CN1120115A - steam-air steam engine - Google Patents
steam-air steam engine Download PDFInfo
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- CN1120115A CN1120115A CN94106614.2A CN94106614A CN1120115A CN 1120115 A CN1120115 A CN 1120115A CN 94106614 A CN94106614 A CN 94106614A CN 1120115 A CN1120115 A CN 1120115A
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Abstract
A steam-air steam engine operates at high pressure and with a working fluid consisting of compressed unburned air components, fuel combustion products and steam. In its cycle, the working fluid is supplied at ambient pressure and temperature, the combustion air is adiabatically supplied by the compressor, the fuel is injected at the desired pressure, at least 40% of all the compressed air is combusted, and the inert liquid is injected at high pressure to produce steam, thereby providing the desired inert high specific heat dilution steam for internal cooling of the internal combustion turbine. The design of such an engine suppresses the formation of pollution, increases the efficiency and power of the engine and reduces specific fuel consumption.
Description
The present invention relates to a kind of steam of under high pressure working and utilizing the working fluid that constitutes by pressurized air, oil inflame product and steam mixture---air vapor machine.The invention further relates to a kind of method that in fuel combustion system, produces electric energy with high efficiency and low specific fuel consumption.The invention still further relates to and a kind ofly also simultaneously can produce drinkable water in not obvious attenuating efficient or the situation that increases oil consumption when producing electric power.
Internal-combustion engine (ICES) is divided into two kinds of constant volume or level pressure usually.Otto engine is worked under near the pressurized air state of the constant volume the upper dead center by the volatile fuel oil (being gasoline) of detonation, and then by improved circulating combustion fuel oil, promptly combustion characteristic is roughly constant pressure process to Diesel cycle engine.
The example such as the steamer of external-combustion engine (ECES), the combustion gas turbine of turbine and some form.The pressure fluid of heat is supplied with combustion gas turbine and utilized the energy that is present in these pressurized gass to make various motor apparatus work from the external fluid supply source, and this process has been known knowledge.
People also know in the firing chamber burning fuel oil and products of combustion are discharged in the clutch release slave cylinder, sometimes also according to the temperature that raises and needs are accompanied by the injection of water or steam.These motors are also divided into external-combustion engine.
People have also proposed some other device, wherein the water or the steam cooling that are added by inside of firing chamber rather than adopt external refrigeration.People have also proposed the device of other form, and it sprays into fuel oil in the combustion cylinders when temperature descends, and have the device that stops oil spout when pressure reaches ideal value.
Every kind in these available engines has all run into the difficulty that hinders them and be used as the power source that drives prime mover work usually.In these difficulties, run into unexpected situation and/or to keep certain operating temperature or pressure and when needing motor effectively to work motor this is seemed powerless.
In addition, be not very effective to the control of these motors, and it is abundant inadequately generally that gas generator itself is maintained at the following ability of stable condition.In all practical engine structures, because of many other latent defects in the loss that the cooling requirement that limits the clutch release slave cylinder casing wall caused efficient and the previous internal-combustion engine.
The present invention has overcome the restriction of above-mentioned prior art.At first, thus control the temperature of the working fluid that is produced and eliminated needs by water being sprayed into combustion process the cooling of air or liquid external.When water sprayed into and be converted into water vapor, this water vapor itself became the part of working fluid, therefore, did not need mechanical compress just can increase the volume of working fluid.Working fluid has just increased when too high burning gas temperature is converted to vapor pressure.
In the present invention, adopted the independent control of combustion flame temperature and fuel-air ratio for the requirement of satisfying working engine.The control flame temperature has also prevented the analyte of the formation of NOx and CO2 hereinafter described.
The present invention also adopts high compression ratio as increasing the measure that efficient and power reduce specific fuel consumption (sfc) simultaneously.When water spray into and firing chamber in the present invention in when being converted into water vapor, this produces chamber pressure.Should be noted that this chamber pressure be by water vapor produce and irrelevant with the compression ratio of motor.Therefore, need not consume extra compression work just can be because of the higher compression ratio of acquisition in motor that sprays into of new water vapor or water.Owing to adopt the mode of a large amount of water-sprayings in the present invention, therefore need not to compress in the prior art system is the diluent air of cooling purpose special use.The cancellation of this requirement causes this system to save lot of energy.
Because the compression ratio in the device of employing water spray of the present invention has increased, thereby manifests the advantage of its several aspects.At first, after water or water vapor begin to be compressed, do not need other merit to go it is continued compression.In other words, behind pressurized water steam to 2 barometric pressure, do not need other merit that it is compressed to higher pressure.This is different from air, and for example air must consume other merit and it could be compressed to higher pressure so that obtain other working fluid quality.In addition, in the present invention, when water was sprayed into and is converted into water vapor, it does not consume other merit will produce chamber pressure.This steam also has constant entropy and enthalpy.
In the present invention, remaining ignition heat is converted into water vapor pressure and does not need mechanical compress just to be used as the associated mass of working fluid.As relatively, in the typical B rayton circulation turbine, the air that 66%～75% mechanical compress is crossed is the air of the temperature of working fluid to be reduced to the requirement of turbine-inlet temperature (TIT) and products of combustion is diluted with work in order to satisfy.
Because water vapor has doubled or increased the working fluid that burning produces and produced 15% or more net power, so water can be considered to a kind of burning in the new thermodynamic system of the present invention, because it provides pressure to native system, and power and efficient.
Circulation of the present invention is that air or water or the situation that has both concurrently can be divided into open type or enclosed according to what spray.Demineralized water or to purify waste water can be by-product from the generating of power station or water boat, at this moment, this circulation is an open type to air, to the demineralized water enclosed of retrieving to say so.Power generation with sea water factory or irrigation water also are feasible environment than system only.
This circulation also can be used for promptly being used for automobile in the closed cycle state in the environment of an activation, truck, and bus is in airliner, common military aircraft and the analog.
One of purpose of the present invention provides a kind of new thermodynamic cycle, this circulation can be open type or enclosed, and pressurized air and according to chemical equivalent burning fuel oil and air, thus the controlled power of high-efficiency low-pollution is provided.
Thereby another purpose of the present invention is needn't mechanically compress diluent air and control combustion temperature fully in motor by the vapour specific latent heat that utilizes water.
Still a further object of the present invention be reduce with motor in the relevant air compressor load of power turbine used, thereby can obtain the achievement that slows down idling and quickening acceleration.
Purpose in addition of the present invention is to control turbine-inlet temperature (TIT) as required respectively.
A further object of the present invention is the composition that changes working fluid as required.
Of the present invention also have a purpose to provide enough stop times with millisecond meter, thus allow by the chemical equivalent proportioning burn, in conjunction with and cooling and balance time fully arranged.
A further object of the present invention is to make comburant burning and cooling, so that prevent to form the smog that causes such as Nox, HC-, CO-particle, CO2 analyte or the like composition.
A further object of the present invention provides a kind of combustion system that 1 pound of chemical heat 100% ground can be converted into 1 pound of heat energy.
A purpose in addition of the present invention is to make whole power system still use high thermal efficiency work under the cooling as much as possible.
A further object of the present invention is in order to cool off, and condensation separates and makes steam regeneration become condensed water and produce vacuum to a certain degree and a kind of condensation process is provided.
Another object of the present invention provides a kind ofly to be made the power generation system of cooling liquid and produces the product of the potable water of desalination as generating with seawater.
A further object of the present invention provides a kind of new circulation, and this circulation will combine in improved Braytor circulation during upper half part of engine operation and the water vapor air vapor circulation during engine operation lower half portion.
Another object of the present invention provides the turbo power generation system of generation electric energy that a kind of and existing obtainable systematic comparison has higher efficient and the specific fuel consumption of reduction is arranged.
A further object of the present invention provides a kind of to produce the moving generation system of electric energy widely greater than 40% total efficiency.
One internal-combustion engine has been described according to one embodiment of present invention.This motor comprises that one is compressed to surrounding atmosphere and has more than or equal to 6 atmospheric pressure and the compressed-air actuated compressor of the temperature of rising is arranged.A firing chamber that is connected on this compressor constitutes the form that guiding pressurized air flows forward from compressor.Independent fuel oil and fluid jet control are used to fuel oil and water are sprayed in the firing chamber respectively as required.Every of the temperature of the emitted dose of pressurized air, fuel oil and fluid and institute's water-spraying is all controlled independently.Therefore, average combustion temperature and combustion/sky are than also controlling independently.The fuel oil and the compressed-air actuated controlled part of spraying are burnt, and the heat that is generated changes into steam with the fluid that sprays.Thereby the fluid that sprays changes into the discharge temperature that steam has reduced to be in the gas of combustion temperature by means of the latent heat of vaporization.Used fluid weight is more much bigger than the weight of fuel oil.Therefore, the mass flow of the working fluid that burning generates under most of operating modes is multiplicable or bigger.
Working fluid is by pressurized air, and the mixture of oil inflame product and water vapor constitutes, and it is to be created in the firing chamber during burning with predetermined combustion temperature.Then, this working fluid can be supplied with one or more working engines to produce useful work.
In embodiment more specifically of the present invention, make engine start with an electric spark igniter.This motor also can be under open type or the enclosed mode works.Under the enclosed situation, the working fluid that part is discharged can utilize again.Chamber temperature is according to from temperature transducer and be arranged in the information decision of the thermostat of firing chamber.
When application is of the present invention,, in working fluid, can obtain stoichiometric combination and balance owing to reduced combustion temperature by combustion control device.Chemical energy all in the fuel oil that sprays into all are converted into heat energy at combustion phase, thereby and water flash to water vapor and produce vortex turbulence and helped mixing of fuel oil and air, so realized bigger stoichiometric burning.The water that sprays into absorbs whole after-heats, thereby the temperature of working fluid is decreased to below the maximum operation temperature of working engine.When the water that sprays into became water vapor, it showed as the pressure of firing chamber and does not need other compression work and extra entropy or the enthalpy of tool not.The careful control of combustion temperature has prevented the composition that causes a fog and the generation of gas.
In another embodiment of the present invention, then make cooling liquid and produce electric power, and can produce the potable water of desalination as the by-product that produces electric power with seawater.
In the third embodiment of the present invention, the new circulation with a motor has been described, thereby when surpassing the predetermined rotating speed (rpm) of one when this engine operation, the part of water-spraying and pressurized air burning increases with engine speed (rpm) and keeps constant.In the time of between first and second desired speeds, water/oil increases, the air percentage of burning increases, and the air that has burnt has produced variation.When motor was worked below second desired speed, the water of injection was directly proportional with oil, and it also is a constant when the pressurized air percentage of burning keeps constant.
This circuit utilization has caused the increase of power, the slow-speed of revolution (rpm), low idling, the fast acceleration; And when the slow-speed of revolution, fall up to 95% pressurized air is burned.
Of the present inventionly more completely understand and further purpose and advantage are more clear with reference to becoming of appended accompanying drawing and following detailed description.Scope of the present invention is to be showed specially by appended thereafter claim.
Fig. 1 is the skeleton diagram of water vapor-air vapor turbine engine of the present invention;
Fig. 2 describes the pressure of the thermal procession of using among the present invention and the graph of a relation of volume;
Fig. 3 describes the thermal procession temperature used among the present invention and the graph of a relation between the entropy;
Fig. 4 is of the present invention comprising the skeleton diagram of seawater desalination with the water vapor-air vapor turbine engine of the device of acquisition drinkable water;
Fig. 5 is the schematic representation of an example example of water vapor shown in Fig. 4 skeleton diagram-air vapor turbine engine;
Fig. 6 is second embodiment's the schematic representation that has the desalination ability and be combined with the water vapor-air vapor turbine engine of the present invention's feature;
Fig. 7 is the curve of an expression compression ratio to the influence of the thermal efficiency of water vapor-air vapor turbine engine of Fig. 1;
Fig. 8 is the curve of an expression compression ratio to the impact effect of the specific fuel consumption of water vapor shown in Figure 1-air turbine machine.
Fig. 9 is the curve of an expression compression ratio to the influence of the turbine power of water vapor-air vapor turbine engine of Fig. 1;
Figure 10 is the curve of an expression compression ratio to the influence of the net power of water vapor shown in Figure 1-air vapor turbine engine.
A. the basic structure of native system
Referring to Fig. 1, it schematically shows the embodiment of combustion gas turbine machine of the present invention.Surrounding atmosphere 6 is compressed to desirable compression ratio by compressor 10, thereby forms pressurized air 11.In most preferred embodiment, compressor 10 is known three grades of formula compressors, and surrounding atmosphere is compressed to the pressure that is higher than 4 barometric pressure with the temperature of about 1400 ° of R, preferably 22 barometric pressure.
This pressurized air 11 is by air stream controller 27 supplied burner 25.Burner all is known in the present invention and prior art.Pressurized air 11 can be supplied with by the circumference mode of classification by being similar to air stream controller 27 controls that U. S. Patent NO.3651641 (Ginter) illustrates.This U. S. Patent NO.3651641 is in this reference as this paper.Pressurized air 11 is supplied with by air stream controller 27 control classification, thereby keeps low burning (flame temperature) temperature in the firing chamber 25.
Temperature in the burner 25 is by combustion controller 100 controls of other parts relevant work of describing in detail above with the present invention.Thereby the conventional supply digital logic programmed microprocessor of combustion controller 100, microcomputer or any other known device that is used for following the tracks of and realizes control in response to feedback signal from the tracker of other associated components that is positioned at firing chamber 25 or this system.
For example, the pressure in the burner 25 can be kept by the engine speed variation by air compressor 10.The temperature signal that temperature transducer in the burner 25 and thermostat (not shown) provide combustion controller 100, indication water spray controller 40 sprays into water more or less as required then.Similarly, by means of changing oil, water and AIR MIXTURES in the burner 25 by the quality of combustion controller 100 Control work fluids.
Also have some known physical constraints, it has stipulated out the CLV ceiling limit value of acceptable combustion temperature.What at first consider in these are considered is can be to the highest turbine-inlet temperature (TIT) of any system adaptation.In order to obtain the highest desirable turbine-inlet temperature, water spray controller 40 is according to allowing working fluid that the needs that combustion temperature remains within the acceptable limit are come water-spraying.This water that sprays into absorbs a considerable amount of combustion flame heats because of its vapour specific latent heat when its pressure with burner 25 is converted into steam.
For ease of lighting the fuel oil that sprays in the burner 25, be necessary greater than 12: 1 compression ratios, so that realize spontaneous combustion.Yet sparker (not shown) in the next available standards of low compression ratio.
As mentioned above, combustion controller 100 is controlled the air supply from the burning of air stream controller 27, fuel injection control apparatus 30 and water spray controller 40 independently, thereby makes the fuel oil and the burning of part pressurized air of injection.At least 95% pressurized air is burned to be fallen.If the O2 burning less than 100% will stay enough O2 so and finish the chemical equivalent combination and be used for acceleration.When the air when 100% consumes, form CO2, so there is not O2 to can be used to form NOx in combustion process.Ignition heat also can be converted into water vapor with the water that sprays into, and has therefore caused working fluid 21 to be made of the mixture that the water that generates in unburned air composition, oil inflame product and the combustion gas compressed steams.Can provide compression ratio by means of compressor 10 from 4: 1 to 100: 1.Turbine-inlet temperature can change in 750 °F to 2300 °F, and higher temperature extremes is owing to the consideration of material aspect is stipulated.
Working machine 50 (typically being turbine) is connected to and receives from the firing chamber 25 working fluid, and to finish useful work (as live axle 54 rotation works done), it drives the generator 56 that produces electric energy 58 successively.When the present invention discusses turbine as working machine, skilled professional workforce will notice that the working fluid that is produced by the present invention also can drive the working machine of reciprocating type working machine, wankel working machine, cam or other form.
This working fluid expands when it passes through working machine 50.After the expansion, working fluid 51 is discharged by waste gas controller 60 with the pressure that changes (in any case all at 0.1 more than the barometric pressure), and the pressure of this variations depends on the closed cycle or the open cycle of being with vacuum pump.Waste gas controller 60 also can comprise a heat exchanger 63 and/or in order to will be from steam 61 condenser condensing 62 of working fluid 51 and in order to discharge the recompression machine 64 of working fluid 51.The described steam of condensation is discharged from as potable water 65 in condenser 62.
B. the thermal procession of adopting in this circulation.
1. total explanation.
When as mentioned above burner is used for real engine, can obtain many thermomechanics advantages.These advantages can obtain best understanding with reference to the circulation thermal procession that the present invention uses.Shown in P-V among Fig. 2 and Fig. 3 and T-S schematic representation.The present invention adopts and relevant water vapor, air and the steam of work turbine, and this circulation is referred to as " VAST " circulation.VAST is a trade mark that is had by the claimant.
When being shown in figure in Fig. 2 and 3, drafting used following parameters:
Compression ratio=22/1;
Turbine-inlet temperature-1800;
Fuel oil-air ratio=0.066;
1 pound of air of per second;
Water inlet temperature-212;
Compressor efficiency=85% that is used for compressor 10;
Efficient=85% of working machine (turbine) 50.
Yet as described below, these running parameters are only represented the embodiment in conjunction with the present invention's feature.Compression ratio, turbine-inlet temperature and entering water temp can change according to the needs of used VAST cycle applications occasion wherein.In addition, fuel used type is depended in the variation that combustion/sky compares, thereby guarantees chemical equivalent, and compressor and efficiency of turbine can improve by using more effective design.In addition, Fig. 2 and 3 is calculated by 1 pound of air of per second.Supply with and then cause increasing power with being directly proportional and export when combustion/sky increases air when constant.
The VAST circulation is the combination of pressurized air work done circulation and vapor recycle, because air and water vapor all are used as working fluid, and wherein each all forms the part of total pressure in burner.In the present invention's argumentation, can find out that term " air " is intended to comprise the fuel oil that is burnt with any superfluous pressurized air that may exist by the pressurized air that enters, and comprise all products of combustion, and term " steam " is meant the superheated vapour that water that liquid state sprays into becomes, but the state that it also can have variation is used for work cycle, and ring becomes again at this state bottom steam and is liquid water.The new circulation of burning fuel oil or mixture that process is utilized air and steam be as working fluid, but except the compression process, only relate to air in this process.
Thermal procession in the VAST circulation is discussed below.Shown in Fig. 2 and 3, process 1-2 and 2-3 are illustrated in the compression in the three stage compressor 10.Exit condition in compressor 10 outlet ports is to calculate and get with isentropic Compression relation, and real condition is with 85% compressor efficiency calculating and get.
Such as explained above, pressurized air enters firing chamber 25 by air stream controller 27.Process in the firing chamber is process 3-4 in Fig. 2 and 3.
Firing chamber 25 is in constant voltage and the fuel oil that approximately burns under the condition of constant temperature, because have the independently control of fuel oil, air and water; Therefore temperature can be controlled fully.After the startup, pressurized air is imported burner under constant voltage.Therefore, thus the mixing of the mixed gas that the air of supplying with under the constant voltage and fixing combustion/sky compare combine by the control of spraying water to turbine-inlet temperature again caused forming constant voltage in the firing chamber.Follow hard under high pressure injected fuel and in the firing chamber, burn, and for efficient provides desirable combustion condition, and avoided initially being richer than the atmospheric pollution that the mixture of perfect combustion produces because of fuel oil mixture.Along with the continuation of burning, additionally added air, this air adds along the circumferencial direction of fuel, and its amount is the minimum amount that equals perfect combustion, i.e. the air of chemical equivalent, but finally can surpass the required air quantity of fuel oil composition perfect combustion.Finish the chemical equivalent combination and be used for acceleration in order to stay enough O2, compressed-air actuated minimum flow about 95% is burned.
Water is sprayed by water spray controller 40 with high pressure (can up to 4000Psi or higher).Because the high temperature in the firing chamber 25, the water of injection flashes to water vapor at once and mixes with combustion gas.In addition, the amount that sprays into the water in the firing chamber 25 depends on described turbine-inlet temperature and the water temperature that has just sprayed into.The part heat that discharges in the oil inflame stage is used for the temperature from the pressurized air of three stage compressor 10 is increased to turbine-inlet temperature (TIT).The water that the after-heat of burning is used for spraying into is converted into water vapor.This procedural representation is that 3-4 part is represented by label in these figure in Fig. 2 and 3.
Total subsequently explaining understands that the independent cover operating conditions for the system that uses No. 2 diesel oil is single.Especially it has pointed out that compression ratio is 22/1, and turbine-inlet temperature is 1800 °F, and the turbine outlet pressure is 1 barometric pressure, and entering water temp is 212 °F.In addition, the efficient of compressor and working machine all moderately is set to 85%.This has just caused 455.11 horsepowers net power, the efficient of 0.523 specific fuel consumption (SFC) and 0.251 (data sheet).The example that calculates in the computer that is connected has printed a simulation process and by being listed in the data sheet, and it has demonstrated and has changed in will compression ratio from 10 to 50 and fire/empty ratio the result that water temperature and turbine-inlet temperature remain unchanged.
According to identical mode, also can change other operating conditions.For example can increase water temperature, maximum temperature is not more than desirable TIT temperature.Water temperature had better not increase to and be higher than the 50 °F degree lower than desirable TIT temperature.Yet,, be to be used for heating the water supplied with because working fluid is discharged turbine, so the common maintenance of entering water temp is not higher than low about 50 degree of this turbine discharge temperature because of actual cause.Water temperature is high more, and the volume that combustion temperature is decreased to the required water of TIT temperature is just big more.Therefore caused bigger gas volume to flow through turbine and bigger power output.Similarly the TIT temperature also can raise or reduce.Example 1-10 is 1800 °F by TIT and calculates in the data sheet.This temperature is not for utilizing refractory alloy or being common acceptable maximum temperature with the turbine of the hollow blade of air or steam cooling.Yet with alloy high temperature resistant and/or corrosion, high-temperature composite material, pottery and other material can be carried out hot operation, will allow with the temperature work up to 2300 such as the motor that is used for the turbine injection.Example 11-16 illustrates the data with higher temperature work.
The example 1-5 of table 1 shows increases air compression comparison power, the influence of efficient and specific fuel consumption.The influence that increases entering water temp and reduce head pressure (efficiency of turbine by 85% and compressor efficiency calculating) is shown in the example 6-10.Example 11-16 shows the air compression comparison and has the influence that TIT is 2000 a system.When the efficiency of turbine with hypothesis is 90% when calculating, the turbine outlet pressure is 0.5 barometric pressure, and the temperature that enters of H2O is under about 625 to about 700 °.Should be noted that by axial turbine of existing obtainable air compression and power turbine expansion unit and efficiency of turbine can be taken as 93%.
In example 1-16, fuel oil is No. 2 diesel oil, and combustion/sky is than being 0.66, and this is the stoichiometric ratio of No. 2 diesel oil.With other different fuel oils, then require different combustions/sky ratio to keep the chemical equivalent condition.Example 17 is used methane, and its combustion/sky is than being 0.058.Because the comparable diesel oil of methane more effectively burns, therefore every pound of air has then been used fuel oil still less, so the water that adds also still less.
Table 1
TIT ％ °F °F atm HP 1 10∶1 85 212 1800 1 376.53 .208 .6312 22∶1 85 212 1800 1 455.11 .251 .5223 30∶1 85 212 1800 1 477.97 .267 .4974 40∶1 85 212 1800 1 495.94 .274 .4795 50∶1 85 212 1800 1 507.51 .280 .4686 22∶1 85 410 1800 1 490.89 .271 .4847 22∶1 85 410 1800 .5 543.09 .300 .4378 22∶1 85 410 1800 .25 556.39 .307 .4279 22∶1 85 600 1800 .5 612.59 .338 .38810 22∶1 85 665 1800 .5 656.96 .363 .36211 5∶1 90 700 2000 .5 611.76 .334 .38812 10∶1 90 704 2000 .5 754.69 .412 .31513 15∶1 90 697 2000 .5 813.72 .444 .29214 20∶0 90 677 2000 .5 832.78 .455 .28515 25∶0 90 653 2000 .5 843.07 .460 .28216 30∶0 90 629 2000 .5 848.41 .464 .28017 29∶0 93 664 2175 .5 840.31 .475 .250
Example 17 also is to calculate when efficiency of turbine is 93% and 2175 turbine-inlet temperature, and the two all is the running parameter that can be used as the commercial turbine of using (it does not use described invention).
The influence that changes air compression comparison systematic function is listed in the example 11-16, and it influences figure and is plotted among Fig. 7-10.
Burner of the present invention is different from the device of prior art aspect basic principle, this is because working fluid can be at normal pressure or at normal temperature the time or increase under the situation of both whiles.Normal temperature is to be sprayed by the water by 40 controls of water spray controller according to the response of the temperature tracker (thermostat) in the burner 25 by combustion controller 100 to keep.In burner 25, when compressor 10 providing chemical equivalents or when remaining less pressurized air, the typical combustion temperature of liquid hydrocarbon fuel oil reaches about 3000 °F to 3800 °F.Certain more substantial excess air will reduce final combustion temperature, but can considerable influence not arranged to actual combustion temperature or firing temperature.
From the practical limit of the discharge temperature in the burner 25 is by the strength of materials at the container wall at delivery temperature place successively, the high temperature License Value of burner wall, the material of the structure of power turbine and turbine blade separate cooling or external cooling or interior cold these factors and decide.This delivery temperature is controlled between the suitable limit by the injection that changes the high pressure water that flashes to water vapor rapidly.The ignition heat of the fuel oil that its vaporization and overheated heat equal to burn.(vaporization the when temperature of burning fuel oil then is heated to TIT by evaporation of water and overheated heat reduce the TIT to ideal).Therefore the water yield that sprays into is to be determined by desirable operating temperature (it is littler concerning high superheat temperature, but in fact remains a fixing operating temperature).
Working pressure need as the rotating speed of any given motor remain constant by compressor 10.
The final working fluid mixture of combustion gas and steam flows into then in the working engine 50 and (is typically and is turbine engine as mentioned above), expands at this steam-fuel gas mixture.Discharge condition in working engine 50 outlet ports is calculated with isentropic relation and efficiency of turbine.This process is presented among Fig. 1 and 2 by 4-5.
Pass through waste gas controller 60 then from the waste gas and the steam of working engine 50.Waste gas controller 60 comprises a condenser, the guarantor of vapor partial pressure power and temperature in this temperature reduces to corresponding to waste gas.Therefore, the steam in the turbine exhaust gas be condensed and by water spray controller 40 blowbacks to firing chamber 25.Then, afterflaming gas is back to atmospheric pressure at this pressure liter, so that it can enter in the atmosphere by second compressor.
The present invention has the remarkable advantage that produces the little latent heat of vaporization as can be seen.When water sprayed into the firing chamber and produces water vapor, can produce several useful results: (1) water vapor had the partial pressure of self; (2) total pressure in the burner will resemble by air compressor keep be the pressure of firing chamber; (3) except that the merit with a spot of pump-in pressure water, the water vapor pressure cost does not need mechanical cost; (4) need not mechanical compress at high-caliber water vapor pressure and just can obtain, but except water and be in constant entropy and the steam of constant enthalpy.Water is converted into water vapor and has also cooled off combustion gas, thereby has caused pollution control hereinafter described.
2. pollute control
No matter be in motor or in industrial boiler, although the kind difference, any burning all can produce the reaction product that constitutes smog in air.The present invention reduces the formation of pollution products by several method to be discussed below.
At first, have the boundary layer cooling of the empty mixture of combustion with the internal-combustion engine of chilled casing wall and cylinder cap work, this is enough to cause discharging in exhaust stroke the unburned hydrocarbons of very little percentage.The present invention has avoided the chamber wall cooling at two aspect tangible, is high thereby keep the combustion temperature of fuel oil, and this two aspect all is described in aforesaid U. S. Patent NO3651641 in more detail.At first, by means of air stream controller 27 hot compressed air wall outside burner 25 is flowed, so that burning only takes place in being heated to above the little space of firing temperature.The second, combustion flame is blocked by the air that does not mix with fuel oil.Therefore, what adopt in the motor by this periodic duty is the hot wall burning, preferably is higher than 2000 °F.
Secondly, by means of being worked, burner 25 stoped the shaping of smog product in a temperature range that limits.For example, the product of CO and other parts burning is limited by high-temp combustion (preferably being higher than 2000), and by keeping a quite long holdup time to be limited in burning beginning back these products.Can form more nitrogen and oxynitrides yet temperature is too high.Therefore, can received temperature in order to reduce the smog product should not be too high also should not be too low.Combustion controller 100 among the present invention at high temperature begins the burning of fuel oil and air, temperature is reduced a quite long holdup time then, cools off the temperature that (after air burning) forms to predetermined prevention smog with water spray then.Therefore, burning is at first carried out in rich mixture; Enough then pressurized air adds with permission fuel oil perfect combustion and has minimum residue oxygen, and in the only about half of holdup time in being stranded in firing chamber 25 combustion gas is cooled to be lower than about 3000 °F; Directly add burning by water spray controller 40 water-sprayings then or before burning, add, thereby keep a temperature accepted of guaranteeing whole hydrocarbon perfect combustions.
In typical motor, hydrocarbon fuels usually is burning with air mixing and when denseer slightly, promptly in order to increase efficient to burn less than stoichiometric ratio.Yet this has just produced excessive CO and more complicated imperfect combustion product.Yet the present invention has diluted burning, thereby has further reduced this smog product owing to provide air progressively by air flows controller 27.
As explained above, nitrogen oxides can more promptly form when high temperature, reduces but also can add the dilution of compressing air control products of combustion by other.
The present invention's burn cycle is consistent with high efficiency fuel burning completely, and has eliminated the partial combustion product, has reduced other product such as nitrogen oxides.(this temperature can be in 1000 to 1800 scope after products of combustion or surplus air are cooled to an acceptable engine operating temperature, when in the structure of turbine engine, adopting suitable material even can be up to 2300 °F, perhaps also can hang down to 700 °F to 800 °F), combustion controller 100 is burnt products of combustion at quite long intial detention in the time.
By means of the Design of length of firing chamber 25 is become is that 2 times of zone of combustion in the firing chamber 25 then can produce a kind of equilibrium conditions to 4 times; Yet the suitable firing chamber of any design all can be adopted.
Described burning provide a kind of reduce the formation of smog element and make at the same time the fuel oil energy be converted into fully fluid can method.
Because combustion/sky when flame temperature is independent control, thus VAST to circulate be a kind of combustion with reduced pollutants system.The control of combustion/empty ratio is especially burnt whole compressed-air actuated chances (if desired, then by a large amount of pressurized air dilutions) and has been stoped the unburned hydrocarbons and the carbon monoxide that produce because of partial combustion.The carbon monoxide that uses inert diluent and can control the formation of nitrogen oxide and suppress to form without air because of carbon dioxide decomposition when the high temperature.Utilize the thinner of high specific heat, aforesaid water or steam have reduced the required dilution dosage of temperature control.For the situation of nitrogen oxide, should be noted that VAST circulation has stoped it to form, and do not resemble in some system, occur really allow its formation, and then attempt to eliminate their this challenges.The synthesis result of all of these factors taken together then makes VAST work under the operating conditions of wide range and has negligible level of pollution, usually is to be in below the limit of the nitrogen oxide responded to the mass spectrum technology and carbon hydride.
Because water rather than surplus air cool off, therefore the air quantity of supplying with significantly reduces, so have only about 30% nitrogen to be present in the combustion gas of firing chamber 25 with comparing with the open cycle Brayton motor of air dilution usually of any form or model.Water forms water vapor along with it and periodically expands, and produces control internal-combustion molecular action par excellence.
3. water sprays
40 controls of water spray controller are by the injection of the water 41 of nozzle, and this arrangement of nozzles must be convenient to trickle water smoke is sprayed in the firing chamber.Water can spray into one or more zones in the motor, and it comprises: atomized in air inlet before compressor 10 will enter into pressurized air by the steam atomisation that itself produces; Around an oil nozzle or a plurality of oil nozzle or wherein, atomize; Atomizing is gone in the combustion flame in the firing chamber 25; Or atomizing is gone in the combustion gas under any required pressure; Or before flowing into working engine 50, they enter in the combustion gas.Other zone can easily be expected by skilled professional workforce.As previously mentioned, the amount of water-spraying is to be foundation by the temperature that detects resulting products of combustion by stationary temperature in the firing chamber 25, and the amount of being sprayed water also depends on used VAST circuit system.For example, if water resembles in Motor Vehicle and wants recirculation used, water just should cool off as much as possible to obtain the useful balance between the output of used Total Water and power, promptly so, if entering water temp is low and TIT is high, then available a spot of water is reduced to TIT with combustion temperature.On the other hand, the same as discussed below if the main purpose of system is to produce drinkable water from seawater, producing electric energy simultaneously, entering water temp will rise to high as far as possible, and TIT then reduces.
C. other embodiments of the invention
1. include the power station that water desalination is handled
Doing with seawater under the situation of cooling liquid generating, for being open type as the used water cycle of air, electric power and Figure 4 and 5.Seawater 41 is driven by pump 42, and contrary by condenser 62 and heat exchanger 63 at it, and that the thermal technology who discharges makes fluid 51 and be heated when flowing, and evaporation rapidly in above-mentioned big capacity firing chamber 25.In order to guarantee better to remove salt, and to increase the diameter of firing chamber, reduce the speed of working fluid simultaneously.
The exemplary operation temperature of burner (1500 to 2300) is higher than the fusing point of salt in the seawater but is significantly less than its boiling point (85% of sea salt is NaCl, and other 14% is MgCl2, MgSO4, the mixture of CaCl2 and KCl).Therefore, when seawater was evaporated to water vapor rapidly, salt resembled and is eliminated away the liquid.For example, NaCl is 1473 fusings and 2575 vaporizations, other salt has lower fusing point and higher boiling point.Therefore, the salt of fusing is easy to assemble the diapire place of doing the firing chamber and should can be discharged by the nut device on the burner bottom by liquid state salt, supply with an extrusion press or metal pattern, it can be configured as bar or pellet shapes at this, or utilizing the pressure in the burner to spray into cooling chamber as driving force by nozzle, it can be deposited as size or shape such as laminar, Powdered or the pellet shapes of any hope by means of selecting suitable mist mouth size and shape at this.Because salt solution is to be exposed in the temperature high in the firing chamber, therefore the salt that reclaims is sterilized, and does not have organic substance.
The water atomization of 6 to 12 multiple magnitudes of fuel weight enters in the combustion flame and evaporation in some milliseconds.The impurity that is contained in the salt in the steam is by crystallization, and deposition and/or filtration separate with steam, till steam Cheng Chun.
The collection of salt and removal mechanism 80 can be realized by any of many well known devices because of firing chamber 25, as being realized by the longitudinal spiral feeder of rotation.This feeding screw seals, thereby can and not remove the work gas that deposition salt bypass is missed a large amount of pressurizeds because of its rotation.As mentioned above, another program is that the salt that will melt sprays into the assembly tower or salt 81 is squeezed into wire harness or shaft-like by nozzle, is cut into required size then.Also having another scheme is directly the salt that melts to be entered in the mould to form salt block 81.This salt block is easy to transportation and is used for chemical treatment.
The final working fluid that includes pure water vapor can be used in the steam turbine or multistage turbine of a standard.Thereupon producing merit by swelling water steam-combustion gas mixing, condenser 62 is formed with the drinkable water source 65 of usefulness with water vapor 61 condensations.Use this open cycle, with 10: 1 or 50: 1 or higher compression ratio can be efficient and low specific fuel consumption ground produce electric power.
Fig. 6 shows second embodiment with VAST circuit desalter.In this embodiment, by being trapped, further improved other used heat the efficient of system from firing chamber 25.Firing chamber 25 is enclosed in the bivalve heat exchanger 90.Shown in scheme in, the pressurized air 11 of the heat of coming out from compressor 10 flow through the housing 92 of direct encirclement burner 10 before it enters burner 25.Cold seawater 41 infeeds second housing 94 that surrounds first housing 92.In such a way, air 11 absorbs usually the other heat of loss from burner 25 and some heats that the seawater 41 that entering absorbs from pressurized air 11.Because air 11 is in and boosts a little, therefore, other benefit be the pressure reduction of chamber wall both sides reduce greatly (promptly in the burner as shown in Figure 5 pressure reduction between the component environment condition or burner inner with pressurized air 11 between pressure reduction), so reduced Yin Gaowen and high pressure and cooperated with stress on the burner wall.Flow through condenser 62 and heat exchanger 73 by seawater 41 after the combustor outer casing 94, to obtain required water spray temperature.Carefully water is remained on as far as possible under the pressure up to 4000Psi, so when water was heated, it can not be converted into water vapor, till it sprays in the firing chamber 25.This firing chamber then is under the higher temperature, and it has than crossing the lower pressure of hot sea water 41 under big portion situation.
To the purification of polluting waste, also all is with VAST circuit motor very potential a kind of application to obtain available product and to produce power as by-product to the processing of solid, liquid and gaseous waste by the commercial processes process.The waste water that is produced by the drying solid refuse can utilize in the present invention, and the final available water of filtration that forms is as a kind of by-product.The other fuel oil and the inorganic dry refuse that are used for burner 25 burnings all are combustible materials, and they can be used for producing fertilizer.Clearly, can from solid and product liquid, extract other chemical substance with the present invention.Also can be used for sewage treatment.Other application comprises softening of water, produces the recovery of irrigation water of relevant steam source, the fertilizer that contains leaching from soil and mineral substance and recirculation or the like with drilling well work and drilling well with oil.
2. Brayton of Hun Heing and VAST circulation.
One of the present invention embodiment utilizes the Brayton-VAST circulation of mixing.Basically when surpassing the rotating speed of 20000rpm, water-spraying is a constant on amount, approximates fuel weight greatly, and the pressurized air of burning part increases and reduces proportionally with engine speed.When being lower than the 20000rpm rotating speed, the water of injection and the pressurized air of burning part then increase pro rata.For example, the infall between 20000 to 10000rpm, combustion air partly increase about 25% to 95%.When being lower than 10000rpm, the amount of combustion air keeps constant, and injection flow rate increases to 7 to 12 times level of fuel weight.
Therefore, adopting the Brayton circulation from 20000rpm to the most about 45000rpm or the first half work of higher rotating speed, and carrying out inner colded VAST circulation by water in lower half portion employing of this process.The point of intersection betides 20000rpm, normal Brayton circulation beginning this moment wasted power.This intersection process is proceeded in 20000 to 10000rpm scope.At the 10000rpm place, motor is purely for the VAST circulation, fully by water cooling.
In such system, along with rotating speed reduces to 10000rpm from 20000rpm, because motor is converted into the VAST circulation at 20000rpm place from Brayton circulation, it is cut down air dilution and increases and more is used to the water that cools off, and therefore should be multiplied by a coefficient is 3 coefficients that are added on 1.Below 10000rpm, motor is only pressed the VAST periodic duty, at least 95% the pressurized air burning by water cooling.Its some advantages are: increase power, reduce rotating speed, slow down idling, accelerate to quicken and basically described pressurized air is burnt on all rpm level to pollute control completely.
3. airplane engine
Above-mentioned VAST circulation, when particularly working with recycled water, when using it for usually commercial aircraft 30000 to 40000 inches high-altitude flights especially effectively and quite low fuel consume arranged.In such high-altitude, external pressure is 0.1 to 0.25 barometric pressure or lower, and ambient temperature is well below 0 °F.Example 6-8 shows the benefit that reduces the turbine outlet temperature.Yet, when this system works on the sea level, in order to produce subatmospheric ambient temperature, thereby need a vacuum pump in the turbine outlet.This pump consumes the energy that this system produces, and has reduced its available capability, thereby has reduced the efficient of system.Do not consider the energy that consumes by vacuum pump, the efficient of this system and power be increase and oil consumption be reduced.
Cancel the vacuum pump of turbine outlet by in the subatmospheric environment of pressure, working, for example, then can increase the available power output of this system, reduce oil consumption thus greater than about 3000 feet height work.Moreover, if the water in the system is regenerated, then can carry out condensation and cooling to exit flow, and make water separation regeneration with the ambient air temperature.
D. data sheet
What below list is the data sheet that includes the particular of the engine performance that designs by the technology of the present invention.These data sheet produce with computer simulator.
Some abbreviations of using in the table comprise:
F/a ratio=F/A ratio;
Turbine outlet pressure=1 barometric pressure;
γ=the Cp/Cv of compressor;
All temperature all are Rankine (absolute Fahrenheit) temperature=(R);
The cpmix=air adds the mixed C p value of water vapor;
The sfc=specific fuel consumption;
Eff=efficient;
Compression ratio is that 22: 1 example is the example 1 of above-mentioned table 1 in data sheet.It is 212 °F (672 ° of R) that the computer program text that is used for simulated engine work has specifically been made entering water temp, turbine-inlet temperature (TIT) is 1800 °F (2260 ° of R), and the temperature that enters another stage compressor is that 60 (520 ° of R) and every stage compressor and turbine are all with 85% efficient work.
VAST circulation f/a ratio=0.066 with compression ratio work in 10: 1; Compression ratio=10.00; Number of compression stages=3; Entering water temp=672.000 ° R; Turbine outlet pressure=1.00; The air rate of band turbine-inlet temperature=2260.000 (° R) is 11b/s; The γ of compressor 1=1.395088723469110
583.127002349018800 the γ of compressor 2=1.393245781855153
749.390666288273000 the γ of compressor 3=1.382644396697381
960.403717287130800 the CPGAS=3.048731265150463E-001 in the burner
1678.944055144487000 Compressor Inlet Temperature T1=520.00; First order outlet temperature T2d=668.53 (° R); Second level outlet temperature T3D=858.78 (° R); Third level outlet temperature T4d=1097.89 (° R); The mass flowrate of water (lb/s)=0.442; γ in the turbine=1.274667679410808
1818.013006841559000 steam partial pressure (barometric pressure)=5.885070348102550; Air partial pressure (barometric pressure)=8.814929461162587; The turbine outlet is protected and temperature=591.701098285192200 (° R); γ=1.346058430899532 of second level compression
633.271250898951400 the cpmix=3.253198837676842E-001 of second level compression
633.271250898951400 turbine-inlet temperature T5 (R)=2260.00; Turbine outlet temperature T6D (R)=1508.62; The temperature drop DT=751.38 at turbine two ends; Turbine power HP=624.28; Compressor horsepower Hpcomp=199.735; Gross mass flow rate (lb/s)=1.5077; Net power (open type) HP=424.54; Specific fuel consumption (open type)=0.560 efficient (open type)=0.234; T7=674.84; The DT=97.81 of T7D=689.51 second compression; The power HP=48.00 of second compression; Pump power HP=0.017; Net power (enclosed) HP=376.53; Specific fuel consumption (enclosed)=0.631; Efficient 2 (enclosed)=0.208; The composition of waste gas (by volume): the percentage of percentage=25.8N2 of percentage=10.8H2O of CO2=63.4
VAST circulation f/a ratio=0.066 with compression ratio work in 22: 1; Compression ratio=22.00; Compressor progression=3; Entering water temp=672.000; Turbine outlet pressure=1.000; The air rate of band turbine-inlet temperature=2260.000 (° R) is 1lb/s; The γ of compressor 1=1.39480952089263
698.043650004366800 the γ of compressor 2=1.392157497682254
849.596261682560700 the γ of compressor 3=1.369677999652017
1177.990796008891000 the CPGAS=3.101676106439402E-001 of combustion gas in the burner
829.089319349098000 Compressor Inlet Temperature T1=520.00 first order outlet temperature T2d (R)=727.16; Second level outlet temperature T3D (R)=1015.24; Third level outlet temperature T4d (R)=1398.18; The mass flowrate of water (lb/s)=0.505; γ in the turbine=1.278767591503703
1706.015578042335000 the cpmix=3.906654117917358E-001 in the turbine
1706.015578042335000 partial pressure of water vapor (barometric pressure)=6.361387976418345; Air partial pressure (barometric pressure)=8.338611832846791; γ=1.344309728848165 in the compression of the guarantor in turbine outlet port and pressure (R)=593.171968080811400 second level
639.522982616262100 the cpmix=3.316760835964484E-001 in the compression of the second level
639.522982616262100 turbine-inlet temperature T5 (R)=2260.00; Turbine outlet temperature T6D (R)=1318.23; The temperature drop DT=941.77 at turbine two ends; Turbine power HP=817.80 compressor horsepower HP=308.108; Gross mass flow rate (lb/s)=1.5708; Net power HP (open type)=509.69; Specific fuel consumption (open type)=0.466; Efficient (open type)=0.281; T7=685.87; T7D=702.23; The temperature drop DT=109.06 of compressor 2; The power HP=54.57 of compressor 2; Pump power HP=0.018; Net power (enclosed)=455.11; Specific fuel consumption (enclosed)=0.522; Efficient 2 (enclosed)=0.251; Waste gas component (by volume): the percentage of CO2=10.8; The percentage of H2O=25.8; The percentage of N2=63.4.
VAST circulation f/a ratio=0.066 with compression ratio work in 30: 1; Compression ratio=30.000; Compressor progression=3; Entering water temp=672.000; Turbine outlet pressure=1.000; The air rate of band turbine-inlet temperature=2260.000 is 1lb/s; The γ of compressor 1=1.394694290256920
618.355140835066100 the γ of compressor 2=1.389029752150665
891.837744705560000 the γ of compressor 3=1.366209070734794
1273.898681933465000 the CPGAS=3.124320900049776E-001 of combustion gas in the burner
1896.892037142618000 Compressor Inlet Temperature T1=520.00 first order compression outlet temperature T2d (R)=751.42; Second level compression outlet temperature T3D (R)=1081.81; The mass flowrate (lb/s)=0.534 of third level compression outlet temperature T4d (R)=1533.78 water; γ in the turbine=1.280208955027821
1666.7472321510066000; Cpmix=3.916002625082443E-001 in the turbine
1666.747232151006000; Partial pressure of water vapor (barometric pressure)=6.562762207406494; Air partial pressure (barometric pressure)=8.137237601858644; The guarantor in turbine outlet port and temperature (R)=593.793812111702800; γ=1.343572354850198 in the compression of the second level
642.266214292339600; Cpmix=3.344248062769462E-001 in the compression of the second level
642.266214292339600; Turbine-inlet temperature T5 (R)=2260.00; Turbine outlet temperature T6D (R)=1251.47; The temperature drop DT=1008.53 on turbine both sides; Turbine power HP=894.00 compression horsepower HP=358.471; Gross mass flow rate (lb/s)=1.5996; Net power HP (open type)=535.53; Specific fuel consumption (open type)=0.444; Efficient (open type)=0.296; T7=690.74; T7D=707.85; The DT=114.05 of compressor 2; The power HP=57.54 of compressor 2; Pump power HP=0.019; Net power (enclosed)=477.97; Specific fuel consumption (enclosed)=0.497; Efficient 2 (enclosed)=0.264; Waste gas components (by volume): the percentage of CO2=10.8; The percentage of H2O=25.8; The percentage of N2=63.4.
VAST circulation f/a ratio=0.066 with compression ratio work in 40: 1; Compression ratio=40.000; Compressor progression=3; Entering water temp=672.000; Turbine outlet pressure=1.000; The air rate of band turbine-inlet temperature=2260.000 (R) is 1 (lb/s); The γ of compressor 1=1.3945845821122682
628.187703506602900; The γ of compressor 2=1.385229573509871
932.452934382434300; The γ of compressor 3=1.360860939314250
1366.979659174880000 the CPGAS=3.145343519546454E-001 of combustion gas in the burner
1962.926186235099000 Compressor Inlet Temperature T1=520.00; First order compression outlet temperature T2d (R)=774.56; Second level compression outlet temperature T3D (R)=1146.07; Third level compression outlet temperature T4d (R)=1665.85; The mass flowrate of water (lb/s)=0.562; γ=1.281335192214647 in the saturating rate
1632.71703670625000; Cpmix=3.925796903477528E-001 in the turbine
1632.717036740625000; Partial pressure of water vapor (barometric pressure)=6.750831994487843; Air partial pressure (barometric pressure)=7.949167814777294; The turbine outlet is protected and temperature (R)=594.374571993012600; γ=1.342884542206362 of second level compression
644.886243238150400; The cpmix=3.370260274627372E-001 of second level compression
644.8862432381 turbine-inlet temperature T5 (R)=2260.00; Turbine outlet temperature T6D (R)=1193.62; The temperature drop DT=1066.38 at turbine two ends; Turbine power HP=964.40; Compressor horsepower HP=408.011; Gross mass flow rate (lb/s)=1.6279; Net power HP (open type)=556.38; Specific fuel consumption (open type)=0.427; Efficient (open type)=0.307; T7=695.40; T7D=713.23; The DT=118.85 of compressor 2; The HP=60.42 of compressor 2; Pump power HP=0.019; Net power HP (enclosed)=495.94; Specific fuel consumption (enclosed)=0.479; Efficient 2 (enclosed)=0.274; The volume composition of waste gas: the percentage of CO2=10.8; The percentage of H2O=25.8; The percentage of N2=63.4.
VAST circulation f/a ratio=0.066 with 50: 1 works of compression ratio; Compression ratio=50.000; Compressor progression=3; Entering water temp=672.000; Turbine outlet pressure=1.000; It is 1 (lb/s) that the air stream of band turbine-inlet temperature=2260.000 (° R) drips; The γ of compressor 1=1.394497572254039
635.996556562169400; The γ of compressor 2=1.382215305172556
965.068507644903400; The γ of compressor 3=1.356615282102378
1442.860640297455000 the CPGAS=3.162590285087881E-001 of combustion gas in the burner
2017.100000649888000 Compressor Inlet Temperature T1=520.00; First order compressor exit temperature T2d (R)=792.93; High stage compressor outlet temperature T3D (R)=1197.96; Third level compressor exit temperature T4d (R)=1774.20; The mass flowrate of water (lb/s)=0.585; γ in the turbine=1.282120028863920
1607.786622664966000; Cpmix=3.934720408020952E-001 in the turbine
1607.786622664966000; Partial pressure of water vapor (barometric pressure)=6.900293693691603; His pressure (barometric pressure)=7.799706115573533 of air; The turbine outlet port is protected and temperature (R)=594.8361100293700; The γ of high stage compressor=1.342338420102895
647.010415983017100; The cpmix=3.391172383199348E-001 of high stage compressor
647.010415983017100; Turbine-inlet temperature T5 (R)=2260.00; Turbine outlet temperature T6D (R)=1151.24; The temperature drop DT=1108.76 at turbine two ends; Turbine power HP=1019.48; Compressor horsepower HP=449.150; Total mass flowrate (lb/s)=1.6514; Net power HP (open type)=570.33; Specific fuel consumption (open type)=0.417; Efficient (open type)=0.315; T7=699.18; T7D=717.60; The DT=122.76 of compressor 2; The power HP=62.80 of compressor 2; Pump power HP=0.020; Net power HP (enclosed)=507.51; Specific fuel consumption (enclosed)=0.469; Efficient 2 (enclosed)=0.280; The volume composition of waste gas: the percentage of CO2=10.8; The percentage of H2O=25.8; The percentage of N2=63.4.
Be used to simulate and adopt the computer program text of engine operation of the present invention to see appendix 1.E. conclusion
When the present invention's different embodiments illustrate as schematic purpose; the present invention's protection domain is only limited in the degree consistent with following claim, and the spirit of claims and scope are not limited in the explanation of the optimization form that this paper includes.
IMPLICIT REAL*8 (A-H，O--Z)DIMENSION PAIR(17)，TT(17)，VAIR(17)，vn2(17) ，pn2(17)， * pco2(17)，vco2(17)，ph20(17)，vh20(17)open(unit＝11，file＝′1′)open(unit＝22，file＝′2′)open(unit＝33，file＝′3′)open(unit＝44，file＝′4 ′)open(unit＝1，file＝′a1′)DO 5 I＝1，17READ(11，*)TT(I)，PAIR(I)，VAIR(I)read(22，*)tt(i)，pn2(i)，vn2(i)read(33，*)tt(i)，ph20(i)，vh20(i)read(44，*)tt(i)，pco2(i)，vco2(i)TT(I)＝TT(I)＋460.05 CONTINUE<!-- SIPO <DP n="38"> --><dp n="d38"/>FA＝0.066READ(*，*)PRns＝3write(*，*)′turbine exit pressure＝？′read(*，*)pttwater＝212.dO＋460.dOtit＝2260.OdO.write(1,555)fa，pr，ns，twater，pt，tit555 format(5x，′f/a ratio＝′，3x，f7.3，/，Sx，′Pressure Ratio＝′，3x， * f7.3，/，Sx，′Number of Compression Stages＝′，i4，/ * ，Sx，′Inlet Water Temperature＝′，f7.3，/， * Sx，′Turbine Exit Pressure＝′，f7.3，/ * ，Sx，′1 lb/s of air with Turbine Inlet Temp(R)＝ ′，f8.3 * ，/，/，/)T1＝520.DOPRS＝(PR)**(1.DO/FLOAT(NS))COMPRESSOR1GA＝1.4DO 10 I＝1，10WRITE(*，*) ′gamma compr.1＝′，ga，tavT2＝T1*(PRS)**((GA－1.0)/GA)TAV＝(T1＋T2)/2.DOGA＝CpAIR(TAV，pair，vair，tt)/CVAIR(TAV，pair，vair，tt)ga＝1.40610 CONTINUEWRITE(1，*)′gamma compr.1＝′，ga，tavT2D＝T1＋(T2－T1)/0.85HPC1＝1.O*(T2D－T1)*CpAIR(TAV，PAIR，VAIR，TT)*778.3/550.0COMPRESSOR2GA＝1.4<!-- SIPO <DP n="39"> --><dp n="d39"/>DO 20 I＝1，10T3＝T2D*(PRS)**((GA－1.O)/GA)TAV＝(T3＋T2D)/2.DOGA＝CpAIR(TAV，pair，vair，tt)/CVAIR(TAV，pair，vair，tt)cga＝1.40620 CONTINUEwrite(1，*)′gamma compr.2＝′，ga，tavT3D＝T2d＋(T3－T2D)/0.85HPC2＝1.0*(T3D－T2D)*CpAIR(TAV，PAIR，VAIR，TT)*778.3/550.0HPC＝HPC1＋HPC2C COMPRESSOR3GA＝1.4DO 25 I＝1，10T4＝T3D*(PRS)**((GA－1.O)/GA)TAV＝(T4＋T3D)/2.DOGA＝CpAIR(TAV，pair，vair，tt)/CVAIR(TAV，pair，vair，tt)c ga＝1.40625 CONTINUEwrite(1，*)′gamma compr.3＝′，ga，tavT4D＝T3d＋(T4－T3D)/0.85HPC3＝1.0*(T4D－T3D)*CpAIR(TAV，PAIR，VAIR，TT)*778.3/550.0HPC＝HPC1＋HPC2＋hpc3BURNERtav＝(t4d＋2260.dO)/2.0TBURN＝FA/0.066*3600.DO＋T4Da1＝CpCo2(tav，pco2，vco2，tt)a2＝cpn2(tav，pn2，vn2，tt)a3＝cph20(tav，ph20，vh20，tt)write(*，*)tav，cpgas，a1，a2，a3cpgas＝(352.O*a1＋162.O*a3＋1263.36*a2)/1777.36WRITE(1，*)′CPGAS in the burner＝′，cpgas，tavWRITE(*，*)CPGAS<!-- SIPO <DP n="40"> --><dp n="d40"/>AMW＝(TBURN－460.D0－1800.DO)*(1.DO＋FA)*cpgas/(1973.6－180.0)amt＝1.dO＋amw＋faWRITE(1，1OO)T1，T2D，T3D，t4d，amwFORMAT(′Comp.Inlet Temp，T1＝′，5X，F7.2，/， ′1st Stage Outlet Temp，T2d(R)＝′，5X，F7.2，/， ′2nd Stage Outlet Temp，T3D(R)＝′，5X，F7.2，/， ′3rd Stage Outlet Temp， T4d(R)＝′，5X，F7.2，/， ′Mass Flow Rate of Water (lb/s)，＝′，5x，f7.3，/)turbinet5＝2260.DOGA＝1.4DO 30 I＝1，10T6＝T5*(pt/PR)**((GA－1.O)/GA)TAV＝(T5＋T6)/2.DOa1＝cpco2(tav，pco2，vco2，tt)a2＝cpn2(tav，pn2，vn2，tt)a3＝cph20(tav，ph20，vh20，tt)cpgas＝(352.0*a1＋162.0*a3＋1263.36*a2)/1777.36CpMIX＝(AMW*A3＋(1.DO＋FA)*CPGAS)/(AMT)c WRITE(*，*)′CPMIX＝′，CPMIXa1＝cVco2(tav，pco2，vco2，tt)a2＝cVn2(tav，pn2，vn2，tt)a3＝cVh20(tav，ph20，vh20，tt)cVgas＝(352.O*a1＋162.O*a3＋1263.36*a2)/1777.36CVMIX＝(AMW*A3＋(1.DO＋FA)*CVGAS)/(AMT)GA＝CPMIX/CVMIXCONTINUEwrite(1，*)′gamma in turbine＝′，ga，tavwrite(1，*)′cpmix in the turbine＝′，cpmix，tavT6D＝TS＋(T6－T5)*0.85DTT＝TS－T6DHPT＝AMT*DTT*778.3/550.0*Cpmix<!-- SIPO <DP n="41"> --><dp n="d41"/> HPN1＝HPT－HPCSFC1＝FA*3600.DO/HPN1EFF1＝HPN1*550.D0/778.3/(3600.0*0.328＋180.DO*O.SS)go to 1100SECONDARY COMPRESSORPP＝pt*14.7*(aMW/18.0)/(aMW/18.0＋(1.DO＋FA)/29.0)pa＝pt*14.7－ppwrite(1，*)′partial press.of steam (atm)＝′，ppwrite(1，*)′partial press.of air (atm)＝′，paHPpump＝amw*(1.dOS－pp/14.7*1.dOS)/1.dO3*1.04/2.2/746SAT＝TSAT(PP)＋460.0 write(1，* )′SAT.TEMP.AT TURBINE OUTLET(R)＝ ′，SAT GA＝1.4 DO 70 I＝1，10 T7＝sat*(14.7/Pa)**((GA－1)/GA) TAV＝(T7＋sat)/2.DO write(*，*)′gamma in sec.comp＝′，ga，tav write (*，* )′cpmix in SEC.COMP＝′，cpmix，tav write(*，*)′t6，sat＝′，t7，sat a1＝cpco2(tav，pco2，vco2，tt) a2＝cpn2(tav，pn2，vn2，tt) a3＝cph20(tav，ph2c，vh20，tt) cpgas＝(352.O*a1＋162.O*a3＋1263.36*a2)/1777.36 CPMIX＝(AMW*A3＋(1.DO＋FA)*CPGAS)/(AMT) WRITE(*，*)′CPMIX＝′，CPMIX a1＝cVco2(tav，pco2，vco2，tt) a2＝cVn2(tav，ph2，vn2，tt) a3＝cVh20(tav，ph20，vh20，tt) cVgas＝(352.0*a1＋162.0*a3＋1263.36*a2)/1777.36 CVMIX＝(AMW*A3＋(1.DO＋FA)*CVGAS)/(AMT) GA＝CPMIX/CVMIX<!-- SIPO <DP n="42"> --><dp n="d42"/>70 CONTINUE write(1，*)′gamma in sec.comp＝′，ga，tav write(1，*)′cpmix in SEC.COMP＝′，cpmix，tav T7D＝(T7－sat)/0.85＋sat DTT1＝t7d－sat HPS＝(1.dO＋fa)*DTT1*778.3/550.0*CpMIX HPN2＝HPT－HPC－HPS－hppump SFC2＝FA*3600.DO/HPN2 EFF2＝HPN2*550.D0/778.3/(3600.0*0.328＋180.D0*0.55) write(1，*) write(1，*)1 1 0 0WRITE(1,200)T5，T6D，DTT，HPT，HPC，AMT，HPN1，SFC1，eff1200 FORMAT(′Turbine Inlet Temp.，T5(R)＝′，SX，F7.2，/， * ′Turbine Exit Temp.，T6D(R)＝′，5X，F7.2， * /，′Temp. drop across Turbine， DT＝′，5X，F7.2，/， * ′HP TURBINE＝′，5X，F7.2，/，′HPCOMP * ＝′5x，f73/，′TOTAL MASS FLOW RATE(lb/s)＝′，5X，F6.4，/， * ′NET HP (open cycle)＝′，5X，F7.2，/ * ，′sfc (open cycle) ＝ ′，5X，F7.3，/， * ′eff(open cycle＝′，5x，f7.3，/，/) WRITE(1,400)T7，T7D，DTT1，HPS，hppump，HPN2，SFC2，eff2400 FORMAT(′T7＝′，5X，F7.2，/，′T7D＝′，5X，F7.2， * /，′DT COMP.2＝′，5X，F7.2，/，′HP COMP.2＝′，5X，F7.2，/， * ′HP water pump＝′，f7.3，/ * ，′NET HP(closed cycle)＝ ′，5X，F7.2，/ * ，′sfc(closed cycle)＝ ′，5X，F7.3，/， * ′eff2(closed cycle)＝′，5x，f7.3，/，/，/)write(1，*)′composition of exhaust by volume′write(1，*)′～<!-- SIPO <DP n="43"> --><dp n="d43"/>Write(1,*)′％ of C02＝10.8′Write(1，*)′％ of H20＝25.8′Write(1，*)′％ of N2＝63.4′ STOP END alr FUNCTION CPAIR(TAV，pair，vair，tt) IMPLICIT REAL*8(A－H，O－Z) DIMENSION PAIR(17)，TT(17)，VAIR(17) COMMON PAIR，TT，VAIR，vn2，cn2，vh20，ph20，vco2，pco2 DO 10 I＝1，16 IF(TAV.LE.TT(I＋1).AND.TAV.GE.TT(I))THENCPAIR＝PAIR(I)＋(TAV－TT(I))*(PAIR(I＋1)－PAIR(I))/(TT(I＋1)－TT(I)) GO TO 999ENDIF10 CONTINUE999 S＝CPAIRRETURNENDFUNCTION CVAIR(TAV，pair，vair，tt)IMPLICIT REAL*8(A－H，O－Z)DIMENSION PAIR(17)，TT(17)，VAIR(17)c cOMMON PAIR，TT，VAIR，vn2，cn2，vh20，ph20，vco2，pco2DO 10 I＝1，16IF(TAV.LE.TT(I＋1).AND.TAV.GE.TT(I))THENCVAIR＝VAIR(I)＋(TAV－TT(I))*(VAIR(I＋1)－VAIR(I))/(TT(I＋1)－TT(I))GO TO 999ENDIF10 CONTINUE999 S＝CPAIR<!-- SIPO <DP n="44"> --><dp n="d44"/> RETURN END FUNCTION CPn2 (TAV，pn2，vn2，tt) IMPLICIT REAL*8 (A－H，O－Z) DIMENSION Pn2(17)，TT(17)，Vn2(17) c COMMON PAIR，TT，VAIR，vn2，cn2，vh20，ph20，vco2，pco2 DO 10 I＝1，16 IF(TAV.LE.TT(I＋1).AND.TAV.GE.TT(I))THEN CPn2＝Pn2(I)＋(TAV－TT(I))*(Pn2(I＋1)－Pn2(I))/(TT(I＋1)－TT(I)) GO TO 999 ENDIF 10 CONTINUE 999 S＝CPn2 RETURN END FUNCTION CVn2 (TAV，pn2，vn2，tt) IMPLICIT REAL*8(A－H，O－Z) DIMENSION Pn2(17)，TT(17)，Vn2(17) c COMMON PAIR，TT，VAIR，vn2，cn2，vh20，ph20，vco2，pco2 DO 10 I＝1，16 IF(TAV.LE.TT(I＋1).AND.TAV.GE.TT(I))THEN CVn2＝Vn2(I)＋(TAV－TT(I))*(Vn2(I＋1)－Vn2(I))/(TT(I＋1)－TT(I)) GO TO 999 ENDIF 10 CONTINUE 999 S＝CVn2 return END h20 FUNCTION CPh20(TAV，ph20，vh20，tt) IMPLICIT REAL*8(A－H，O－Z) DIMENSION Ph20(17)，TT(17)，Vh20(17)<!-- SIPO <DP n="45"> --><dp n="d45"/>c COMMON PAIR，TT，VAIR，vn2，cn2，vh20，ph20，vco2，pco2DO 10 I＝1，16IF(TAV.LE.TT(I＋1).AND.TAV.GE.TT(I))THENCPh20＝Ph20(I)＋(TAV－TT(I))*(Ph20(I＋1)－Ph20(I))/(TT(I＋1)－TT(I))GO TO 999ENDIF10 CONTINUE999 S＝CPh20RETURNENDFUNCTION CVh20(TAV，ph20，vh20，tt)IMPLICIT RFAL*8(A－H，O－Z)DIMENSION Ph20(17)，TT(17)，Vh20(17)c COMMON PAIR，TT，VAIR，vn2，Ch2，vh20，ph20 vco2，pco2DO 10 I＝1，16IF(TAV.LE.TT(I＋1).AND.TAV.GE.TT(I))THENCVh20＝Vh20(I)＋(TAV－TT(I))*(Vh20(I＋1)－Vh20(I))/(TT(I＋1)－TT(I))GO TO 999ENDIF10 CONTINUE999 S＝CVh20RETURNEND co2FUNCTION CPco2(TAV，pco2，vco2，tt)IMPLICIT REAL*8(A－H，O－Z)DIMENSION Pco2(17)，TT(17)，Vco2(17)c COMMON PAIR，TT，VAIR，vn2，cn2，vh20，ph20，vco2，pco2DO 10 I＝1，16IF(TAV.LE.TT(I＋1).AND.TAV.GE.TT(I))THEN<!-- SIPO <DP n="46"> --><dp n="d46"/>CPco2＝Pco2(I)＋(TAV－TT(I))*(Pco2(I＋1)－Pco2(I))/(TT(I＋1)－TT(I))GO TO 999ENDIF10 CONTINUE999 S＝CPco2RETURNENDFUNCTION CVco2(TAV，pco2，vco2，tt) IMPLICIT REAL*8(A－H，O－Z)DIMENSION Pco2(17)，TT(17)，Vco2(17)c COMMON PAIR，TT，VAIR，vn2，cn2，vh20，ph20，vco2，pco2DO 10 I＝1，16IF(TAV.LE.TT(I＋1).AND.TAV.GE.TT(I))THENCVco2＝Vco2(I)＋(TAV－TT(I))*(Vco2(I＋1)－Vco2(I))/(TT(I＋1)－TGO TO 999ENDIF10 CONTINUE999 S＝CVco2RETURNENDC STEAM TABLES FUNCTION TSAT (PP) IMPLICIT REAL*8(A－H，O－Z) DIMENSION X(22)，Y(22) DO 10 I＝1，22 X(I)＝FLOAT(I)*I10 CONTINUE Y(1)＝101.64 Y(2)＝125.88 Y(3)＝141.32 Y(4)＝152.81<!-- SIPO <DP n="47"> --><dp n="d47"/> Y(5)＝162.09 Y(6)＝170.02 Y(7)＝176.8 Y(8)＝182.77 Y(9)＝188.2 Y(10)＝193.17 Y(11)＝197.73 Y(12)＝201.92 Y(13)＝205.74 Y(14)＝209.46 Y(15)＝212.94 Y(16)＝216.09 Y(17)＝219.23 Y(18)＝222.37 Y(19)＝225.11 Y(20)＝227.78 Y(21)＝230.45 Y(22)＝233.05DO 20 I＝1，21IF(PP.LE.x(I＋1).AND.PP.GE.x(I))THENTSAT＝y(I)＋(PP－x(I))*(y(I＋1)－y(I))/(x(I＋1)－x(I))GO TO 999ENDIF20 CONTINUE999 S＝TSATRETURNEND
Claims (68)
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/US1993/010280 WO1994010427A1 (en) | 1992-10-27 | 1993-10-27 | Vapor-air steam engine |
| USPCT/US93/10280 | 1993-10-27 |
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| Publication Number | Publication Date |
|---|---|
| CN1120115A true CN1120115A (en) | 1996-04-10 |
| CN1055982C CN1055982C (en) | 2000-08-30 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN94106614A Expired - Fee Related CN1055982C (en) | 1993-10-27 | 1994-04-25 | Water vapor - air steam engine |
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| CN (1) | CN1055982C (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104234864A (en) * | 2013-09-12 | 2014-12-24 | 摩尔动力(北京)技术股份有限公司 | Gas closing engine |
| CN104373246A (en) * | 2013-09-12 | 2015-02-25 | 摩尔动力(北京)技术股份有限公司 | Gas-driving-closed piston type engine |
| CN108050332A (en) * | 2017-12-12 | 2018-05-18 | 中国舰船研究设计中心 | A kind of steam pipework thermal compensation device and its design method with heat shock resistance effect |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3885390A (en) * | 1974-02-12 | 1975-05-27 | Glen R Evans | Internal combustion and steam pressure generator with powered expansion engine |
| US4387576A (en) * | 1978-04-25 | 1983-06-14 | Bissell Lawrence E | Two-phase thermal energy conversion system |
| US4248039A (en) * | 1978-12-06 | 1981-02-03 | International Power Technology, Inc. | Regenerative parallel compound dual fluid heat engine |
| SE434883B (en) * | 1980-10-15 | 1984-08-20 | Stal Laval Turbin Ab | SET TO OPERATE A COMBINED GAS ANTURBIN INSTALLATION AND COMBINED GAS ANTURBIN INSTALLATION FOR USE OF THE SET |
| US4569195A (en) * | 1984-04-27 | 1986-02-11 | General Electric Company | Fluid injection gas turbine engine and method for operating |
| US4928478A (en) * | 1985-07-22 | 1990-05-29 | General Electric Company | Water and steam injection in cogeneration system |
| KR0140975B1 (en) * | 1989-11-22 | 1998-07-01 | 더블유. 군너만 루돌프 | Aqueous fuel for internal combustion engines and combustion method thereof |
-
1994
- 1994-04-25 CN CN94106614A patent/CN1055982C/en not_active Expired - Fee Related
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104234864A (en) * | 2013-09-12 | 2014-12-24 | 摩尔动力(北京)技术股份有限公司 | Gas closing engine |
| CN104373246A (en) * | 2013-09-12 | 2015-02-25 | 摩尔动力(北京)技术股份有限公司 | Gas-driving-closed piston type engine |
| CN104234864B (en) * | 2013-09-12 | 2016-03-16 | 摩尔动力(北京)技术股份有限公司 | Gas closed engine |
| CN108050332A (en) * | 2017-12-12 | 2018-05-18 | 中国舰船研究设计中心 | A kind of steam pipework thermal compensation device and its design method with heat shock resistance effect |
| CN108050332B (en) * | 2017-12-12 | 2019-10-25 | 中国舰船研究设计中心 | A steam pipeline thermal compensation device with thermal shock resistance and its design method |
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| CN1055982C (en) | 2000-08-30 |
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