CN103114939A - Air cylinder phase cycle engine - Google Patents
Air cylinder phase cycle engine Download PDFInfo
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- CN103114939A CN103114939A CN2013100425492A CN201310042549A CN103114939A CN 103114939 A CN103114939 A CN 103114939A CN 2013100425492 A CN2013100425492 A CN 2013100425492A CN 201310042549 A CN201310042549 A CN 201310042549A CN 103114939 A CN103114939 A CN 103114939A
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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 power field, especially a kind of motor.
Background technique
The thermal power system of making according to circulations such as Rankine cycle, Stirling circulation, Otto cycle, diesel circulation and Bradenton circulations all has such and such shortcoming, therefore needs the more simple motor of a kind of structure of invention.
Summary of the invention
In order to address the above problem, the technological scheme that the present invention proposes is as follows:
Scheme 1: a kind of cylinder phase cycle engine comprises cylinder piston acting mechanism, external combustion vaporizer and condenser; Described external combustion vaporizer is communicated with the cylinder of described cylinder piston acting mechanism, on described external combustion vaporizer, establishing the working medium communication port on the cylinder top of described cylinder piston acting mechanism and/or on described external combustion vaporizer and described cylinder piston do work communicating passage between the cylinder of mechanism, described condenser is communicated with described working medium communication port, establishes the timing control valve on the communicating passage between described working medium communication port and described condenser.
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 cylinder phase cycle engine comprises cylinder piston acting mechanism, internal combustion evaporation device and condenser; Described internal combustion evaporation device is communicated with the cylinder of described cylinder piston acting mechanism, on described internal combustion evaporation device, establishing the working medium communication port on the cylinder top of described cylinder piston acting mechanism and/or on described internal combustion evaporation device and described cylinder piston do work communicating passage between the cylinder of mechanism, described condenser is communicated with described working medium communication port, establishes the timing control valve on the communicating passage between described working medium communication port and described condenser; Establish the working medium export mouth at least one place in communicating passage between cylinder, described condenser and this three of described internal combustion evaporation device, described cylinder piston acting mechanism, described internal combustion evaporation device is communicated with oxidizer source, and described internal combustion evaporation device is communicated with the reducing agent source.
Scheme 4: on the basis of scheme 3, the place establishes working medium derivation control valve at described working medium export mouth.
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 arbitrary scheme 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 arbitrary scheme of scheme 1 to 5, establish regenerator on the communicating passage between described working medium communication port and described condenser.
Scheme 8: on the basis of arbitrary scheme of scheme 1 to 5, described 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 made as 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, the sender property outlet of described timing liquor pump is communicated with communicating passage between described cylinder piston acting mechanism and described external combustion vaporizer 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 on the basis of arbitrary scheme, described 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 the working medium entrance of described impeller gas compressor through attached cooler, 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: on the basis of arbitrary scheme, described oxidizer source is made as four class door cylinder piston mechanisms in scheme 3 to 5.
Scheme 12: on the basis of scheme 11, establish suction port, relief opening, air supply opening and recharge mouth on the cylinder of described four class door cylinder piston mechanisms, described suction port, described relief opening, described air supply opening and described recharge mouth locate successively correspondence intake valve, exhaust valve are set, for valve with recharge door; Described four class door cylinder piston mechanisms are made described four class door cylinder piston mechanisms control according to the control mechanism that the suction stroke-air feed stroke-gas of calming the anger recharges expansion stroke-exhaust stroke mode cycle work, described air supply opening is communicated with described internal combustion evaporation device, and the described mouth that recharges is communicated with described working medium export mouth.
Scheme 13: in scheme 3 to 5 on the basis of arbitrary scheme, described cylinder phase cycle engine also comprises oxygenant sensor and oxygenant control gear, described oxygenant sensor is located in the working medium passage, described oxygenant sensor provides signal to described oxygenant control gear, and described oxidizer source is subjected to described oxygenant control gear to control to realize adjusting the amount of the oxygenant that enters described internal combustion evaporation device.
Scheme 14: on the basis of scheme 1 or 3, described cylinder piston acting mechanism is made as 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: make overheated and/or criticalization of liquid working substance generating gasification that intrasystem pressure is increased in described internal combustion evaporation device or described external combustion vaporizer to promote the in-house descent of piston of described cylinder piston acting (by top dead center to lower dead center) externally to do work, in the process of described piston approaches bottom dead centre, pressure and temperature in the cylinder of described cylinder piston acting mechanism descends, in the time of near piston reaches lower dead center, open described timing control valve this moment, working medium after decrease temperature and pressure enters described condenser through described working medium communication port, and liquefy in described condenser, liquid working substance after 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 make the working medium of described cylinder phase cycle engine that the device of vaporization occurs.
In the present invention, so-called internal combustion evaporation device is to instigate the direct vaporizing unit that directly mixes with the working medium that need to be vaporized of products of combustion.
In the present invention, the effect of described working medium export mouth is in the structure that is provided with described internal combustion evaporation device, intrasystem unnecessary working medium to be derived, to keep the normal operation of system.
In the present invention, so-called condenser refers to make the device of the working medium generation condensation liquefaction of cylinder phase cycle engine of the present invention, and it can be radiator, can be also 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 cylinder phase cycle engine can be that all liquid-gas phase transition can occur or the working medium that liquid critical state changes occurs, and the working medium in all inorganic Rankine cycles such as water, freon, ethers and organic Rankine circulation all can.
In the present invention, described gas-liquid cylinder refers to hold gas working medium and/or liquid, and the container of energy bearing certain pressure, 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 the gas working medium communication port, and described gas working medium communication port is used for other device or the mechanism connection with described working medium passage; The liquid end of described gas-liquid cylinder is provided with the liquid communication mouth, and described liquid communication mouth 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 is gas working medium and the liquid in the described gas-liquid cylinder of isolation, preferably, described gas-liquid isolating structure and described gas-liquid cylinder sealed sliding are movingly.In described piston liquid mechanism working procedure, be in 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, perhaps 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 be stopped by the thrust of connecting rod or pulling force, thereby realize the restriction to piston stroke, and in described gas-liquid cylinder, when the gas working medium in described gas-liquid cylinder is done positive work, described gas-liquid isolating structure is stressed and moves to the lower dead center direction, liquid is discharged described gas-liquid cylinder with high voltage style and promoted externally acting of hydraulic power mechanism (for example liquid motor), when liquid is about to drain, change liquid motor operations pattern or start liquid working medium send-back system, liquid in described gas-liquid cylinder is no longer reduced, this moment, liquid can apply braking force to the described gas-liquid isolating structure in described gas-liquid cylinder, it is stopped, to prevent that it from clashing into the wall of the liquid bottom section of gas-liquid cylinder, when constantly in the described gas-liquid cylinder during infusion fluid, described gas-liquid isolating structure can constantly move to the top dead center direction, in the time of near arriving top dead center, stop in the described gas-liquid cylinder infusion fluid or make the liquid in described gas-liquid cylinder reduce (outflow), however, liquid and described gas-liquid isolating structure in described gas-liquid cylinder still can be because inertia moves to the top dead center direction, at this moment, if the pressure of the gas working medium in described gas-liquid cylinder is not high enough, can cause described gas-liquid isolating structure continue to move upward and clash into the wall at gas-liquid cylinder top, for fear of this shock, need to make the pressure of gas working medium in gas-liquid cylinder enough high, inertial force sum when it is moved reciprocatingly greater than the liquid in described gas-liquid cylinder and described gas-liquid isolating structure to the pressure of described gas-liquid isolating structure.
in the present invention, inertial force sum when the liquid in gas-liquid cylinder described in the working procedure of described cylinder phase cycle engine and described gas-liquid isolating structure move reciprocatingly changes, therefore should guarantee all to satisfy at any operation time the condition of " the inertial force sum the when gas working medium in described gas-liquid cylinder moves reciprocatingly greater than the liquid in described gas-liquid cylinder and described gas-liquid isolating structure to the pressure of described gas-liquid isolating structure " in engineering design, for example by adjusting the working pressure in described working medium passage, adjust the quality of gas-liquid isolating structure, the modes such as fluid density or adjustment liquid depth of adjusting realize, wherein, described liquid depth refers to the degree of depth of the liquid of liquid on the direction that moves reciprocatingly.
So-called " adjusting the working pressure in described working medium passage " is to flow into and/or the volume flowrate that flows out the gas working medium of described working medium passage realizes by adjustment, for example can realize by the openings of sizes of the switch gap of adjusting described working medium export mouth, each time of opening and/or described working medium export mouth place control valve.
In the present invention, described internal combustion evaporation device is the internal combustion firing chamber, and described internal combustion firing chamber can be made as internal combustion continuous combustion chambers, internal combustion intermittent combustion chamber 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 chamber refers to the internal combustion firing chamber of the described heat-producing chemical reaction of discontinuous generation, described internal combustion intermittent combustion chamber can be timing intermittent combustion chamber, once described heat-producing chemical reaction only occurs in the firing chamber in each work cycle of described cylinder phase cycle engine, and described heat-producing chemical reaction only occurs in a stroke; Can be perhaps positive time length interval firing chamber, once described heat-producing chemical reaction occurs in the firing chamber in a plurality of work cycle of described cylinder phase cycle engine; Can be perhaps long timing intermittent combustion chamber, in the continuous a plurality of work cycle of described cylinder phase cycle engine, the firing chamber recurs described heat-producing chemical reaction.
In the present invention, described oxygenant sensor refers to the device that the content to the oxygenant in described working medium passage detects.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 predefined described working medium passage, static or dynamic oxygenate content setting value controls to increase or reduces the amount of supplying with oxygenant in the described working medium passage to described oxygenant control valve, reaches the purpose of the content of oxygenant in described working medium passage.
The setting value of described oxygenate content can be a numerical value, can be also a numerical value interval, can be 5%, 10% or 10% ~ 12% etc. such as: the setting value of the oxygenate content in described working medium passage.
Described oxygenant sensor can be located on working medium passage away from described internal combustion evaporation device, can guarantee that whole working medium passage is to work under oxygen enrichment (oxygen content is greater than zero) state, make stable combustion chemistry reaction occurs in described internal combustion evaporation device, can also prevent the generation of carbon distribution simultaneously.
In the present invention, the fuel that the 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 can adopt spray into after solid assembled in advance, powdered or powdered after input cylinder phase cycle engine with the mode that sprays into after liquid or atmospheric carbon dioxide fluidisation again.
The inventor proposes the new elaboration mode 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.Yet, in thermodynamic study up to now, do not have the out-of-phase diagram take pressure P and temperature T as coordinate is used for research to thermodynamic process and thermodynamic cycle.In more than 200 year since thermomechanics is born, the inventor proposes the thought with out-of-phase diagram research thermodynamic process and thermodynamic cycle for the first time.In utilizing out-of-phase diagram research thermodynamic process and thermodynamic cycle, the inventor finds that out-of-phase diagram all has obvious advantage than P-V figure commonly used and T-S figure, it more constitutionally the variation of working medium state in thermodynamic process and thermodynamic cycle is described, make the inventor to thermodynamic process and thermodynamic cycle, more deep understanding be arranged.Utilize out-of-phase diagram, the inventor has summed up the new elaboration mode of ten second laws of thermodynamics, although it is of equal value that these new elaboration modes and Kelvin in the past and Clausius's thermomechanics is set forth mode, but clearer and more definite announcement to the difference of heating process and the compression process of working medium, also indicated direction for the exploitation of high efficiency thermal machine.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 are widely used in thermodynamic study already, yet in view of P, T are the most important status parameters of working medium, so the inventor has drawn out-of-phase diagram take pressure P and temperature T as coordinate, and Carnot Cycle and Otto Cycle are identified in out-of-phase diagram shown in Figure 10.Clearly, out-of-phase diagram makes the variation of working medium state in thermodynamic process and thermodynamic cycle more apparent, and the essence of thermodynamic process and thermodynamic cycle is more readily understood.For example: the out-of-phase diagram of Carnot Cycle shown in Figure 10, can make the inventor easily draw such conclusion: the mission of the reversible adiabatic compression process of Carnot Cycle is that the mode with reversible adiabatic compression is increased to the temperature of working medium the temperature of its high temperature heat source, under the prerequisite that is consistent with the temperature that realizes with high temperature heat source from high temperature heat source constant temperature heat absorption inflation process.In addition, the inventor can also find out significantly: when the temperature of the high temperature heat source of Carnot Cycle raises, the inventor must be with more plus depth ground compression of working medium in the reversible adiabatic compression process of Carnot Cycle, make it 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 heat absorption inflation process after heating up, thereby the raising of implementation efficiency.
According to adiabatic process equation
(wherein, C is constant, and k is the adiabatic index of working medium), the inventor with the Drawing of Curve of adiabatic process equation of different C values in Figure 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 with the process of any adiabatic process curve intersection be diabatic process, in other words, the process of two different adiabatic process curves of any connection is diabatic process (so-called diabatic process refers to have the process that heat transmits, the i.e. process of heat release and the process of heat absorption).In Figure 12, the inventor has marked two state points, namely puts A and puts B.If a thermal procession or a series of interconnective thermal procession are from an A point of arrival B, the inventor is referred to as the process of tie point A and some B, otherwise the inventor is referred to as the process of tie point B and some A.According to shown in Figure 12, the inventor can draw such conclusion: on adiabatic process curve at some A place, the process of tie point A and some B is adiabatic process as a B; As the right side of a B at adiabatic process curve at some A place, the process of tie point A and some B is endothermic process; As the left side of a B at adiabatic process curve at some A place, the process of tie point A and some B is exothermic process.Because the process of tie point A and some B may be exothermic process, adiabatic process or endothermic process, thus the inventor take a B as reference, will put A be defined as respectively have superfluous temperature, ideal temperature and not enough temperature.In like manner, the process of tie point B and some A may be exothermic process, adiabatic process or endothermic process, thus the inventor take an A as reference, will put B be defined as respectively have superfluous temperature, ideal temperature and not enough temperature.
By these analyses and definition, the inventor draws following ten about the new elaboration mode of 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 of endothermic process return 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 of exothermic process return 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.
Any in compression process the efficient of the heat engine of not heat release can not reach the efficient of Carnot's cycle.
10. be to the heating process of working medium with to the difference of the compression process of working medium: heating process necessarily produces superfluous temperature, and compression process is quite different.
About ten of the second law of thermodynamics new elaboration modes, be of equal value, also can be through mathematical proof, any one in these ten elaboration modes all can be used separately.Inventor's suggestion: in the thermodynamic study process, answer extensive use out-of-phase diagram and above-mentioned new elaboration mode about the second law of thermodynamics.Out-of-phase diagram and the exploitation to thermodynamic (al) progress and high efficiency thermal machine is significant about the new elaboration mode of the second law of thermodynamics.
The English expression of the new elaboration mode 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 in heat energy and power field, necessary parts, unit or system etc. are set in the place of necessity.
Beneficial effect of the present invention is as follows:
The present invention is simple in structure, efficient is high, the low long service life of cost.
Description of drawings
Shown in Figure 1 is the structural representation of the embodiment of the present invention 1;
Shown in Figure 2 is the structural representation of the embodiment of the present invention 2;
Shown in Figure 3 is the structural representation of the embodiment of the present invention 3;
Shown in Figure 4 is the structural representation of the embodiment of the present invention 4;
Shown in Figure 5 is the structural representation of the embodiment of the present invention 5;
Shown in Figure 6 is the structural representation of the embodiment of the present invention 6;
Shown in Figure 7 is the structural representation of the embodiment of the present invention 7;
Shown in Figure 8 is the structural representation of the embodiment of the present invention 8;
Shown in Figure 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 the 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, and A and B are state points;
Shown in Figure 12 is the out-of-phase diagram of adiabatic process curve.Wherein, C is constant, and k is adiabatic index, and A and B are state points,
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 oxygenant control valves, 55 oxidizer sources, 7 regenerators, 71 working medium storage tank, 70 timing liquor pumps, 5001 connecting ports.
Embodiment
Cylinder phase cycle engine as shown in Figure 1 comprises cylinder piston acting mechanism 1, external combustion vaporizer 22 and condenser 3; Described external combustion vaporizer 22 is communicated with the cylinder of described cylinder piston acting mechanism 1, and described external combustion vaporizer 22 is located at the below of described cylinder piston acting mechanism 1, establish working medium communication port 4 on the communicating passage between the cylinder of described external combustion vaporizer 22 and described cylinder piston acting mechanism 1, described condenser 3 is communicated with described working medium communication port 4, establishes timing control valve 5 on the communicating passage between described working medium communication port 4 and described condenser 3.
in the course of the work, working medium after 22 vaporizations of described external combustion vaporizer promotes the piston of described cylinder piston acting mechanism 1 to externally acting of lower dead center motion, in the process of described piston approaches bottom dead centre, pressure and temperature in the cylinder of described cylinder piston acting mechanism 1 descends, in the time of near the piston arrives lower dead center, open described timing control valve 5, working medium after acting enters in described condenser 3 through described working medium communication port 4, and interior liquefaction of described condenser 3, liquid working substance after liquefaction is back in described external combustion vaporizer 22, close described timing control valve 5 this moment, 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 on the cylinder top of described cylinder piston acting mechanism 1.
Cylinder phase cycle engine as shown in Figure 2, and embodiment 1 difference is: establish regenerator 7 on the communicating passage between described timing control valve 5 and described condenser 3, purpose is that the heat that enters in described condenser 3 is stayed 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 efficient of more effective raising motor.
Cylinder phase cycle engine as shown in Figure 3 comprises cylinder piston acting mechanism 1, internal combustion evaporation device 21 and condenser 3; Described internal combustion evaporation device 21 is communicated with the cylinder of described cylinder piston acting mechanism 1, and described internal combustion evaporation device 21 is positioned at the below of described cylinder piston acting mechanism 1, establish working medium communication port 4 on the communicating passage between the cylinder of described internal combustion evaporation device 21 and described cylinder piston acting mechanism 1, described condenser 3 is communicated with described working medium communication port 4, establishes timing control valve 5 on the communicating passage between described working medium communication port 4 and described condenser 3; Establish working medium export mouth 6 on the communicating passage between described internal combustion evaporation device 21 and described cylinder piston acting mechanism 1, described internal combustion evaporation device 21 is communicated with oxidizer source 55, described internal combustion evaporation device 21 is communicated with the reducing agent source, and described working medium export mouth 6 places are provided with working medium delivery valve 61.
Selectively, establish working medium export mouth 6 at least one place in the communicating passage between cylinder, described condenser 3 and this three of described internal combustion evaporation device 21, described cylinder piston acting mechanism 1.
Selectively, establish regenerator 7 on the communicating passage between described working medium communication port 4 and described condenser 3.
Cylinder phase cycle engine as shown in Figure 4, its difference with embodiment 1 is: described 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 sender property outlet of described timing liquor pump 70 is communicated with the communicating passage that described cylinder piston does work between mechanism 1 and described internal combustion evaporation device 21.
The condensed working medium of described condenser 3 directly enters described working medium storage tank 71, and the working medium that described working medium storage tank is 71 li is pumped in described external combustion vaporizer 22 through described timing liquor pump 70.
Cylinder phase cycle engine as shown in Figure 5, itself and embodiment's 2 difference is: described cylinder piston acting mechanism 1 is located at the below of described external combustion vaporizer 22.
Cylinder phase cycle engine as shown in Figure 6, its difference with embodiment 3 is: described 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 the working medium entrance of described impeller gas compressor 200 through attached cooler 401, 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.
Described attached working medium export mouth 3002 shown in figure is located on communicating passage between the working medium entrance of described attached cooler 401 and described impeller gas compressor 200, and the sender property outlet of described impeller gas compressor 200 is communicated with described cylinder piston acting mechanism 1.
Described attached working medium export mouth 3002 selectively is located on the sender property outlet and the passage between described attached cooler 401 of described turbo-power mechanism 100, the sender property outlet of described impeller gas compressor 200 is communicated with connecting port 5001 on being located at 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.
Cylinder phase cycle engine as shown in Figure 7, itself and embodiment 5 differences are: described cylinder piston acting mechanism 1 is made as 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 are controlled by process control mechanism 99.
Cylinder phase cycle engine as shown in Figure 8, itself and embodiment's 3 difference is: described oxidizer source 55 is made as four class door cylinder piston mechanisms 80, establish suction port 81, relief opening 82, air supply opening 83 and recharge mouthfuls 84 on the cylinder of described four class door cylinder piston mechanisms 80, described suction port 81, described relief opening 82, described air supply opening 83 and described recharge mouthful 84 places successively correspondence intake valve 85, exhaust valve 86 are set, for valve 87 with recharge door 88; Described four class door cylinder piston mechanisms 80 are made described four class door cylinder piston mechanisms 80 control according to the control mechanism that the suction stroke-air feed stroke-gas of calming the anger recharges expansion stroke-exhaust stroke mode cycle work, described air supply opening 83 is communicated with described internal combustion evaporation device 21, and the described mouth 84 that recharges is communicated with described working medium export mouth 6.
Embodiment 9
Cylinder phase cycle engine as shown in Figure 9, its difference with embodiment 3 is: described cylinder phase cycle engine also comprises oxygenant sensor 58 and oxygenant control gear 52, described oxygenant sensor 58 is located in the working medium passage, 58 pairs of described oxygenant control gear 52 of described oxygenant sensor provide signal, and described oxidizer source 55 is subjected to described oxygenant control gear 52 to control to realize adjusting the amount of the oxygenant that enters described internal combustion evaporation device 21.
The sensor of oxygenant described in Fig. 9 58 is located on 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 derive or association goes out many flexible programs, all these flexible programs also should be thought protection scope of the present invention.
Claims (10)
1. a cylinder phase cycle engine, is characterized in that: comprise cylinder piston acting mechanism (1), external combustion vaporizer (22) and condenser (3); Described external combustion vaporizer (22) is communicated with the cylinder of described cylinder piston acting mechanism (1), go up at described external combustion vaporizer (22), establishing working medium communication port (4) on the cylinder top of described cylinder piston acting mechanism (1) and/or on the communicating passage between the cylinder of described external combustion vaporizer (22) and described cylinder piston acting mechanism (1), described condenser (3) is communicated with described working medium communication port (4), establishes timing control valve (5) on the communicating passage between described working medium communication port (4) and described condenser (3).
2. 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. a cylinder phase cycle engine, is characterized in that: comprise cylinder piston acting mechanism (1), internal combustion evaporation device (21) and condenser (3); Described internal combustion evaporation device (21) is communicated with the cylinder of described cylinder piston acting mechanism (1), go up at described internal combustion evaporation device (21), establishing working medium communication port (4) on the cylinder top of described cylinder piston acting mechanism (1) and/or on the communicating passage between the cylinder of described internal combustion evaporation device (21) and described cylinder piston acting mechanism (1), described condenser (3) is communicated with described working medium communication port (4), establishes timing control valve (5) on the communicating passage between described working medium communication port (4) and described condenser (3); Establish working medium export mouth (6) at least one place in communicating passage between cylinder, described condenser (3) and this three of described internal combustion evaporation device (21), described cylinder piston acting mechanism (1), described internal combustion evaporation device (21) is communicated with oxidizer source (55), and described internal combustion evaporation device (21) is communicated with the reducing agent source.
4. cylinder phase cycle engine according to claim 3, is characterized in that: locate to establish working medium at described working medium export mouth (6) and derive control valve (61).
5. 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. as cylinder phase cycle engine as described in any one in claim 1 to 5, it is characterized in that: described working medium communication port (4) is arranged on the cylinder of described cylinder piston acting mechanism (1).
7. as cylinder phase cycle engine as described in any one in claim 1 to 5, it is characterized in that: establish regenerator (7) on the communicating passage between described working medium communication port (4) and described condenser (3).
8. the described cylinder phase of any one cycle engine according to claim 1 to 5 is characterized in that: described cylinder phase cycle engine also comprises intermittent type liquid feed mechanism.
9. cylinder phase cycle engine according to claim 8, it is characterized in that: described intermittent type liquid feed mechanism is made as timing liquid feed mechanism, described timing liquid feed mechanism comprises timing liquor pump (70) and working medium storage tank (71), the working medium entrance of described working medium storage tank (71) is communicated with described condenser (3), the sender property outlet of described working medium storage tank (71) is communicated with the working medium entrance of described timing liquor pump (70), the sender property outlet of described timing liquor pump (70) is communicated with communicating passage between described cylinder piston acting mechanism (1) and described external combustion vaporizer (22) or the sender property outlet of described timing liquor pump (70) is communicated with the communicating passage that described cylinder piston does work between mechanism (1) and described internal combustion evaporation device (21).
10. as cylinder phase cycle engine as described in any one in claim 3 to 5, it is characterized in that: described 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 working medium entrance of the sender property outlet of described turbo-power mechanism (100) and described impeller gas compressor (200) is provided with attached working medium export mouth (3002).
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 |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201210040476 | 2012-02-20 | ||
| CN201210040476.9 | 2012-02-20 | ||
| CN201210048976.7 | 2012-02-28 | ||
| CN201210048976 | 2012-02-28 | ||
| CN201210054199 | 2012-03-03 | ||
| CN201210054199.7 | 2012-03-03 | ||
| CN201210063356 | 2012-03-12 | ||
| CN201210063356.0 | 2012-03-12 | ||
| CN201210065851.5 | 2012-03-13 | ||
| CN201210065851 | 2012-03-13 | ||
| CN201210134825.3 | 2012-04-28 | ||
| CN201210134825 | 2012-04-28 | ||
| CN201210134824.9 | 2012-04-28 | ||
| CN201210134824 | 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 true CN103114939A (en) | 2013-05-22 |
| CN103114939B CN103114939B (en) | 2015-01-21 |
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| CN103114939B (en) | 2015-01-21 |
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