CN86104890A - The thermodynamic conversion system of air circulation - Google Patents
The thermodynamic conversion system of air circulation Download PDFInfo
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- CN86104890A CN86104890A CN86104890.3A CN86104890A CN86104890A CN 86104890 A CN86104890 A CN 86104890A CN 86104890 A CN86104890 A CN 86104890A CN 86104890 A CN86104890 A CN 86104890A
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
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- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E20/00—Combustion technologies with mitigation potential
- Y02E20/14—Combined heat and power generation [CHP]
Abstract
The air circulation thermodynamic conversion system utilizes the interstage cooler between every pair of adjacent compressor, certain gas of compression in the multistage compression process.Before the squeeze operation that respectively continues, interstage cooler makes the pressurized gas temperature get back to room temperature.In the heat exchanger, pressurized gas is heated to increase its heat energy the heat exhaust gases that flows through with it.Having two strands of air-flows of thermal capacity about equally by establishment keeps adding and pines for the minimum temperature gradient between the waste gas in pressurized gas and the cooling.Add hot compressed gas and in turbine, expand, to produce the moment that is enough to drive multi-stage compression system at least.In most preferred embodiment, the working gas in compressor, interstage cooler and the turbine is an air.
Description
The present invention relates to the heat power conversion equipment, more particularly, relate to and use the heating power conversion equipment of air as working medium.
Some heat power conversion or chemical process can produce a large amount of by-product hot gas that contains enough heat energy, are energy saving, go to collect and utilize this heat energy to attract much attention.For example, gas turbine has the fuel of air to produce various hot gas a firing chamber internal combustion.When expanding, these hot gas produce moment in gas-turbine.Part moment is used to drive an air compressor-give the firing chamber with pressurized air.All the other moments are used on the output shaft.
The temperature of discharging the waste gas of gas turbine is about 1000 °F.When this hot waste gas was discharged into atmosphere, a kind of like this thermodynamic efficiency of gas turbine was lower, (for example, comparing with steam turbine).Although its efficient is lower, because gas turbine can provide quick starting and operation flexibly, it is a kind of for producing peak power and the prime mover in marine propulsion system to have impelled it to be used as.
The steam boiler that reclaims heat generally forms the circulatory system of a steam and gas turbine combination with the gas turbine cooperation.The heat recovery steam boiler is drawn the quite most of heat energy that is present in the waste gas, thus the generation steam-by any using process, just can be applied.The circulatory system of this combination, its total efficiency is higher than the efficient of steam turbine.
The circulatory system of steam and gas turbine combination has many shortcomings.Steam is the medium that is difficult to splendid attire and manipulation.For example, for fear of the corrosion and the fouling of the water of heat recovery steam boiler side, must handle meticulously make-up water, to guarantee its purity.For the equipment that obtains this pure water is expensive.In addition, the heat recovery steam boiler is huge device and the actual real estate that needs to drop into substantial contribution.
The response that the heat recovery steam boiler changes required output than gas turbine slowly many.Cold starting (cold start) for the heat recovery steam boiler, need continue for some time-for example, 2 hours, during this period of time, output power is only produced by gas turbine, simultaneously, the water in the waste heating heat recovery steam boiler of gas turbine makes it reach operating temperature and pressure.When not utilizing the output of heat recovery steam boiler, need closing (shut-down) cycle again corresponding to starting cycle.If steam and gas turbine engine systems move 16 hours every day, then wherein the operation of depending merely on gas turbine in 4 hours to be arranged, make the heat recovery steam boiler be heated to working state, or make it be cooled to state of rest.Like this,, output power is provided and has improved efficient, be less than its total working time its working lipe significantly by the heat recovery steam boiler though the starting that provides by gas turbine and the flexibility of operation have been provided.
I find: during draw heat, can obtain the maximum heat dynamic efficiency from the hot gas with (emit the medium of heat and receive between the medium of heat) minimum thermal gradient.Producing steam must have such zone promptly in this zone, and the medium in heat exchange water keeps constant temperature, and water just flashes to steam.About the rule of minimum thermal gradient, thereby reduced and from hot waste gas, to absorb and pass to the quantity of an energy in the application process above this process is run counter to.Countless production and chemical process need be supplied a large amount of heat, unpolluted pressurized air.Unpolluted airborne oxygen is also without burning, otherwise in combustion process, most of oxygen wants burned product (generally include carbon dioxide, carbon monoxide, the fuel that burns incompletely and under solid-fuelled combustion case, carry fuel, dust and slag particle secretly) to substitute.The circulatory system of steam and gas turbine combination is not requiring that independent hardware goes to produce under the situation of pollution-free air, with regard to the supply of unavailable this pollution-free air.
The temperature of leaving the flue gas of steam and the gas turbine combination circulatory system is approximately 270 °F.Though this means a kind of significant waste of energy, because the existence of etching reagent (mainly being sulphide), as long as its temperature reduces greatly just and can separate out from flue gas, it is unpractiaca therefore reclaiming heat with conventional method from flue gas again.Otherwise, concerning heated exhaust flow, require not have this temperature restraint.Can be reduced as much as possible in the temperature that does not produce heated air under the situation that harmful matter separates out, the temperature that reduces this hot air makes in it contained moisture content separate out at the most.And this water of being separated out may be a kind of commodity that economic value is arranged under some environment.
Therefore, an object of the present invention is to a Combined Cycle system is provided, this system comprises that a gas turbine-its thermodynamic efficiency is higher than the efficient of single gas turbine, and keeps the operating flexibility of gas turbine.
Another object of the present invention provides a kind of Combined Cycle system, this system applies air-lock circulation.Reclaim heat energy in the heated air stream in a kind of favourable mode.
Another purpose of the present invention is to remove pressurized air with have intercooled multistage compression process at least between two stage compression.Before pressurized air entered with the hot air flow exchange, middle cooling was cooled to alap temperature with it earlier.Make heat exchange begin from the minimum temperature gradient between hot air flow and the air stream to carry out, thereby obtain the maximum heat efficiency of transmission.By MAF being controlled to some values, strengthen this minimum thermal gradient effect with the thermal capacity that is substantially equal to the hot gas capacity.
Another object of the present invention is for the circulation of a kind of air-lock is provided, and this circulation comprises auxiliary combustion, to increase the heat energy in the heated pressurized air.
Briefly, the invention provides an air circulation heat power converting system, in this system, utilize the interstage cooler between every pair of adjacent compressor, compress certain compressible gas with the multistage compression method.Interstage cooler makes the temperature that is compressed gas turn back to each squeeze operation in succession ambient temperature before.Be compressed hot waste gas heating that gas driven in the wrong direction with it and increased its heat energy in a heat exchanger.By establishing the pressurized gas heating and the waste gas two plume measurers in the cooling roughly the same thermal capacity is arranged, keep the minimum temperature gradient between them.Heated pressurized gas expands in a turbo machine, to produce the moment that is enough to promote multi-stage compression system at least.In this turbo machine, may produce the additional moment that is used to drive certain using process.In other words, when the heat that is heated gas exceeded for the needed amount of driving turbo machine, the heat that exceeds can directly be sent in certain using process.In addition, can be used to come draw heat from the heated medium of interstage cooler and from the waste gas of turbo machine.In most preferred embodiment, the working gas in compressor, interstage cooler and turbo machine is an air.
According to one embodiment of present invention, the thermodynamic conversion system that is used to absorb the heat that is heated gas stream that is provided comprises: first and second (at least two) air compressor that is used for compress ambient air, interstage cooler between at least the first and second compressors, (this interstage cooler comprises the device that is used to reduce temperature, this device will make first pressurized air that comes from first air compressor before it enters second air compressor, reduce to about room temperature), heat exchanger (be included as the heat conversion equipment that produces heated compressed air-change second pressurized air into) from second air compressor from the heated air circulation, according to this heated compressed air, at least one air turbine drives at least one air compressor in first and second air compressors, described heated compressed air includes to exceed by at least one air turbine and drives the required energy of at least one compressor in first and second air compressors, and this heat exchanger also comprises the transmitting set that this part excess energy is transferred to a using process.
According to a device of the present invention, an air-lock circuit Combined Cycle system of being equipped comprises a gas turbine, (this gas turbine comprises again in order to produce the device of hot air flow), a heat exchanger, first, the second and the 3rd air compressor, be used to connect first, the connection set of the second and the 3rd empty compressor (these three air compressors be used for pressurized air), one first interstage cooler (being disposed between first and second air compressors in the connection set), one second interstage cooler (between the second and the 3rd air compressor in connection set), the device that is associated with first and second interstage coolers (being used for the temperature by the air is reduced to about room temperature) there, above-mentioned heat exchanger comprises the device that is used to transmit heat, this device heat of heating air flow is passed to pressurized air from the 3rd air compressor, thereby produce heated compressed air, at least one air turbine (air turbine) responds this heated compressed air and goes to drive above-mentioned first, the second and the 3rd air compressor, heated compressed air comprises exceeding by at least one air turbine and goes to drive first, the surplus of the second and the 3rd air compressor institute energy requirement, above-mentioned heat exchanger also comprises the transmitting set that is used for excess energy is delivered to using process.
Above-mentioned and other purposes of the present invention, feature and advantage will be from below in conjunction with seeing clearlyer the description of the drawings, in the accompanying drawing, same numeral is indicated identical component.
Fig. 1 is a schematic representation according to the steam of prior art and the gas turbine combination circulatory system.
Fig. 2 is theoretic temperature one entropy diagram, in the desirable locking cyclic process of explanation gas turbine, and will be with reference to this figure.
Fig. 3 is a locking circuit temperature-entropy diagram that the heat recovery steam boiler is used.
Fig. 4 is the simplification schematic diagram with an air-lock circuit Combined Cycle system, and this system adopts the two-stage air compression, cooling in the middle of having between two compression stages.
Fig. 5 is a temperature entropy diagram of Combined Cycle shown in Figure 4 system.
Fig. 6 is the temperature-entropy diagram of a Combined Cycle system that includes the air closed loop of Pyatyi air compression.
Fig. 7 has an air-lock circuit Combined Cycle system, and this system has three air compressors (interstage cooler is arranged) and two to be used to drive the independently air turbine of output shaft and jack shaft (intershafts).
Fig. 8 is simplification principle feature (closeup) figure for air-lock circuit temperature of the present invention and load control.
Fig. 9 is the simplification schematic diagram of a Combined Cycle system, and in this system, it is the hot air that has compressed that the air-lock circuit is mainly exported.
Figure 10 is the close up view of simplification principle of the heat exchanger of a Combined Cycle system, with the auxiliary combustion of gas side that this exchanger is described.
Figure 11 is the close up view of simplification principle of the heat exchanger of a Combined Cycle system, with the auxiliary combustion of air side that this exchanger is described.
Referring to Fig. 1, the figure illustrates according to the steam of prior art and the circulatory system 10 of gas turbine combination.Gas turbine 12 comprises compressor 14-compress ambient air effectively, so that it reacts with fuel in firing chamber 16.Hot gas (air and the products of combustion that comprise unreacted) from firing chamber 16 is sent to turbine engine 18, and produces an output torque on output shaft 20 within it effectively, goes Driven Compressor 14 by jack shaft 22 simultaneously.
Under about 1000 temperature, discharge turbine engine 18 after above-mentioned gas expands, be transported to heat recovery steam boiler 26 through waste gas duct 24.These hot gass are emitted quite most of heat energy in heat recovery steam boiler 26, to produce steam, the steam that is produced is sent to certain traditional using process by steam pipeline 28 again.This using process, (for example can be a steam turbine, the boiler of steam turbine or chemical process) it doesn't matter to the present invention, so be not described further in addition.Temperature is reduced to about 275 hot gas and is discharged into atmosphere by outlet pipe 30.Make-up water or condensing steam enter heat recovery steam boiler 26 by water pipe 32.
Those skilled in the art knows that surely heat recovery steam boiler 26 for improving 2 its thermodynamic efficiencys, may comprise numerous parts, and this base part can be (for example) feed water preheater, recovering device, superheater.All these all belong to conventional components, so need not explain in addition or illustrate it.
Now referring to Fig. 2, this figure is the temperature-entropy diagram of (a being shown in broken lines) gas turbine cycle 34.This gas turbine inhaled air has room temperature and by point 36 represented pressure.This air is in compressor 14, and (neither heating is not also under the situation of heat extraction) compressed along vertical adiabatic compression line 38 adiabatic ground, and its temperature and pressure raises during this period.In the firing chamber 16 li, to this pressurized air along 40 heating of constant voltage line until the vitiated air that becomes heat-contain products of combustion, 42 places discharge firing chamber 16 at point.This hot gas expands until the exhaust gas temperature that reaches waste gas point 46-gas turbine along vertical adiabatic expansion line 44 adiabaticly.Connect waste gas point 46 and put 36 constant voltage line 48 closures the circulation loop 34 of gas turbine.
As well-known, the area in gas turbine cycle loop 34 has promptly been represented the heat energy that this process produced.By total available energy that energy produced of consuming between the compression and the period of heating is the gross area that vertical line surrounded between constant voltage line 48 and the room temperature line 50.This has represented the unrenewable that part of energy of gas turbine engine systems (because of its exhaust gas temperature height) by the leg-of-mutton power consumption district 52 that elongation line limited of room temperature line 50, constant voltage line 48 and vertical adiabatic expansion line 44 usually.Reclaiming the heat energy in the energy consumption district 52 as much as possible, promptly is locking circuit purpose.
Fig. 3 shows as a steam locking circuit temperature-entropy diagram.For the purpose of observing, water and steam afterwards are to flow through heat exchanger (heat recovery steam boiler 26) to face toward from the hot air flow direction of gas turbine 12.Can see by the relation of each the steam lines of the each several parts constant voltage line 48 near and point and to show: the relation between temperature-entropy when its adjacent water or steam heated of reaching of the relation when hot gas cool off between the entropy of its temperature.
Beginning, water point 54 low approach under ambient temperature and the pressure pressurized, then along 56 heating of water-heater wire until reaching its boiling point 58.Because boiling, water along the boiling line 60 of steady temperature, increase its heat energy under constant temperature.After this, steam is under constant voltage, along the promptly overheated through exhaust gas temperature that approaches gas turbine to some 66-of line 62.Energy in the pressure steam of heat expands along vertical adiabatic expansion line 68 in (for example) steam turbine (not shown), and is through to room temperature line 50.The final increment of cool to room temperature line 50 needs heat dissipation in the condenser (not shown) of a routine.Yet be enough to hypothesis concerning current discussion: the whole energy in the steam at point 66 places all are callable.This figure is along room temperature line 50 closures, the room temperature line can be represented with regard to the thermal losses that at room temperature causes owing to vapour condensation as being produced in the condenser of a routine, to form steam turbine locking circulation 70, the circulation of heat is reclaimed in this circulation representative from GTE by the steam circulation.
People can notice: can find the worse cooperation in a place on the interface between gas turbine cycle 34 and the steam turbine locking circulation 70.That is exactly that in steam turbine locking circulation 70, water is converted into during this part of steam, produces one and be generally the not triangle gap 72 of recovered energy in this locking circulation.Therefore, steam turbine locking circulation 70 is actually whole energy that can not obtain in the GTE.
I find: the many problems that are present in inherently in the heat recovery of steam locking circuit can be by adopting certain gas, and (preferably adopting air) overcomes as working medium.Now, have air-lock circuit Combined Cycle system (totally by 74 expressions) referring to Fig. 4, will be by waste gas duct 24 from the hot gas guiding of gas turbine 12, by heat exchanger 76.First order compressor 78 is with first compression multiple (for example, about twice) compress ambient air.
Simultaneously with reference to the corresponding temperature-entropy diagram among the figure 5, first order compressor 78 improves the temperature of air along vertical compression line 80 now.Pressurized air is sent to interstage cooler 82 by first order compressor 78, and this cooler 82 makes pressurized air get back to along constant voltage line 84 and approaches room temperature.After centre cooling, pressurized air again in second air compressor 85 along second vertical compression line 86(Fig. 5) be compressed, till its temperature approaches relevant temperature on the constant voltage line 48.
From the pressurized air of second air compressor 85 is facing to flowing through heat exchanger 76 from the hot waste gas of gas turbine 12, to draw the heat in the waste hot gas.This circuit heat exchanger is partly represented with constant voltage line 88.When this air was discharged heat exchanger 76, its temperature was very near the temperature of GTE.This heated compressed air expand and finish closed air turbines circulation 91 90 li of air turbines.When heated air expands, on output shaft 92, produce an output torque in air turbine 90, on jack shaft 94, produce compressor moment simultaneously, so that drive the first order compressor 78 and second air compressor 85.Because this pressurized air do not need evaporation stage, so when it heats, the temperature that its temperature still keeps approaching hot gas from gas turbine 12 when cooling off.Like this, in heat exchanger 76, be present in heated air and the cooling in gas between temperature gradient be smaller.
I find: airflow rate is determined in such value, when promptly this value has the total thermal capacity of the thermal capacity that is substantially equal to the hot gas that flows through in heat exchanger 76, gas in the cooling and the temperature gradient that adds between the air of pining for can be reduced to minimum.When the mass rate of flow of establishing air and hot gas equated, then the thermal capacity for first approximation equated.The hot air temperature that leaves heat exchanger 76 can be in 95% scope of the hot gas temperature that enters heat exchanger 76.In other words, if when hot gas temperature is 1050 left and right sides, the temperature of hot air can reach about 1000 °F.
Not the various reasons that the optimal heat efficiency of transmission may require the air mass flow dose rate except that this ideal situation, will be illustrated at the rear portion of this specification.
Cooling air delivery air turbine 90 after in air turbine 90, expanding, the temperature on smoke-ejecting pipe 96, (for example) is approximately 450 °F.Because the air in smoke-ejecting pipe 96 is untainted and contains considerable waste heat amount, so also establishing under the situation of its further draw heat in there, will it not be discharged into atmosphere.This waste gas can be used for chemistry or the production process such as the paper oven dry or is used as the air source of fluidized bed combustion process.This waste gas even can be added to another locking circulation that (for example) uses steam generator.
Usually interstage cooler 82 need be used for removing from the air stream between the first order compressor 78 and second air compressor 85 pressurization device of heat.This pressurization device is represented with blower 98, and is driven by any power source of blower easily 100.Blower power source 100 can be (for example), is added to the power supply of blower 98 built-in motors.This power supply may be purchased, if but use output shaft 92 to remove to drive a generator, then use consequent electric power and a special advantage is provided.That is exactly, and when having the Combined Cycle system starting of air-lock circulation 74, blower 98 starts together therewith and produces the air stream that one is cooling off, and this strand air-flow can be automatically be forced to change with the moment output of air turbine 90.On the other hand, blower power source 100 can directly concern with 92 one-tenth gear transmissions of output shaft by conventional gearing (not shown), thereby blower 98 is driven by the direct mechanical connection with ratio certain speed in output shaft 92 speed.
Another alternative plan, by extracting (tapping off) some pressurized air out at the intermediate section of first order compressor 78 and utilizing the air conduct of this extraction to force cooling unit, be used for promoting the cooling procedure in the recoler 82, and cancelled blower 98 and blower power source 100.This is similar to the throughput that is produced by the air inlet blade of a turbofan aircraft motor (the inlet fan of a fan-jet aircraft engine).This arrangement is by 102 promptings of the dotted line among the figure.
People will appreciate that surely:adopt the air of extracting out from first order compressor 78 and do not adopt blower 98 can significantly improve efficient together with electric or Mechanical Driven.Concerning electric driving situation, this method of deflating has been avoided changing the poor efficiency that is caused between electric power and the moment, and has cancelled the many equipment that are included in the blower 98.Concerning direct gear-driven Mechanical Driven, the poor efficiency that this method of deflating has avoided this capital cost and this gear-driven mechanical type to drive.It is sizable being used to cool off the power that is consumed on output shaft 92,500 kilowatts of or bigger of can reach in a big machine.Therefore, cancellation blower 98 and power supply or mechanical actuation device have tremendous influence to capital expenditure and usage charges.
Should not ignore equally: be present in and leave interstage cooler and hot air on smoke-ejecting pipe 104, with it as callable energy source problem.Though this hot air temperature has only 160 °F or 170 °F, but clean, does not have precipitation or etching problem, thereby not treatedly can be used for chemistry or production process.For example, the air quantity of the interstage cooler that is discharged by a plant-scale Combined Cycle system with air-lock circulation 74 can be heated to about 160 °F by room temperature with the water of 3000 gallons of per minutes through low price equipment.Just a kind of cheapness and a large amount of easily thermal water sources can be used for family or industry like this, without lifting an eyebrow.Because this air is clean, so it can be directly used in hot gas space heat supply (hat-air space heating).
The invention is not restricted to adopt air as the interstage cooler that removes thermal medium, but can adopt any suitable interstage cooler technical equipment.For example, can adopt air → liquid interstage cooler, be used for heat is reached certain liquid (for example water) from air.Should think: be used to reduce the steam of working medium temperature or other effectively in the middle of cooling type all within the scope of the present invention.
Now particularly with reference to Fig. 5, we can notice: though constant voltage line 48 is closelyed follow along constant voltage line 88 in the top of air turbine loop 91, and adjacent room temperature line 50 indentions or the pit of its underpart, thereby stayed not recovery section of an energy that draws with dot and dash line.Number by being increased in the employed compressor of air compression function aspects and between every pair of adjacent air compressor, adopt interstage cooler to show and land and reduce this pit effect.
With reference to Fig. 6, the figure illustrates as an example modified model air turbine circulation 91 ', in this circulation, compression duty is finished by a series of (5) compressor and (4) interstage cooler, except last compression, after each compression, interstage cooler all will be reduced to air temperature about room temperature.Several compressors is being shared compression function, thereby every compressor provides a less ratio to the raising of total pressure.Be noted that air turbine circulation 91 ' unusual good fit near with room temperature line 50 in bottom, thereby make not by gas turbine cycle 34 utilized almost all useful poweies become available.
From the heat power viewpoint, perhaps using increase compressor and interstage cooler number increases the efficient of air circulation, yet, from economic point of view, will inevitably recognize: the capital cost that adds compressor, interstage cooler, blower and pipeline, only applying under the situation about go froming bad to worse of expenditure, will soon become and to compensate by improving the efficient profit.In most preferred embodiment, adopted three compressors to be in series with two interstage coolers, as if (between every pair of adjacent compressor an interstage cooler being arranged) provide a kind of compromise proposal of satisfaction between air cycle efficiency and investment cost.
Concerning a multistage compressor system, and do not require that the compression ratio of the compressor that they are all equates.On the contrary, there is cogent reason to impel people in a plurality of compressors, to use different compression ratios.For example, the efficient of first and last compressor in three grades of series connection compression systeies may show as not as the intergrade compressor efficiency.Therefore, preferably obtain than from first and the last stage compressor required total compression amount of vast scale more from the intergrade compressor.For example, when requiring overall compression ratio to be 20, then improved comprehensive compression efficiency can be utilized compression ratio to be about 2 first and final stage compressor and compression ratio to be about 5 intergrade compressor and to reach.
Referring now to Fig. 7, the figure illustrates embodiment with Combined Cycle system of air-lock circuit, totally by 106 expressions, in this system, three-stage air compressor: first order air compressor 108, second level air compressor 110 and third level air compressor 112 are configured to two independently groups.Be connected by jack shaft 116 by low-pressure air turbine 114, to drive first order air compressor 108, the output torque from 108 is passed to a load (not shown) on first output shaft 118.High pressure turbine 120 is connected by jack shaft 122, with the jack shaft 124 that drives a second level air compressor 110 and a prolongation to drive third level air compressor 112.Output torque also can be delivered to a load (not shown) on second output shaft 126.
From the pressurized air of first order air compressor 108 after 128 coolings of first interstage cooler, just by feed-in second level air compressor 110.Equally, after 130 coolings of second interstage cooler, just enter third level air compressor 112 from the pressurized air of second level air compressor 110 and stand its final compression.The same with the foregoing description, pressurized air is drawn from the heat that flows through the waste hot gas in it in heat exchanger 76.Heated compressed air carries out expanding the first time, to produce the compressor transmission and first output torque to third level air compressor 112 and second level air compressor 110 in high pressure turbine 120.This air carries out expanding the second time in low-pressure air turbine 114 then, to produce the compressor transmission and second output torque to first order air compressor 108.The cleaning exhaust gas that comes out from low-pressure air turbine 114 is sent to the downstream process (downstream process) that chimney maybe can utilize this waste heat by an outlet pipe 132.
The biaxial system of Fig. 7 is connected an one-axis system on the common shaft than all compressors and air turbine and has more operating flexibility.For example, the relative size of third level air compressor 112 and low-pressure air turbine 114 can be decided to be to produce disalignment speed and the required size of output torque.In fact can save one or two output shafts (118 and 126).
I find: can operate device of the present invention and go to increase or reduce the temperature of gas at flue 30, and hot air changes temperature at outlet pipe 132 with opposite direction.That is to say,, can from the hot gas that reverse flow is crossed, absorb heat more or less by used pressure ratio in the air pressurized process of selecting to flow through heat exchanger 76.If more heat is absorbed by air, then the gas of discharging is inevitable colder.
Now, the figure illustrates a sensitiveer control technique referring to Fig. 8.This control technique is equally applicable to all embodiments of the present invention.A pair of heat-operated valve 134 comprises control valve 136, and valve 136 controls are by the part pressurized air of heat exchanger 76.Bypass valve 138 controls directly flow to the part pressurized air of pipe 142 air supply turbines along bypass tube 140.By air stream is divided into two-way: a part flows through heat exchanger 76 and a part of bypass heat exchanger 76, and when this two-way air met at pipeline 142, this temperature of converging stream was controlled.
Control valve 136 and bypass valve 138 should be operated simultaneously, but its direction difference.In other words, when control valve 136 was opened a certain specified rate, bypass valve 138 should be closed a corresponding amount.For be more convenient for the operation for the purpose of, shown in dotted line 144, control valve 136 and bypass valve 138 mechanically connected into have single adjusting heat-operated valve to 134.
The load of air turbine (Fig. 4 or 7) is by a pair of load control valve 146 controls, valve to 146 by the load control valve 148 that links with the hot air that comes automatic heat-exchanger 76, form valve 150 with bleeder valve 150 and release effectively, thereby make air big or in a small amount be added to air turbine from the hot air of system.The air that is utilized by air turbine is not released or is directly passed to a using process.Load control valve 148 and bleeder valve 150 mechanically are linked to be the position and are differed 180 ° shown in dotted line 152, so that by the single adjusting of " load control valve to " 146 they are linked with opposite direction.
Be present in heat-operated valve to 134 and load control valve to the basic correlation between 146, probably be clearly to a those skilled in the art.In other words, by heat-operated valve to 134 regulate establish certain air temperature after, then can change the hot air that is added to pipeline 142 ratio to 146 position to cool air by adjusting load control valve.By means of the temperature, pressure of the routine that has nothing to do with the present invention and the measurement of flow instrument, be to possess the ability that makes two cover control gear reach good configuration fully to an operator who is skilled in technique who has utilized disclosed content.
Heat-operated valve to 134 and load control valve can manually or by semi-automatic or full-automatic device control 146, and this control gear (for example can be the part of power plant control system.Being used to realize that the equipment of this control is conventional equipment, is not constituent element of the present invention, therefore no longer describes in detail.
Another embodiment of the present invention is shown in Fig. 9, and this embodiment is a Combined Cycle system with air-lock circulation 153; Saved moment output so that to greatest extent the pressurized air of heat is supplied with a using process.By air compressor 154,156 and 158 three grades of compression systeies forming make pressurized air add to control valve assembly 164 by heat exchanger 76 with interstage cooler 160 between air compressor 154 and 156 and the interstage cooler 162 between air compressor 156 and 158.Control valve assembly 164 comprises a turbine negative valve 166 and delivery valve 168, and this two valve is preferably shown in dotted line 170, and the interior connection by a kind of machinery mechanically links it in opposite direction.Turbine negative valve 166 is used for effectively heated compressed air being added to air turbine 172, and turbine 172 only produces is enough to drive the moment of air compressor 154,156 and 158, and does not have to drive other moments of output shaft.Basic output with Combined Cycle system of air-lock circulation 153 is the clean pressurized air that sends the heat of a using process by delivery valve 168 to.
Usually resemble all previous embodiments, except the basic output (pressurized air of the heat among Fig. 9 embodiment, moment among other embodiments) outside, also have from interstage cooler 160 and 162 and can be reclaimed again from the energy in the clean thermal air current of air turbine 172.
For further increasing aforementioned arbitrary embodiment's output, can use auxiliary combustion.Though auxiliary combustion has consumed additional fuel, this facility is another the measure that increases operational flexibility to this system.In addition, auxiliary combustion is to make the air circulation of Combined Cycle system partly reach operating rate, method for simplifying is provided, and the air circulation part can produce useful power output under operating rate, and irrelevant with the gas turbine running state partly of Combined Cycle system.Auxiliary combustion can carry out in the gas side or the air side of system.
Now referring to Figure 10, the figure shows the situation that auxiliary combustion carries out at the gas side of system.The auxiliary combustion stove 174 of a routine is inserted in the exhaust manifolds 24 of gas access side of heat exchanger 76.Fuel channel 176 fuel that any is suitable is transported to auxiliary combustion stove 174, so that burning within it.Can make the compressed-air actuated heat to the air side of heat exchanger 76 is the summation that adds the heat that is increased from the heat that gas turbine transmits by exhaust manifolds 24 auxiliary combustion stove 174 in, deducts common invalid heat transport heat (inefficiencies) in the heat exchanger 76 again.Auxiliary combustion stove 174 can be the arbitrary or multiple available fuel combustion furnace of (comprising gas, liquid or solid) that can burn.The combustion air that is used for reacting with fuel can be used to the excess air from gas turbine waste gas.On the other hand, auxiliary combustion stove 174 can comprise a blower (not shown) that is used to supply combustion air.Auxiliary combustion stove 174 can whole system all run duration or only in the selected cycle of the extra heating of needs to entering the waste heating of heat exchanger 76, it is believed that sizeable auxiliary combustion stove 174 may make the air circulation of group shot partly produce the output power that doubles.
One embodiment of the present of invention shown in Figure 11 are that auxiliary combustion can be carried out under the undesirable heat transmission loss of heat exchanger 76 not having.Conventional auxiliary combustion stove 178 is placed in the stream of heated compressed air of discharging heat exchanger 76.Owing to need not pass through heat exchanger 76, so make this part improved efficiency of system about 0.5 to 1% of embodiment of comparable Figure 10 of this part efficient of this system from the additional heat of auxiliary combustion.This improvement on efficient obtains as cost to have increased the calcinate in the air stream.Therefore for avoiding damaging corresponding air turbine, must handle and will add the step that is generally used for handling hot combustion gas the output of auxiliary combustion stove 178.If utilize the untainted air of the clean heat of the process need of Combined Cycle system output, this embodiment system then of the present invention is inappropriate.
Though the present invention is described under the locking circuit situation of gas turbine being used for, should be realized that: the performance of described air circulation heat power converting system and the applicable scope of advantage exceed the function of obtaining heat energy from GTE in the present disclosure.To carry out aspect the energy recovery any row from process may be valuable but this air circulation system is to being comprised in heat energy in certain cooling medium.For example, countless chemical processes are emitted the hot gas that contains remarkable heat in a large number, and institute's heat content just can be used air circulation system of the present invention and reclaimed.
Again referring to Fig. 9, shown in dotted line 180, make its input of getting back to air compressor again after can allowing the output of air turbine 172 by an interstage cooler 182, thereby constitute a closed-system.May cause under some environmental conditions of device damage owing to sucking surrounding atmosphere, closed-system is perhaps particularly useful.For example, the air ambient that contains abrasive particle or aggressive chemistry composition may corrode rotation and/or the fixing component that is under this air.Equally, the air ambient of high humidity may cause fault by condensed water content size.
Closed circulation has been avoided problems such as dirt, pollution or humid air state by allowing air continuously circulate in system.In addition, can obtain the increase of output power by the pressurization of this closed-system.In other words, with inlet pressure to the external pressure of limit air turbine 172 substitute that the conventional art (not shown) may adopt in this inlet supercharging and the corresponding increased pressure that runs through this closed-system.The increase of the air density of the whole closed-system that causes thus can increase as the achievable workload of medium in its of certain setter capacity.
Most preferred embodiment of the present invention is described with reference to accompanying drawing, certainly, the present invention is not limited to those specific embodiments, and one of skill in the art may make various changes and remodeling to it under situation about not breaking away from as scope of the present invention defined in the claims or spirit.
Claims (23)
1, be used to draw the thermodynamic conversion system of the heat of heated air stream, be characterised in that to comprise:
-be used for the first and second at least two air compressors of compress ambient air;
-a interstage cooler between described the first and second at least two air compressors;
-described interstage cooler comprises cooling device, so that before described first pressurized air enters described second air compressor, will reduce to about room temperature from the first compressed-air actuated temperature of described first air compressor;
-heat exchanger, it comprises heat-transfer apparatus--is used for second pressurized air of the heat transferred that flows from described heated air, to produce the pressurized air of heating from described second air compressor;
-at least one responds the air turbine of described heated compressed air, driving one of described first and second air compressors platform at least,
Described heated compressed air comprises exceeding by described at least one air turbine removes to drive the required excess energy of one of described first and second air compressors platform; With
-transfer unit is used for described excess energy is passed to a using process.
2, according to the thermodynamic conversion system of claim 1, be characterised in that: wherein said thermodynamic conversion system comprises and is used for and will reduces to minimum device by the temperature gradient of described heat exchanger, obtains maximum transmitted efficient thus.
3,, be characterised in that wherein saidly to be used for that temperature gradient is reduced to minimum device and to comprise that control gear-described second pressurized air by described heat exchanger and described heated air current control is to the value that roughly has equal thermal capacity according to the thermodynamic conversion system of claim 2.
4,, be characterised in that wherein said cooling device comprises a blower and the motor-driven source of air blast according to the thermodynamic conversion system of claim 1.
5,, be characterised in that wherein said blower power source comprises an electrodynamic machines according to the thermodynamic conversion system of claim 4.
6,, be characterised in that wherein said blower power source comprises the mechanical linkage from described at least one air turbine according to the thermodynamic conversion system of claim 4.
7,, be characterised in that described cooling device comprises one air stream from described first order compressor according to the thermodynamic conversion system of claim 4.
8, according to the thermodynamic conversion system of claim 1, be characterised in that the wherein said device that is used to transmit excess energy, comprise an output shaft of described at least one air turbine.
9, thermodynamic conversion system according to Claim 8 is characterised in that the wherein said device that is used to transmit described excess energy also comprises the device that is used for the remainder of described heated compressed air is delivered to described using process.
10,, be characterised in that the wherein said device that is used to transmit described excess energy comprises the device that is used for the described heated compressed air of at least a portion is delivered to described using process according to the thermodynamic conversion system of claim 1.
11,, be characterised in that also to comprise according to the thermodynamic conversion system of claim 1:
-a pair of heat-operated valve is right;
-described heat-operated valve is to comprising a control valve and a bypass valve;
-described control valve comprises control gear, and this device is controlled described second air supply by described heat exchanger for producing a part of heated compressed air;
-described bypass valve comprises such control gear, promptly controls described second air supply that the described heat exchanger of bypass also directly leads to described at least one air turbine; With
-be used for automatically disposing the device of described control valve and described bypass valve, so that the right single control of described temperature-control valve can oppositely be controlled described control valve and described bypass valve effectively simultaneously.
12,, be characterised in that the wherein said device that is used for configuration automatically comprises the interconnection mechanism of the machinery between described control valve and described bypass valve according to the thermodynamic conversion system of claim 11.
13,, be characterised in that also to comprise according to the thermodynamic conversion system of claim 11:
-a pair of load control valve is right;
-described load-control valve is to comprising a load control valve and a bleeder valve;
-described load control valve comprises the device of the amount that is used to control the described heated compressed air part of leading to described air turbine;
-described bleeder valve comprises the device that is used for the described heated compressed air part of controlled discharge surplus; With
-the second automatic inking device is used for disposing described load control valve and described bleeder valve automatically, so that the right single control of load control valve just can side by side be controlled along opposite direction load control valve and bleeder valve effectively.
14,, be characterised in that also to comprise according to the thermodynamic conversion system of claim 1:
-one right to load control valve;
-described load control valve is to comprising a load control valve and a bleeder valve;
-described load control valve comprises the device that is used to control the described heated compressed air amount of leading to described at least one air turbine;
-described bleeder valve comprises the device that is used for the described heated compressed air surplus of controlled discharge; With
-automatic inking device is used for disposing described load control valve and described bleeder valve automatically, thereby the right single control of described load control valve just can side by side be controlled described load control valve and described bleeder valve effectively in opposite direction.
15,, be characterised in that also to comprise the described heated compressed air of an auxiliary combustion stove-effectively additional heat is added to according to the thermodynamic conversion system of claim 1.
16,, be characterised in that wherein said auxiliary combustion stove is configured to: heat is added in the described heated air of described heat exchanger upstream according to the thermodynamic conversion system of claim 15.
17,, be characterised in that wherein said auxiliary combustion stove is configured to: heat is added in the described heated compressed air in described heat exchanger downstream according to the thermodynamic conversion system of claim 15.
18,, be characterised in that also to comprise according to the thermodynamic conversion system of claim 1: thus the connection set that is used for the air that described at least one air turbine is discharged is linked the inlet of described at least the first and second air compressors constitutes a closed-system.
19,, be characterised in that wherein said connection set comprises an interstage cooler-be used for before described air is added to described inlet, the air that described at least one air turbine of cooling is discharged according to the thermodynamic conversion system of claim 18.
20, one has air-lock circuit Combined Cycle system, is characterised in that to comprise:
-one gas turbine;
-described gas turbine comprises the device that is used to produce one hot air flow;
-one heat exchanger;
-first, second and the 3rd air compressor;
-be used to connect described first, second and the 3rd air compressor is so that compressed-air actuated connection set;
-one first interstage cooler, this cooler is in the described connection set that places between described first and second air compressors;
-one second interstage cooler, this cooler is in the described connection set that places between the described second and the 3rd air compressor;
-with the relevant cooling device of described first and second interstage coolers, be used for will by the there described air temperature reduce to about room temperature;
-described heat exchanger comprises heat-transfer apparatus, is used for the heat transferred of the described heated air pressurized air from described the 3rd air compressor, to produce heated compressed air;
-at least one air turbine responds described heated compressed air, to drive described first, second and the 3rd air compressor;
-described heated compressed air comprises exceeding by described at least one air turbine removes to drive described first, second and the required excess energy of the 3rd air compressor; With
-be used for described excess energy is passed to the device of a using process.
21, have an air-lock circuit Combined Cycle system according to claim 20, be characterised in that wherein said at least one air turbine comprises first and second air turbines, described first air turbine comprises that first output shaft and described second air turbine have second output shaft, and described first and second output shafts can change independently of one another.
22, according to the Combined Cycle system of claim 20, be characterised in that also to comprise:
-be used for the air of discharging described at least one air turbine is connected to the connection set of described first air compressor inlet, thus constitute a closed-system.
23, according to the Combined Cycle system of claim 22, be characterised in that wherein said connection set comprises an interstage cooler-be used for before described air is added to described inlet, cool off the described air that described at least one air turbine is discharged.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN86104890A CN1008757B (en) | 1986-07-31 | 1986-07-31 | The thermodynamic conversion system of air circulation |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN86104890A CN1008757B (en) | 1986-07-31 | 1986-07-31 | The thermodynamic conversion system of air circulation |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN86104890A true CN86104890A (en) | 1988-02-10 |
| CN1008757B CN1008757B (en) | 1990-07-11 |
Family
ID=4802638
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN86104890A Expired CN1008757B (en) | 1986-07-31 | 1986-07-31 | The thermodynamic conversion system of air circulation |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1008757B (en) |
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| CN1008757B (en) | 1990-07-11 |
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