CN103114939B - Air cylinder phase cycle engine - Google Patents
Air cylinder phase cycle engine Download PDFInfo
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- CN103114939B CN103114939B CN201310042549.2A CN201310042549A CN103114939B CN 103114939 B CN103114939 B CN 103114939B CN 201310042549 A CN201310042549 A CN 201310042549A CN 103114939 B CN103114939 B CN 103114939B
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Abstract
The invention discloses an air cylinder phase cycle engine which comprises an air cylinder piston acting mechanism, an external fire vaporizer, and a condenser. The external fire vaporizer is communicated with an air cylinder of the air cylinder piston acting mechanism. Working medium mouths are formed in the external fire vaporizer and the top of the air cylinder of the air cylinder piston acting mechanism and/or a communication channel between the external fire vaporizer and the air cylinder of the air cylinder piston acting mechanism. The condenser is communicated with the working medium flow mouths. A timing control valve is arranged on a communication channel between the working medium flow mouths and the condenser. The air cylinder phase cycle engine is simple in structure, high in efficiency, low in manufacturing cost, and long in service life.
Description
Technical field
The present invention relates to heat energy and dynamic field, especially a kind of motor.
Background technique
According to the thermal power system that the circulations such as Rankine cycle, Stirling cycle, Otto cycle, diesel cycle and Bradenton circulation manufacture, all there is such and such shortcoming, therefore need to invent the more simple motor of a kind of structure.
Summary of the invention
In order to solve the problem, the technological scheme that the present invention proposes is as follows:
Scheme 1: a kind of air cylinder phase cycle engine, comprises cylinder piston acting mechanism, external combustion vaporizer and condenser; The do work cylinder of mechanism of described external combustion vaporizer and described cylinder piston is communicated with, on described external combustion vaporizer, in the cylinder top of described cylinder piston acting mechanism and/or described external combustion vaporizer and described cylinder piston do work mechanism cylinder between communicating passage on establish working medium communication port, described condenser is communicated with described working medium communication port, and the communicating passage between described working medium communication port and described condenser establishes timing control valve.
Scheme 2: on the basis of scheme 1, described external combustion vaporizer is located in the cylinder lower end of described cylinder piston acting mechanism.
Scheme 3: a kind of air cylinder phase cycle engine, comprises cylinder piston acting mechanism, internal combustion evaporation device and condenser; The do work cylinder of mechanism of described internal combustion evaporation device and described cylinder piston is communicated with, on described internal combustion evaporation device, in the cylinder top of described cylinder piston acting mechanism and/or described internal combustion evaporation device and described cylinder piston do work mechanism cylinder between communicating passage on establish working medium communication port, described condenser is communicated with described working medium communication port, and the communicating passage between described working medium communication port and described condenser establishes timing control valve; In the cylinder, communicating passage between described condenser and this three of described internal combustion evaporation device, described cylinder piston acting mechanism, at least one place establishes working medium export mouth, described internal combustion evaporation device is communicated with oxidizer source, and described internal combustion evaporation device is communicated with reducing agent source.
Scheme 4: on the basis of scheme 3, establishes working medium to derive control valve at described working medium export mouth place.
Scheme 5: on the basis of scheme 3, described internal combustion evaporation device is located in the cylinder lower end of described cylinder piston acting mechanism.
Scheme 6: on the basis of the either a program of scheme 1 to 5, described working medium communication port is arranged on the cylinder of described cylinder piston acting mechanism.
Scheme 7: on the basis of the either a program of scheme 1 to 5, the communicating passage between described working medium communication port and described condenser establishes regenerator.
Scheme 8: on the basis of the either a program of scheme 1 to 5, described air cylinder phase cycle engine also comprises intermittent type liquid feed mechanism.
Scheme 9: on the basis of scheme 8, described intermittent type liquid feed mechanism is set to timing liquid feed mechanism, described timing liquid feed mechanism comprises timing liquor pump and working medium storage tank, the working medium entrance of described working medium storage tank is communicated with described condenser, the sender property outlet of described working medium storage tank is communicated with the working medium entrance of described timing liquor pump, sender property outlet and the described cylinder piston communicating passage of doing work between mechanism and described external combustion vaporizer of described timing liquor pump is communicated with or the sender property outlet of described timing liquor pump is communicated with the communicating passage that described cylinder piston does work between mechanism and described internal combustion evaporation device.
Scheme 10: in scheme 3 to 5 either a program basis on, described air cylinder phase cycle engine also comprises turbo-power mechanism and impeller gas compressor, described working medium export mouth is communicated with the working medium entrance of described turbo-power mechanism, the sender property outlet of described turbo-power mechanism is communicated with through the working medium entrance of attached cooler with described impeller gas compressor, the sender property outlet of described impeller gas compressor and working medium channel connection; Communicating passage between the sender property outlet of described turbo-power mechanism and the working medium entrance of described impeller gas compressor is provided with attached working medium export mouth.
Scheme 11: in scheme 3 to 5 either a program basis on, described oxidizer source is set to four class door cylinder piston mechanisms.
Scheme 12: on the basis of scheme 11, the cylinder of described four class door cylinder piston mechanisms is established suction port, relief opening, air supply opening and is recharged mouth, described suction port, described relief opening, described air supply opening and described recharge a mouthful place be corresponding in turn to arrange intake valve, exhaust valve, for valve and recharge door; Described four class door cylinder piston mechanisms control by the control mechanism making described four class door cylinder piston mechanisms according to suction stroke-air feed stroke of calming the anger-gas refill expansion stroke-exhaust stroke cycle of modes work, described air supply opening is communicated with described internal combustion evaporation device, described in recharge mouth and be communicated with described working medium export mouth.
Scheme 13: in scheme 3 to 5 either a program basis on, described air cylinder phase cycle engine also comprises oxygenant sensor and oxygenant control gear, described oxygenant sensor is located in working medium passage, described oxygenant sensor provides signal to described oxygenant control gear, and described oxidizer source controls to realize adjusting the amount entering the oxygenant of described internal combustion evaporation device by described oxygenant control gear.
Scheme 14: on the basis of scheme 1 or 3, described cylinder piston acting mechanism is set to piston liquid mechanism, and described piston liquid mechanism comprises gas-liquid cylinder and gas-liquid isolating structure, and described gas-liquid isolating structure is located in described gas-liquid cylinder.
Principle of the present invention is: in described internal combustion evaporation device or described external combustion vaporizer, make overheated and/or criticalization of liquid working substance generating gasification make intrasystem pressure increase promote the described cylinder piston in-house descent of piston (by top dead center to lower dead center) that does work externally do work, in the process of described piston approaches bottom dead centre, pressure and temperature in the cylinder of described cylinder piston acting mechanism declines, when piston reaches lower, now open described timing control valve, working medium after decrease temperature and pressure enters described condenser through described working medium communication port, and liquefy in described condenser, the liquid working substance of post liquefaction is back in described external combustion vaporizer or internal combustion evaporation device, the piston of described cylinder piston acting mechanism is by lower dead center convergence top dead center, go round and begin again, periodic duty.
In the present invention, so-called external combustion vaporizer refers to the device that can make the working medium of described air cylinder phase cycle engine that vaporization occurs.
In the present invention, so-called internal combustion evaporation device is the vaporizing unit that the working medium of instigating products of combustion to be directly vaporized with needs directly mixes.
In the present invention, the effect of described working medium export mouth is derived, intrasystem unnecessary working medium to maintain the normal work of system in the structure being provided with described internal combustion evaporation device.
In the present invention, so-called condenser refers to the device of the working medium generation condensation liquefaction that can make air cylinder phase cycle engine of the present invention, and it can be radiator, also can be heat exchanger.
In the present invention, described working medium passage refers to when engine work, the space that working medium stream can arrive.
In the present invention, the working medium of described air cylinder phase cycle engine can be that all liquid-gas phase transition can occur or the working medium of liquid critical state change occurs, such as, working medium in all inorganic Rankine cycles such as water, freon, ethers and organic Rankine bottoming cycle.
In the present invention, described gas-liquid cylinder refers to and can hold gas working medium and/or liquid, and the container of certain pressure can be born, described gas-liquid cylinder is separated into gas end and liquid end by described gas-liquid isolating structure, the gas end of described gas-liquid cylinder is provided with gas working medium communication port, and described gas working medium communication port is used for and other device in described working medium passage or mechanism connection; The liquid end of described gas-liquid cylinder is provided with liquid stream port, and described liquid stream port is used for being communicated with hydraulic power mechanism and/or liquid working substance send-back system.
In the present invention, described gas-liquid isolating structure refers to the structure that can move reciprocatingly in described gas-liquid cylinder, as isolating plate, isolating film, piston etc., its effect be isolation described gas-liquid cylinder in gas working medium and liquid, preferably, described gas-liquid isolating structure and the sealing of described gas-liquid cylinder are slidably matched.In described piston liquid institution staff process, being in the diverse location in described gas-liquid cylinder according to described gas-liquid isolating structure, may be all gas working medium in described gas-liquid cylinder, may be also all liquid, or gas working medium and liquid exist simultaneously.
In the present invention, liquid in described gas-liquid cylinder is different from traditional piston crank mechanism with described gas-liquid isolating structure, piston in traditional piston crank mechanism can stop by the thrust of connecting rod or pulling force, thus the restriction realized piston stroke, and in described gas-liquid cylinder, when the gas working medium in described gas-liquid cylinder does positive work, described gas-liquid isolating structure is stressed to lower dead center direction and moves, liquid is discharged described gas-liquid cylinder with high voltage style and promotes hydraulic power mechanism (such as fluid motor) and externally do work, when liquid is about to drain, change fluid motor mode of operation or start liquid working medium send-back system, liquid in described gas-liquid cylinder is no longer reduced, now liquid can apply braking force to the described gas-liquid isolating structure in described gas-liquid cylinder, make it stop, with the wall preventing it from clashing into the liquid bottom portion of gas-liquid cylinder, when constantly in described gas-liquid cylinder during infusion fluid, described gas-liquid isolating structure can constantly move to top dead center direction, when arriving near top dead center, stop to infusion fluid in described gas-liquid cylinder or make the liquid in described gas-liquid cylinder reduce (outflow), however, liquid in described gas-liquid cylinder and described gas-liquid isolating structure still can move to top dead center direction due to inertia, now, if the pressure of the gas working medium in described gas-liquid cylinder is not high enough, described gas-liquid isolating structure then can be caused to continue to move upward and clash into the wall at gas-liquid cylinder top, in order to avoid this shock, need to make the pressure of gas working medium in gas-liquid cylinder enough high, it is made to be greater than inertial force sum when liquid in described gas-liquid cylinder and described gas-liquid isolating structure move reciprocatingly to the pressure of described gas-liquid isolating structure.
In the present invention, inertial force sum when liquid in gas-liquid cylinder described in the working procedure of described air cylinder phase cycle engine and described gas-liquid isolating structure move reciprocatingly is change, therefore the condition all meeting " pressure of the gas working medium in described gas-liquid cylinder to described gas-liquid isolating structure is greater than inertial force sum when liquid in described gas-liquid cylinder and described gas-liquid isolating structure move reciprocatingly " at any operation time should be ensured in engineering design, such as by the working pressure in the described working medium passage of adjustment, the quality of adjustment gas-liquid isolating structure, the modes such as rearrange liquids density or the rearrange liquids degree of depth realize, wherein, described liquid depth refers to that liquid is in the degree of depth of the liquid on direction that moves reciprocatingly.
So-called " adjusting the working pressure in described working medium passage " is that the volume flowrate by adjusting the gas working medium flowing into and/or flow out described working medium passage realizes, such as, can realize by adjusting the switch gap of described working medium export mouth, each time of unlatching and/or the openings of sizes of described working medium export mouth place control valve.
In the present invention, described internal combustion evaporation device is internal combustion firing chamber, and described internal combustion firing chamber can be set to internal combustion continuous combustion chambers, internal combustion intermittent combustion room or internal combustion timing firing chamber; Described internal combustion continuous combustion chambers refers to the internal combustion firing chamber that can recur described heat-producing chemical reaction in it; Described internal combustion intermittent combustion room refers to the internal combustion firing chamber of the described heat-producing chemical reaction of discontinuous generation, described internal combustion intermittent combustion room can be timing intermittent combustion room, only once described heat-producing chemical reaction occurs in firing chamber in each work cycle of described air cylinder phase cycle engine, described heat-producing chemical reaction only occurs in a stroke; Or can be positive time length interval firing chamber, in the multiple work cycle of described air cylinder phase cycle engine, in firing chamber, once described heat-producing chemical reaction occur; Or can be long timing intermittent combustion room, in the multiple work cycle of described air cylinder phase cycle engine continuous print, firing chamber recurs described heat-producing chemical reaction.
In the present invention, described oxygenant sensor refers to the device detected the content of the oxygenant in described working medium passage.Described oxygenant sensor provides signal to described oxygenant control gear, in the signal that described oxygenant control gear provides according to described oxygenant sensor and the described working medium passage that presets, static or dynamic oxygenate content setting value controls to increase or reduces the amount supplying oxygenant in described working medium passage to described oxidizer control valve, reaches the object of the content of oxygenant in described working medium passage.
The setting value of described oxygenate content can be a numerical value, also can be a numerical intervals, such as: the setting value of the oxygenate content in described working medium passage can be 5%, 10% or 10% ~ 12% etc.
Described oxygenant sensor can be located on the working medium passage away from described internal combustion evaporation device, can ensure that whole working medium passage works under oxygen enrichment (oxygen content is greater than zero) state, make stable combustion chemistry reaction occurs in described internal combustion evaporation device, the generation of carbon distribution can also be prevented simultaneously.
In the present invention, the fuel that combustion chemistry reaction occurs in described internal combustion evaporation device can be hydrocarbon, hydrocarbon oxygen compound or solid carbon.Solid carbon does not have the gas concentration lwevel in water generation and burning afterproduct high after having burning, the advantages such as easy liquefaction; Solid carbon sprays into after can adopting solid assembled in advance, powdered or inputs air cylinder phase cycle engine by the mode sprayed into after liquid or atmospheric carbon dioxide fluidisation again after powdered.
The present inventor proposes the new illustrative fashion of out-of-phase diagram as described below and the second law of thermodynamics:
Pressure and temperature is the most basic, the most important status parameter of working medium.But, in thermodynamic study up to now, the out-of-phase diagram that is coordinate with pressure P and temperature T is not used in the research to thermodynamic process and thermodynamic cycle.In more than 200 year since thermomechanics is born, the thought of thermodynamic process and thermodynamic cycle is studied in the present inventor's first time proposition with out-of-phase diagram.Study in thermodynamic process and thermodynamic cycle utilizing out-of-phase diagram, the present inventor finds that out-of-phase diagram all has obvious advantage than conventional P-V figure and T-S figure, it more can describe the change of working medium state in thermodynamic process and thermodynamic cycle by constitutionally, makes the present inventor have more deep understanding to thermodynamic process and thermodynamic cycle.Utilize out-of-phase diagram, the present inventor summarizes the new illustrative fashion of ten second laws of thermodynamics, although these new illustrative fashion are of equal value with the thermomechanics illustrative fashion of Kelvin in the past and Clausius, but the clearer and more definite difference disclosing heating process to working medium and compression process, also for the exploitation of high efficiency thermal machine specifies direction.This new method and new law, will promote the progress of thermodynamic (al) development and heat engine industry greatly.Specific as follows:
P-V figure and T-S figure is widely used already in thermodynamic study, but in view of P, T be the most important status parameter of working medium, so the present inventor with pressure P and temperature T for coordinate depicts out-of-phase diagram, and Carnot Cycle and Otto Cycle to be identified in the out-of-phase diagram shown in Figure 10.Clearly, out-of-phase diagram makes the change of working medium state in thermodynamic process and thermodynamic cycle more apparent, also makes the essence of thermodynamic process and thermodynamic cycle be more readily understood.Such as: the out-of-phase diagram of the Carnot Cycle shown in Figure 10, the present inventor can be made easily to draw such conclusion: the mission of the reversible adiabatic compression process of Carnot Cycle is the temperature in the mode of reversible adiabatic compression, the temperature of working medium being increased to its high temperature heat source, to realize absorbing heat inflation process from high temperature heat source constant temperature under the prerequisite that is consistent with the temperature of high temperature heat source.In addition, the present inventor can also find out significantly: when the temperature of the high temperature heat source of Carnot Cycle raises, working medium more must be compressed to plus depth by the present inventor in the reversible adiabatic compression process of Carnot Cycle, it is made to reach higher temperature, to reach the temperature of the high temperature heat source after intensification, with realize with heat up after the prerequisite that is consistent of the temperature of high temperature heat source under high temperature heat source constant temperature after heating up to absorb heat inflation process, thus the raising of implementation efficiency.
According to adiabatic process equation
(wherein, C is constant, and k is the adiabatic index of working medium), the present inventor by the Drawing of Curve of adiabatic process equation of different C value in fig. 11.According to mathematical analysis, and as shown in figure 11, any two adiabatic process curves are all non-intersect.This means: the process on same adiabatic process curve is adiabatic process, and be diabatic process with the process of any adiabatic process curve intersection, in other words, the process of the different adiabatic process curve of any connection two is diabatic process (so-called diabatic process refers to the process having heat and transmit, i.e. the process of heat release and the process of heat absorption).In fig. 12, the present inventor has marked two state points, namely puts A and some B.If a thermal procession or a series of interconnective thermal procession are from an A point of arrival B, then the present inventor is referred to as the process of tie point A and some B, otherwise the present inventor is referred to as tie point B and puts the process of A.According to Figure 12, the present inventor can draw such conclusion: if a B is on adiabatic process curve at an A place, then tie point A is adiabatic process with the process of some B; If a B is on the right side of adiabatic process curve at an A place, then tie point A is endothermic process with the process of some B; If a B is in the left side of adiabatic process curve at an A place, then tie point A is exothermic process with the process of some B.Due to tie point A and some B process may be exothermic process, adiabatic process or endothermic process, so the present inventor with a B for reference, an A is defined as respectively there is superfluous temperature, ideal temperature and not enough temperature.In like manner, tie point B and some A process may be exothermic process, adiabatic process or endothermic process, so the present inventor with an A for reference, a B is defined as respectively there is superfluous temperature, ideal temperature and not enough temperature.
Analyzed and definition by these, the present inventor draws following ten new illustrative fashion about the second law of thermodynamics:
1. there is no the participation of endothermic process, exothermic process can not be returned to its initial point.
2. there is no the participation of exothermic process, endothermic process can not be returned to its initial point.
3. there is no the participation of diabatic process, diabatic process can not be returned to its initial point.
4. only use adiabatic process, diabatic process can not be returned to its initial point.
5., when making the pressure recover of endothermic process to the pressure of its initial point with the thermal procession beyond exothermic process, its temperature is necessarily higher than the temperature of its initial point.
6., when making the pressure recover of exothermic process to the pressure of its initial point with the thermal procession beyond endothermic process, its temperature is necessarily lower than the temperature of its initial point.
7. endothermic process can produce superfluous temperature.
8. exothermic process can produce not enough temperature.
9. the efficiency of the heat engine of any not heat release in compression process can not reach the efficiency of Carnot's cycle.
10. pair working medium heating process and the difference of the compression process of working medium is: heating process necessarily produces superfluous temperature, and compression process is quite different.
About ten of the second law of thermodynamics new illustrative fashion, be of equal value, also can through mathematical proof, any one in these ten illustrative fashion all can be used alone.The present inventor advises: in thermodynamic study process, answer extensive use out-of-phase diagram and the above-mentioned new illustrative fashion about the second law of thermodynamics.Out-of-phase diagram and being significant about the exploitation of new illustrative fashion to thermodynamic (al) progress and high efficiency thermal machine of the second law of thermodynamics.
The English expression of the new illustrative fashion of the second law of thermodynamics:
1.It?is?impossible?to?return?a?heat?rej?ection?process?to?its?initial?state?without?a?heat?injection?process?involved.
2.It?is?impossible?to?return?a?heat?injection?process?to?its?initial?state?without?a?heat?rejection?process?involved.
3.It?is?impossible?to?return?a?non-adiabatic?process?to?its?initial?state?without?a?non-adiabatic?process?involved.
4.It?is?impossible?to?return?a?non-adiabatic?process?to?its?initial?state?only?by?adiabatic?process.
5.If?the?final?pressure?of?heat?injection?process?is?returned?to?its?initial?pressure?by?process?other?than?heat?rejection?process,the?temperature?of?that?state?is?higher?than?that?of?the?initial?state.
6.If?the?final?pressure?of?heat?rejection?process?is?returned?to?its?initial?pressure?by?process?other?than?heat?injection?process,the?temperature?of?that?state?is?lower?than?that?of?the?initial?state.
7.It?is?impossible?to?make?heat?injection?process?not?generate?excess-temperature.
8.It?is?impossible?to?make?heat?rejection?process?not?generate?insufficient-temperature.
9.It?is?impossible?for?any?device?that?operates?on?a?cycle?to?reach?the?efficiency?indicated?by?Carnot?cycle?without?heat?rejection?in?compression?process.
10.The?difference?between?heat?injection?process?and?compression?process?which?are?applied?to?working?fluid?of?thermodynamic?process?or?cycle?is?that?heat?injection?process?must?generate?excess-temperature,but?compression?process?must?not.
According to the known technology of heat energy and dynamic field, necessary parts, unit or system etc. are set in the place of necessity.
Beneficial effect of the present invention is as follows:
Structure of the present invention is simple, efficiency is high, the low long service life of cost.
Accompanying drawing explanation
Shown in Fig. 1 is the structural representation of the embodiment of the present invention 1;
Shown in Fig. 2 is the structural representation of the embodiment of the present invention 2;
Shown in Fig. 3 is the structural representation of the embodiment of the present invention 3;
Shown in Fig. 4 is the structural representation of the embodiment of the present invention 4;
Shown in Fig. 5 is the structural representation of the embodiment of the present invention 5;
Shown in Fig. 6 is the structural representation of the embodiment of the present invention 6;
Shown in Fig. 7 is the structural representation of the embodiment of the present invention 7;
Shown in Fig. 8 is the structural representation of the embodiment of the present invention 8;
Shown in Fig. 9 is the structural representation of the embodiment of the present invention 9;
Shown in Figure 10 is the out-of-phase diagram of Carnot's cycle and Otto cycle.Wherein, C
0, C
1and C
2be the constant of different numerical value, k is adiabatic index, and circulation 0-1-2-3-0 is Carnot's cycle, and circulation 0-1-4-5-0 is the Carnot's cycle after high temperature heat source temperature raises, and circulation 0-6-7-8-0 is Otto cycle;
Shown in Figure 11 is the out-of-phase diagram of many different adiabatic process curves.Wherein, C
1, C
2, C
3, C
4and C
5be the constant of different numerical value, k is adiabatic index, A and B is state point;
Shown in Figure 12 is the out-of-phase diagram of adiabatic process curve.Wherein, C is constant, and k is adiabatic index, A and B is state point,
Wherein:
1 cylinder piston acting mechanism, 22 external combustion vaporizers, 21 internal combustion evaporation devices, 3 condensers, 4 working medium communication port, 5 timing control valves, 6 working medium export mouths, 61 working medium derive control valve, 100 turbo-power mechanisms, 200 impeller gas compressors, 401 attached coolers, 3002 attached working medium export mouths, 5001 connecting ports, 101 gas-liquid cylinders, 102 gas-liquid interrupters, 97 liquid working substance send-back systems, 99 process control mechanisms, 96 hydraulic power mechanisms, 80 4 class door cylinder piston mechanisms, 81 suction ports, 82 relief openings, 83 air supply openings, 84 recharge mouth, 85 intake valves, 86 exhaust valves, 87 for valve, 88 recharge door, 58 oxygenant sensors, 52 oxygenant control gear, 53 oxidizer control valve, 55 oxidizer sources, 7 regenerators, 71 working medium storage tank, 70 timing liquor pumps, 5001 connecting ports.
Embodiment
Embodiment 1
Air cylinder phase cycle engine as shown in Figure 1, comprises cylinder piston acting mechanism 1, external combustion vaporizer 22 and condenser 3; The do work cylinder of mechanism 1 of described external combustion vaporizer 22 and described cylinder piston is communicated with, and described external combustion vaporizer 22 is located at the below of described cylinder piston acting mechanism 1, described external combustion vaporizer 22 and described cylinder piston do work mechanism 1 cylinder between communicating passage on establish working medium communication port 4, described condenser 3 is communicated with described working medium communication port 4, and the communicating passage between described working medium communication port 4 and described condenser 3 establishes timing control valve 5.
In the course of the work, working medium after described external combustion vaporizer 22 vaporization promotes the piston of described cylinder piston acting mechanism 1 to lower dead center motion externally acting, in the process of described piston approaches bottom dead centre, pressure and temperature in the cylinder of described cylinder piston acting mechanism 1 declines, when piston arrives lower, open described timing control valve 5, working medium after acting enters in described condenser 3 through described working medium communication port 4, and liquefy in described condenser 3, the liquid working substance of post liquefaction is back in described external combustion vaporizer 22, now close described timing control valve 5, the piston of described cylinder piston acting mechanism 1 is by lower dead center convergence top dead center, and so forth.
Selectively, described working medium communication port 4 is on described external combustion vaporizer 22 or in the cylinder top of described cylinder piston acting mechanism 1.
Embodiment 2
Air cylinder phase cycle engine as shown in Figure 2, and the difference of embodiment 1 is: the communicating passage between described timing control valve 5 and described condenser 3 establishes regenerator 7, object makes the heat entered in described condenser 3 stay in described regenerator 7, and then the condensed working medium of described condenser 3 is returned in the process of described external combustion vaporizer 22 absorb heat, the efficiency of more effective raising motor.
Embodiment 3
Air cylinder phase cycle engine as shown in Figure 3, comprises cylinder piston acting mechanism 1, internal combustion evaporation device 21 and condenser 3; The do work cylinder of mechanism 1 of described internal combustion evaporation device 21 and described cylinder piston is communicated with, and described internal combustion evaporation device 21 is positioned at the below of described cylinder piston acting mechanism 1, described internal combustion evaporation device 21 and described cylinder piston do work mechanism 1 cylinder between communicating passage on establish working medium communication port 4, described condenser 3 is communicated with described working medium communication port 4, and the communicating passage between described working medium communication port 4 and described condenser 3 establishes timing control valve 5; Communicating passage between described internal combustion evaporation device 21 and described cylinder piston acting mechanism 1 establishes working medium export mouth 6, described internal combustion evaporation device 21 is communicated with oxidizer source 55, described internal combustion evaporation device 21 is communicated with reducing agent source, and described working medium export mouth 6 place is provided with working medium delivery valve 61.
Selectively, in the cylinder, communicating passage between described condenser 3 and this three of described internal combustion evaporation device 21, described cylinder piston acting mechanism 1, at least one place establishes working medium export mouth 6.
Selectively, the communicating passage between described working medium communication port 4 and described condenser 3 establishes regenerator 7.
Embodiment 4
Air cylinder phase cycle engine as shown in Figure 4, the difference of itself and embodiment 1 is: described air cylinder phase cycle engine also comprises timing liquid feed mechanism, described timing liquid feed mechanism comprises timing liquor pump 70 and working medium storage tank 71, described condenser 3 is communicated with the working medium entrance of described working medium storage tank 71, the sender property outlet of described working medium storage tank 71 is communicated with the working medium entrance of described timing liquor pump 70, and the communicating passage that sender property outlet and the described cylinder piston of described timing liquor pump 70 do work between mechanism 1 and described internal combustion evaporation device 21 is communicated with.
The condensed working medium of described condenser 3 directly enters described working medium storage tank 71, and the working medium of described working medium storage tank 71 li is pumped in described external combustion vaporizer 22 through described timing liquor pump 70.
Embodiment 5
Air cylinder phase cycle engine as shown in Figure 5, the difference of itself and embodiment 2 is: described cylinder piston mechanism 1 of doing work is located at the below of described external combustion vaporizer 22.
Embodiment 6
Air cylinder phase cycle engine as shown in Figure 6, the difference of itself and embodiment 3 is: described air cylinder phase cycle engine also comprises turbo-power mechanism 100 and impeller gas compressor 200, described working medium export mouth 6 is communicated with the working medium entrance of described turbo-power mechanism 100, the sender property outlet of described turbo-power mechanism 100 is communicated with through the working medium entrance of attached cooler 401 with described impeller gas compressor 200, the sender property outlet of described impeller gas compressor 200 and described working medium channel connection; Passage between the sender property outlet of described turbo-power mechanism 100 and the working medium entrance of described impeller gas compressor 200 is provided with attached working medium export mouth 3002.
In communicating passage between the working medium entrance that described attached working medium export mouth 3002 shown in figure is located at described attached cooler 401 and described impeller gas compressor 200, sender property outlet and the described cylinder piston of described impeller gas compressor 200 mechanism 1 of doing work is communicated with.
Described attached working medium export mouth 3002 is selectively located on the passage between the sender property outlet of described turbo-power mechanism 100 and described attached cooler 401, the sender property outlet of described impeller gas compressor 200 is communicated with the connecting port 5001 be located on described working medium passage, and described connecting port 5001 and described working medium export mouth 6 are located at the diverse location on described working medium passage.
Embodiment 7
Air cylinder phase cycle engine as shown in Figure 7, itself and embodiment 5 distinguish and are: described cylinder piston mechanism 1 of doing work is set to piston liquid mechanism, described piston liquid mechanism comprises gas-liquid cylinder 101 and gas-liquid isolating structure 102, and described gas-liquid isolating structure 102 is located in described gas-liquid cylinder 101.The liquid end of described gas-liquid cylinder 101 is communicated with hydraulic power mechanism 96, and described hydraulic power mechanism 96 is communicated with liquid working substance send-back system 97, and described liquid working substance send-back system 97 is communicated with the liquid end of described gas-liquid cylinder 101; Described hydraulic power mechanism 96 and described liquid working substance send-back system 97 control by process control mechanism 99.
Embodiment 8
Air cylinder phase cycle engine as shown in Figure 8, the difference of itself and embodiment 3 is: described oxidizer source 55 is set to four class door cylinder piston mechanisms 80, the cylinder of described four class door cylinder piston mechanisms 80 is established suction port 81, relief opening 82, air supply opening 83 and is recharged mouth 84, described suction port 81, described relief opening 82, described air supply opening 83 and described recharge mouth 84 place be corresponding in turn to arrange intake valve 85, exhaust valve 86, for valve 87 and recharge door 88; Described four class door cylinder piston mechanisms 80 control by the control mechanism making described four class door cylinder piston mechanisms 80 according to suction stroke-air feed stroke of calming the anger-gas refill expansion stroke-exhaust stroke cycle of modes work, described air supply opening 83 is communicated with described internal combustion evaporation device 21, described in recharge mouth 84 and be communicated with described working medium export mouth 6.
Embodiment 9
Air cylinder phase cycle engine as shown in Figure 9, the difference of itself and embodiment 3 is: described air cylinder phase cycle engine also comprises oxygenant sensor 58 and oxygenant control gear 52, described oxygenant sensor 58 is located in working medium passage, described oxygenant sensor 58 provides signal to described oxygenant control gear 52, and described oxidizer source 55 controls by described oxygenant control gear 52 amount realizing adjusting the oxygenant entering described internal combustion evaporation device 21.
The sensor of oxygenant described in Fig. 9 58 is located in the communicating passage between described cylinder piston acting mechanism 1 and described internal combustion evaporation device 21.
Selectively, the piston of described cylinder piston acting mechanism 1 is connected with connecting rod.
Obviously, the invention is not restricted to above embodiment, according to known technology and the technological scheme disclosed in this invention of related domain, can to derive or association goes out many flexible programs, all these flexible programs, also should think protection scope of the present invention.
Claims (12)
1. an air cylinder phase cycle engine, is characterized in that: comprise cylinder piston acting mechanism (1), external combustion vaporizer (22) and condenser (3), the do work cylinder of mechanism (1) of described external combustion vaporizer (22) and described cylinder piston is communicated with, on described external combustion vaporizer (22), in the cylinder top of described cylinder piston acting mechanism (1) or described external combustion vaporizer (22) and described cylinder piston do work mechanism (1) cylinder between communicating passage on establish working medium communication port (4), described condenser (3) is communicated with described working medium communication port (4), communicating passage between described working medium communication port (4) and described condenser (3) is established timing control valve (5).
2. air cylinder phase cycle engine as claimed in claim 1, is characterized in that: described external combustion vaporizer (22) is located in the cylinder lower end of described cylinder piston acting mechanism (1).
3. an air cylinder phase cycle engine, is characterized in that: comprise cylinder piston acting mechanism (1), internal combustion evaporation device (21) and condenser (3), the do work cylinder of mechanism (1) of described internal combustion evaporation device (21) and described cylinder piston is communicated with, on described internal combustion evaporation device (21), in the cylinder top of described cylinder piston acting mechanism (1) or described internal combustion evaporation device (21) and described cylinder piston do work mechanism (1) cylinder between communicating passage on establish working medium communication port (4), described condenser (3) is communicated with described working medium communication port (4), communicating passage between described working medium communication port (4) and described condenser (3) is established timing control valve (5), in the cylinder, communicating passage between described condenser (3) and this three of described internal combustion evaporation device (21), described cylinder piston acting mechanism (1), at least one place establishes working medium export mouth (6), described internal combustion evaporation device (21) is communicated with oxidizer source (55), and described internal combustion evaporation device (21) is communicated with reducing agent source.
4. air cylinder phase cycle engine according to claim 3, is characterized in that: establish working medium to derive control valve (61) at described working medium export mouth (6) place.
5. air cylinder phase cycle engine as claimed in claim 3, is characterized in that: described internal combustion evaporation device (21) is located in the cylinder lower end of described cylinder piston acting mechanism (1).
6. air cylinder phase cycle engine according to any one of claim 1 to 5, is characterized in that: described working medium communication port (4) is arranged on the cylinder of described cylinder piston acting mechanism (1).
7. air cylinder phase cycle engine according to any one of claim 1 to 5, is characterized in that: the communicating passage between described working medium communication port (4) and described condenser (3) is established regenerator (7).
8. air cylinder phase cycle engine according to any one of claim 3 to 5, it is characterized in that: described air cylinder phase cycle engine also comprises turbo-power mechanism (100) and impeller gas compressor (200), described working medium export mouth (6) is communicated with the working medium entrance of described turbo-power mechanism (100), the sender property outlet of described turbo-power mechanism (100) is communicated with through the working medium entrance of attached cooler (401) with described impeller gas compressor (200), the sender property outlet of described impeller gas compressor (200) and working medium channel connection; Communicating passage between the sender property outlet of described turbo-power mechanism (100) and the working medium entrance of described impeller gas compressor (200) is provided with attached working medium export mouth (3002).
9. air cylinder phase cycle engine according to any one of claim 3 to 5, is characterized in that: described oxidizer source (55) is set to four class door cylinder piston mechanisms (80).
10. air cylinder phase cycle engine according to claim 9, it is characterized in that: on the cylinder of described four class door cylinder piston mechanisms (80), establish suction port (81), relief opening (82), air supply opening (83) and recharge mouth (84), described suction port (81), described relief opening (82), described air supply opening (83) and described recharge mouth (84) place be corresponding in turn to arrange intake valve (85), exhaust valve (86), for valve (87) and recharge door (88); Described four class door cylinder piston mechanisms (80) control by the control mechanism making described four class door cylinder piston mechanisms (80) according to suction stroke-air feed stroke of calming the anger-gas refill expansion stroke-exhaust stroke cycle of modes work, described air supply opening (83) is communicated with described internal combustion evaporation device (21), described in recharge mouth (84) and be communicated with described working medium export mouth (6).
11. according to any one of claim 3 to 5 air cylinder phase cycle engine, it is characterized in that: described air cylinder phase cycle engine also comprises oxygenant sensor (58) and oxygenant control gear (52), described oxygenant sensor (58) is located in working medium passage, described oxygenant sensor (58) provides signal to described oxygenant control gear (52), and described oxidizer source (55) controls by described oxygenant control gear (52) to realize the amount that adjustment enters the oxygenant of described internal combustion evaporation device (21).
12. as described in claim 1 or 3 air cylinder phase cycle engine, it is characterized in that: described cylinder piston acting mechanism (1) is set to piston liquid mechanism, described piston liquid mechanism comprises gas-liquid cylinder (101) and gas-liquid isolating structure (102), and described gas-liquid isolating structure (102) is located in described gas-liquid cylinder (101).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
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| CN201310042549.2A CN103114939B (en) | 2012-02-20 | 2013-02-01 | Air cylinder phase cycle engine |
Applications Claiming Priority (25)
| Application Number | Priority Date | Filing Date | Title |
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| CN201210040476 | 2012-02-20 | ||
| CN201210040476.9 | 2012-02-20 | ||
| CN201210048976 | 2012-02-28 | ||
| CN201210048976.7 | 2012-02-28 | ||
| CN201210054199 | 2012-03-03 | ||
| CN201210054199.7 | 2012-03-03 | ||
| CN201210063356.0 | 2012-03-12 | ||
| CN201210063356 | 2012-03-12 | ||
| CN201210065851.5 | 2012-03-13 | ||
| CN201210065851 | 2012-03-13 | ||
| CN201210134825.3 | 2012-04-28 | ||
| CN201210134824.9 | 2012-04-28 | ||
| CN201210134824 | 2012-04-28 | ||
| CN201210134825 | 2012-04-28 | ||
| CN201210180398.2 | 2012-06-01 | ||
| CN201210180398 | 2012-06-01 | ||
| CN201210201941.2 | 2012-06-16 | ||
| CN201210201941 | 2012-06-16 | ||
| CN201210212534 | 2012-06-22 | ||
| CN201210212534.1 | 2012-06-22 | ||
| CN201210217777 | 2012-06-27 | ||
| CN201210217777.4 | 2012-06-27 | ||
| CN201210233188 | 2012-07-05 | ||
| CN201210233188.5 | 2012-07-05 | ||
| CN201310042549.2A CN103114939B (en) | 2012-02-20 | 2013-02-01 | Air cylinder phase cycle engine |
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| CN103114939A CN103114939A (en) | 2013-05-22 |
| CN103114939B true CN103114939B (en) | 2015-01-21 |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN105822453A (en) * | 2016-05-11 | 2016-08-03 | 刘良存 | External combustion type liquid engine |
| CN215109063U (en) * | 2019-11-29 | 2021-12-10 | 钟学斌 | Low-loss prime motor |
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Effective date of registration: 20201202 Address after: Guolou village, sikm south, Weiwan Town, Caoxian County, Heze City, Shandong Province, 274400 Patentee after: Caoxian Luguan furfural Co., Ltd Address before: 100101, Beijing, Chaoyang District Beiyuan Road, No. 168, Sheng Sheng building, 24 floor Patentee before: MOLECULE POWER BEIJING TECH Co. |
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