropriate temperature must be recovered by increasing the recirculation fraction. And vice versa, the fraction should decrease when the mixture of fumes and air is below the reference temperature.
Activation of the mixture also occurs naturally, through the holes that pass through the wall that separates the drawer of flames, from the peripheral ring of arrival of the smoke-air mixture to the combustion chamber. When the flames are very alive, they produce acceleration of their fumes, and therefore a suction or depression, which drags the peripheral smoke through the mentioned holes, with which the mixture begins earlier, and the flame is attenuated. On the contrary, if the clean air that arrives, with the fuel, into the drawer of flames, produces little liveliness of the flame, the effect of suction will not occur with such intensity, so that the mixture between flames and recirculated flow will occur later, when both fluids have reached the mixing drawer. This will have had time to develop complete combustion in the flame, if it is more deadly.
As regards the circuit of the heat-carrying fluid, as regards the invention, this is limited to a plurality of tubes or pipes that occupy a high volume fraction of the heating exchanger; and the outer surface of said pipes or conduits is the common border of the heat-carrying fluid, with the flow of air and smoke mixture, that border being what functions as a thermal transfer area in the heating exchanger.
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EXPLANATION OF THE FIGURES
The figures, in general, are not to scale, since the relative sizes of the elements are very different, and not all the elements would be appreciated; but they are representative of the invention and its operating principles.
Figure 1 shows a diagram, in straight section, of the device as a whole.
Figure 2 shows the scheme of the central part of the device, which is the flame box and the mixing zones.
Figure 3 shows a bundle of tubes through which the heat carrier fluid passes, the straight section of said beam being a quadrangular arrangement.
Figure 4 corresponds precisely to a detail view of said quadrangular arrangement.
Figure 5 corresponds to the straight section of the heater at its furthest end of the combustion zone, the peripheral part through which the recirculated flow to said combustion zone returns.
Figure 6 represents an air jet pump.
Figure 7 represents a temperature scale in which the recirculation process is schematized.
Figure 8 is a qualitative Cartesian representation that in abscissa reflects the relative location of the components, and the length that these have, and in ordinates the pressure value is represented.
In order to facilitate the understanding of the figures of the invention, and of their embodiments, the relevant elements thereof are listed below:
1. Burners or lighters
2. Box of flames
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3. Walls of the flame box
4. Annular space for recirculation flow contribution
5. Isolator for outflow and recirculation flow
6. Recirculation duct
7. Mixing drawer
8. Furnace Vault
9. Air jet pump
10. Tube bundle that configures the heater. In Figure 8, the smoke circuit that passes through the outside of beam 10 is identified with 10.
11. Beam tube outlet closure plate 10
12. Outlet of beam 10, from the oven assembly
13. Internal insulator that separates the fluid flow inside the heater, from the recirculation
14. External wall (insulated or insulated) of the device assembly
15. Recirculation duct, which wraps around the entire heater
16. Beam inlet closure plate
17. Beam input
18. Manifold through which the mixed fluid comes out, after passing through the heater
19. Part or fraction of heater flow, which is evacuated
20. Fraction of the mixture flow that, at its outlet from the heater, is recirculated.
21. Heat recovery smoke to air. It has logically two separate circuits, with a common border surface. A circuit is that of clean air, identified by 21a; and another is the smoke outlet, identified as 9pm. Additionally, the heat recuperator of the fumes to be evacuated can be used to heat the clean, compressed air used in the
jet pumps 9, and employing tank 36 for compressed air storage. This air can be heated using the above smoke, which would be done in a section of the recuperator, which we identify as 21c.
5 22. Fume extractor
23. Smoke evacuation
24. Driving clean air to the burners
25. Clean air impeller
26. Clean air inlet
10 27. Air-fuel pre-mixers
28. Through holes in the walls (3) of the flame box
29. Set of tubes of a beam whose virtual axes coincide in the same virtual plane. This set is called a tube plate.
15 30. Virtual line that aligns the centers of the elbows of all
tubes of an iron of them, of a quadrangular beam.
31. Line that marks the orientation of the tubes of an iron, before a certain elbow. The acute angle formed by lines 30 and 31 is called the projection angle.
20 32. Tube of a quadrangular arrangement
33. Extreme points on the side of a square of the beam tube reticule of a heating exchanger
34. Jet pump jet
35. Jet pump valve
25 36. Jet pump overpressure tank
37. Jet air supply compressor
38. Air intake of the jet pump
39. Venturi, to induce higher velocity to the base fluid
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40. Conduction (of any straight section, not necessarily a tube) in which a jet pump operates
41. Heat transmission from the mixing flow, to the heat-carrying fluid
42. Heat transfer from the evacuated mixture flow, to the clean air that enters.
In addition to the previous numbers, in Figure 7 identifying labels composed of the letter T are used followed by a number, which indicates the (absolute) temperature of the point indicated by the number in question.
Similarly, in Figure 8, identifying labels composed of the letter P are used followed by a number, indicating the pressure of the point indicated by the number in question.
The following capital letters are also used, representing the mass flow or expense (in kg / s) that flows through the indicated conduit, and that corresponds to
A: mass consumption of clean air blown into the combustion chamber H: mass expenditure injected with fuel
J: mass expenditure of air jet pumps (in principle, pre-compressed clean air
B: mass flow rate evacuated = A + H + J
R: recirculated mass expenditure (equal to x-M)
M: mass expenditure circulating through the heater, corresponding to the mixture flow, which goes outside the tubes.
G: mass expenditure of the fluid that carries the heat, and goes inside the tubes or conduits of the beam 10
EMBODIMENT OF THE INVENTION
The invention is constructed as a conjunction of the circuit of recirculated fumes and the bundle of pipes or pipes that constitute
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the circuit through which the heat-carrying fluid goes, which will use it for the purpose that is relevant.
The materials of the combustion chamber and its recirculation circuit of fumes mixed with air are of the refractory type, including refractory steels, although the option of selecting a ceramic or metallic envelope can be made by the designer depending on the temperatures of operation, available budget, and expected duration of installation.
It should be noted, on the issue of measurements, that when combustion is carried out at atmospheric pressure level, the sizes must be large, since there are no high power densities, unless the air and fumes moved at speeds very high This would be counterproductive in the face of recirculation, which requires a pressure map that is now detailed, and that it is all the more difficult to meet the greater the manometric load losses in the various sections of the smoke circuit; which increases more the faster the movement is performed.
Note that the pressure at point 18 at the outlet of the exchanger, smoke circuit, will be less than the pressure in the vault of the combustion chamber 8, which in turn will be somewhat less than that of the annular space around the box of flames (2) and the annular space (4), the latter being the volume to which the recirculated flow has to reach. This forces the jet pumps (9) to provide a driving effect, by dragging the jets on the smoke, that overcomes the loss of manometric load from volume (4) to (18) through the vault (8) and the entire heater exchanger.
The jet pumps will have a dynamic pressure that will be half the density of the fluid they inject by the square of their velocity. Said fluid, in general clean air, may be heated after the pre-compression phase, to give it the overpressure that then becomes kinetic energy of the jet. In the pressure tank itself the air can be heated, with the residual fumes that are
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Discharge as a non-recirculated flow: From this tank the jet propulsion takes place, when opening the corresponding valve, which will have a straight section X (m2) a density Y (kg / m3) and a speed Z (m / s) that will have to comply
XYZ3> (m '/ rho) -AP4-18
Being the last term, AP4.18 the loss of manometric load from 4 to 18, in absolute value; rho the density of the recirculated fluid, and m 'the mass expenditure (kg / s) recirculated.
In Figure 8 you cannot go up without ascending force, which can be achieved by natural convection, (by adding heat, increasing the temperature and decreasing density) or by mechanical drive, with some type of pump, including those of jet (9) or discharge (25) or extraction (22).
To be more precise in the explanation of how the invention is carried out, an alkane of the diesel range, the dean, C10H22, whose combustion equation is the following, will be used as fuel, n being the contribution multiplier of air over the stoichiometry value, which would be that of n = l
C10H22 + n (31/2) 02+ 3.9n (31/2) N2-> 10 C02 + 11 H20 + (n-
l) (31/2) 02+ 3.9n (31/2) N2
It should be noted that 142 g of dean generate fumes whose mass is (in grams) of 142 + 2189n. Most of the mass is the nitrogen of the air itself used to provide oxygen.
In the preceding equation a simplified composition of air has been used, which would correspond to 3.9 molecules of nitrogen for each of oxygen. (The argon of the air, less than 1% in molar fraction, is considered accumulated to the N2, although they are of somewhat different properties, but both inert).
To determine combustion thermometry, the value of the lower calorific value of the dean is evaluated, evaluated at 42.5 MJ / kg. In the combustion of one mole of dean, 142 grams, the heat given off would be 6.05 MJ.
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If we admit a specific isobaric heat of 1.1 J / gK for the smoke (mixture of several molecules, most of N2), the temperature increase occurred, assuming that all the heat goes to the fumes produced, that is, the adiabatic increase ATa is
Uld
6.05 • 106
1.1 • (142 + 2189n)
For pure stoichiometry (n = 1), the adiabatic increase would be 2,536 K, assuming that everything could be burned (which would require a time tended to infinity, since the last alkane molecules would not easily find oxygen to react).
Regarding the mass flows, or expenses, the recirculated fraction is called x (and 1-x is the non-recirculated, or emanated from the exhaust pipe or chimney).
Therefore, x is the recycled fraction of M, which is the global smoke expenditure, the recycled expenditure being R.
In turn, we must have three contributions of mass to the burner circuit, from the outside, which are H = mass fuel expenditure, (mass per unit of time).
J = mass expenditure of the pump or jet pumps that activate the recirculation, by means of discharging into a recirculation duct, a jet or stream of air (compressed and slightly heated), therefore being non-vitiated air It must be counted as such, in addition to the drag effect it has due to its dynamic pressure (pv2 / 2). Note that with a density of 1 kg / m3 and a v = 10 m / s, this pressure is 50 Pa, very much the level of the suction pressures in air recirculation.
A = expenditure (kg / s) of atmospheric air mechanically insufflated in the burner charge flow.
B = sum of the three aforementioned contributions, which are counted together, as it is not necessary to detail them at a very precise level, given other uncertainties: B = A + H + J
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Measured in mass, the same amount B (kg / s) is injected into the combustion chamber, which is derived from the heater exhaust to the final exhaust
The combustion reaction of the dean, embedded in a recirculation rate x of its own fumes, implies a situation in which a certain expense of alkane must be contributed and completely burned, to release the thermal power E that is needed, and there is to do so by distributing that heat between the molecules of an expense M (g / s) in such a way that the increase of T in the smoke expenditure corresponding to the increase of T that is required in the heat-carrying fluid (with expense) is achieved G and specific heat C, at constant pressure) whereby you have E (W) = GC- (T12-T17)
Since the PCI of the dean is 42.5 MJ / kg, you can write E (W) = g '(g / s) -42,500-nq Where g' is the expense of the dean.
Note that the dean is not introduced alone, but with air, with an excess marked by the dosage factor n. That makes us enter not only g 'into the flame chamber, but an amount of air that weighs 2,189n grams for every 142 grams of injected dean. If we count for (g / s), the expense of the contribution part would be: g '(l + 15.4n)
To which we must add the recycled part, which is the fraction x of what is circulating through the burner, which accumulates according to the geometric series 1 + x + x2 + x3 + x4 + ... = l / (lx )
The recirculation will saturate with a speed that will require less time the smaller the recirculation fraction. For example, for x = 0.2, the average residence time of a smoke molecule in the burner will be 3 times more, measured by the distance to be traveled along the circuit, broken by the average smoke speed. For x = 0.5 it will take about 9 times that time tr.
In stationary equilibrium, the circulating smoke consumption, M (g / s) for a dosage n, and a recirculation fraction x, is M = g '- (l + 15.4n) / (l-x)
The values that are selected in x or in n can now be uniquely determined to obtain the desired values, in n or in x; and the absolute value of g 'is determined to give a certain power E in the heater.
In the first case, the relationship between x and n does not depend on g ', because
it intervenes linearly in the two terms, of mass and energy. He
10 value of the AT Increase in the fumes (1.1 J / g-K being the heat
specific isobar of the fumes) corresponds to
(1 - x) • 42,500
AT - ----------------
1.1 (1 + 15.4 n)
In short, the invention is materialized by the orderly aggregation of components as described in the descriptive list of the elements of the figures; and in the preceding paragraphs the invention has been explained in terms of the two main intensive thermodynamic variables, Pressure and Temperature, with which the materialization of the invention is justified.
Once the invention is clearly described, it is stated
that the particular embodiments described above are subject to modifications in detail as long as they do not alter the fundamental principle and the essence of the invention.

权利要求:
Claims (1)
[1]
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1 - Combustion furnace for heating fluid in a high temperature range, characterized in that the invention is composed of two separate circuits that share a common boundary, which we will call thermal transfer surface, two fluids flowing through said circuits, which They are
- the heat-carrying fluid, which goes inside airtight pipes, except at its entrance and its exit, which is driven by pumps or similar machines, the pipes having a configuration that is selected from the various modalities of heat exchangers. heat, which are essentially tubular-shaped conduits, or conduits of rectangular straight section, the outer part of the conduits being bathed by the fluid of the second circuit being in any case, said bath covering what constitutes the thermal transfer surface; and on the other side of said common border is the second fluid, which is:
- the mixed air flow with combustion products, whose movement is activated or deactivated by the impeller machines, selected from compressors, fans and air jet pumps, which discharge their jets through venturi devices; producing a partial recirculation of combustion products in the air and smoke mixture circuit, including not only the molecules resulting from a chemical oxidation-reduction reaction, but the accompanying gases in the inlet flow, so that the circuit through which the mixture of air and smoke flows consists of the following physical parts:
- the atmospheric clean air intake duct, in whose mouth a driving machine (25) is placed, with inward discharge;
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- the passage of the clean air flow through the heat recuperator (21), where it is heated with the thermal energy that carries the smoke mixture that is on its way to the evacuation into the air, through the chimney or exhaust (23);
- the air inlet duct (24) to the combustion chamber, where the burners or burners (1) are located, forming a pre-mixing flame at the beginning, which is completed with diffusion flame at the top of it , in the area called drawer of flames (2), of refractory walls, and adiabatic-rerradiants, and that also contains perforations (28) that communicate the interior of the drawer of flames with the annular space (4) around it, which is the recirculated flow contribution space;
- the air and smoke mixing box (7), where the flames and the immediate combustion products receive the recirculated fraction of fumes, flowing from there all mixed;
- channeling vault (8) of said gas mixture, towards the fundamental body of the oven, which is a heater, which is essentially a heat exchanger where the conduits (10) of the heat-carrying fluid are located, whose flow is separated from the of the mixture of air and fumes through the common border, or thermal transfer surface;
- the mixture of air and fumes coming out from the opposite side (18) to which they have entered the heater;
- branching off at two different flows:
- a recirculation flow (20), which is channeled to the annular space around the flame box, with the mixing drawer above it;
- an exhaust flow (19), which is directed towards the chimney or smoke evacuation device, which are mixed with residual combustion air:
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- passing this exhaust flow through a heat exchanger called recuperator (21), in which part of its enthalpy is transferred to the clean inlet air, which is the one that circulates through the aspiration duct of atmospheric clean air (24).
2 - Combustion furnace for heating fluid in a high temperature range, according to claim one, characterized in that the recirculation fraction, and the general movement of the gases, are determined by the pressure profile that is created in the various parts of the smoke and air circuit, thanks to the action of all types of driving machines, such as fans, compressors and jet pumps (9); these being particularly useful in very high temperature conditions, and are activated by the discharge of a gas, usually clean, previously compressed air, tempered to the temperature considered; and the recirculation is carried out by activating the injectors of the jet pumps with greater or lesser dynamic pressure, said pressure defining half the product of the density by the square of the velocity; so that when the temperature is measured too high in the thermometric sensors located in the mixing drawer, the recycle fraction is increased giving more dynamic pressure to the jet; and the dynamic pressure of the jets is reduced when the mixture in the mixing drawer (7) is below the reference temperature.
3 - Combustion furnace for heating fluid in a high temperature range, according to claim one or two, characterized in that the activation of the mixture also occurs naturally, by means of the orifices (28) that cross the wall (3) that separates the flame drawer (2), from the peripheral ring (4) of the arrival of the smoke-air mixture to the combustion chamber; and when the flames are very alive, they produce acceleration of their fumes, and therefore a suction or depression, which drags the peripheral smoke through the mentioned holes, with which the mixture begins earlier, and the flame is attenuated; and on the contrary, if the clean air that arrives, with the fuel, to the drawer of flames, produces little liveliness of the
flame, the suction effect will not occur with such intensity, so the mixture between flames and recirculated flow will occur later, when both fluids have reached the mixing drawer (7).

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ES2660907B2|2018-10-04|

引用文献:

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GB750092A|1952-04-21|1956-06-06|Bailey Meters Controls Ltd|An improved method of and apparatus for regulating the temperature of a fluid|

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US4109613A|1976-06-05|1978-08-29|Foster Wheeler Energy Corporation|Steam boilers|

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GB1583808A|1976-12-20|1981-02-04|Electric Power Res Inst|Convective heat transfer steam boiler for fuels of low energy and ash content|

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CN204127939U|2014-09-03|2015-01-28|上海汉鼎环保技术工程有限公司|With the steam generator system of cold flue gas recirculation|

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优先权:

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ES201800004A|ES2660907B2|2018-01-09|2018-01-09|Combustion furnace for heating fluid in a high temperature range|ES201800004A| ES2660907B2|2018-01-09|2018-01-09|Combustion furnace for heating fluid in a high temperature range|