CN103147878A - Phase cycling engine for hot cylinder - Google Patents
Phase cycling engine for hot cylinder Download PDFInfo
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- CN103147878A CN103147878A CN2013100392751A CN201310039275A CN103147878A CN 103147878 A CN103147878 A CN 103147878A CN 2013100392751 A CN2013100392751 A CN 2013100392751A CN 201310039275 A CN201310039275 A CN 201310039275A CN 103147878 A CN103147878 A CN 103147878A
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Abstract
The invention discloses a phase cycling engine for a hot cylinder, which comprises a cylinder piston mechanism, a vaporizer, a heat regenerator and a condenser, wherein the cylinder piston mechanism is communicated with the heat regenerator; the heat regenerator is communicated with the condenser; the condenser is communicated with a timing pulse liquid mechanism; and the vaporizer is arranged in the cylinder piston mechanism and/or is arranged on a channel between the heat regenerator and the cylinder piston mechanism. The phase cycling engine for the hot cylinder has the advantages of simple structure, high efficiency, low cost and long service life.
Description
Technical field
The present invention relates to heat energy and power field, especially a kind of hot cylinder phase cycle engine.
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 hot cylinder phase cycle engine, comprise cylinder piston mechanism, vaporizer and condenser, the cylinder of described cylinder piston mechanism is communicated with described condenser, described condenser and timing pulse liquid mechanism connection, described vaporizer are arranged in described cylinder piston mechanism and/or are arranged on communicating passage between described condenser and described cylinder piston mechanism.
Scheme 2: on the basis of scheme 1, described vaporizer is made as the internal combustion firing chamber, establishes the working medium export mouth on the working medium conduit wall.
Scheme 3: on the basis of scheme 2, establish regenerator on the communicating passage between described vaporizer and described condenser, described working medium export mouth is arranged on communicating passage between described condenser and described regenerator, or is arranged in described timing pulse liquid mechanism.
Scheme 4: on the basis of scheme 1, described vaporizer is made as and take the external combustion firing chamber as the external combustion heat exchanger of thermal source.
Scheme 5: on the basis of scheme 1, described vaporizer is made as the residual heat exchanger take waste heat as thermal source.
Scheme 6: on the basis of scheme 1, described vaporizer is made as the solar energy heat exchanger take solar energy as thermal source.
Scheme 7: on scheme 1,2,4,5 or 6 basis, establish regenerator on the passage between described vaporizer and described condenser.
Scheme 8: on the basis of scheme 7, described regenerator is made as the material filling type regenerator.
Scheme 9: on scheme 1,2,4,5 or 6 basis, described timing pulse liquid mechanism is made as piston type liquid reciprocator, and the piston of described piston type liquid reciprocator and the piston of described cylinder piston mechanism are by the interlock of timing relation.
Scheme 10: on scheme 1,2,4,5 or 6 basis, described timing pulse liquid mechanism is made as the timing liquor pump, shown in the entrance of timing liquor pump be communicated with described condenser, described timing liquid delivery side of pump is communicated with described vaporizer.
Scheme 11: on the basis of scheme 10, described timing liquid delivery side of pump is communicated with described vaporizer through regenerator.
Scheme 12: on the basis of scheme 7, described regenerator is made as the heat exchanger type regenerator, the liquid inlet of described timing pulse liquid mechanism is communicated with described condenser, the liquid outlet of described timing pulse liquid mechanism is communicated with the entrance that is heated the fluid passage of described heat exchanger type regenerator, and the outlet that is heated the fluid passage of described heat exchanger type regenerator is communicated with described vaporizer.
Scheme 13: on the basis of scheme 10, establish the liquid storage space on the communicating passage between described timing liquor pump and described condenser.
scheme 14: in scheme 1, 2, 4, on 5 or 6 basis, described timing pulse liquid mechanism is made as by liquor pump, heat exchanger type regenerator and timing control valve consist of, the entrance of described liquor pump is communicated with described condenser, described liquid delivery side of pump is communicated with the entrance that is heated the fluid passage of described heat exchanger type regenerator, the outlet that is heated the fluid passage of described heat exchanger type regenerator is communicated with described timing control valve, described timing control valve is communicated with described vaporizer, the zone of heat liberation that adds of described heat exchanger type regenerator arranges on communicating passage between described vaporizer and described condenser.
Scheme 15: on scheme 1,2,4,5 or 6 basis, establish gas working medium timing control valve on the passage between described vaporizer and described condenser.
Scheme 16: on scheme 1,2,4,5 or 6 basis, the working medium of described hot cylinder phase cycle engine is made as water or organic substance.
Scheme 17: on the basis of scheme 2, described hot 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; Establish attached working medium export mouth on the passage between the working medium entrance of the sender property outlet of described turbo-power mechanism and described impeller gas compressor.
Scheme 18: on the basis of scheme 2, described hot cylinder phase cycle engine comprises oxidizer source, reducing agent source, 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, described oxidizer source is through oxygenant control valve and described working medium channel connection, described oxygenant control gear is controlled described oxygenant control valve, described reducing agent source and described working medium channel connection.
Scheme 19: on the basis of scheme 2, the mass flow rate of the material of described internal combustion firing chamber discharge is greater than the mass flow rate of the material of the described internal combustion of importing firing chamber outside the working medium passage.
Scheme 20: on scheme 1,2,4,5 or 6 basis, described cylinder piston 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.
Scheme 21: on the basis of scheme 20, 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.
principle of the present invention is: make overheated and/or criticalization of working medium generating gasification in described vaporizer, intrasystem pressure is increased, the piston that the High Temperature High Pressure working medium that produces promotes in described cylinder piston mechanism moves and externally acting to lower dead center, in crossing the process of the continuous convergence top dead center of lower dead center, described piston makes working medium directly or enter described condenser after described regenerator generation temperature drop, and liquefy in described condenser, liquid working substance after liquefaction is by described timing pulse liquid collect, in the time of near described piston is in top dead center, described timing pulse liquid mechanism directly turns back to liquid working substance in described vaporizer, or after endothermic process is sent into described regenerator, after further absorbing heat intensification or heat absorption phase transformation, described regenerator enters described vaporizer again, enter next circulation external outputting power that goes round and begins again.
Vaporizer of the present invention refers to make the working medium of described hot cylinder phase cycle engine that the device of vaporization occurs, and it can be heat exchanger, can be also the internal combustion firing chamber.
Regenerator described in the present invention can be the regenerator that back and forth circulates, and leaves heat for regenerator when namely hot working fluid flows through, draw heat from regenerator again when cold working medium refluxes by original passage.
Condenser described in the present invention refers to make the device of the working medium generation condensation liquefaction in the present invention, and it can be radiator, can be also heat exchanger.
The pulse liquid of timing described in the present invention mechanism refers to receive the liquid that is produced by described condenser, and the mechanism of pulse liquid working medium can be provided according to the timing relation.
The working medium of hot cylinder phase cycle engine described in the present invention 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.
Working medium conduit wall described in the present invention refers to the wall in the space that working medium can touch, and comprises unit and the communicating passage between them such as described cylinder piston mechanism, described vaporizer, described regenerator, described condenser and described timing pulse liquid mechanism.
In the present invention, described working medium passage refers to when engine work, the space that working medium stream can arrive.
Liquid storage space described in the present invention refers to store the container of liquid, storage tank for example, liquid bath etc.
In the present invention, working pressure (for example can realize by cracking pressure or the switching time of adjusting described working medium export mouth) by adjusting described working medium passage and the discharge capacity of hot junction mechanism, to control the quality discharge capacity of hot junction mechanism, make the flow mass M of the material of described internal combustion firing chamber discharge
2Flow mass M greater than the material of the described internal combustion of importing firing chamber outside described working medium passage
1That is to say except importing from described working medium passage outside the material of described internal combustion firing chamber, some material imports described internal combustion firing chamber from described working medium passage, because described internal combustion firing chamber is arranged in described working medium passage, so that is to say that the material of discharging from described internal combustion firing chamber has at least a part to flow back to described internal combustion firing chamber, having realized namely that working medium has back and forth between hot junction mechanism and cold junction mechanism flows.Can be oxygenant, reducing agent, pressurized gas or high-temperature fuel gas etc. from the material of the export-oriented described internal combustion of described working medium passage firing chamber importing.
In the present invention, described hot junction mechanism refers to that described internal combustion firing chamber is located at wherein, at first the working medium that perhaps occurs to produce after the combustion chemistry reaction in described internal combustion firing chamber enter distribution device or acting mechanism wherein, mechanisms such as cylinder piston mechanism or lobed rotor motor.
In the present invention, described cold junction mechanism refers to the timing pulse liquid mechanism of working medium from entering after described hot junction mechanism flows out.
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 hot 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.
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 19.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 19, 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 20.According to mathematical analysis, and as shown in figure 20, 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 21, 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 21, 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.
When 5, 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.
When 6, 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.
9, 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?rejection?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?innection?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?ingection?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 structural representation of the embodiment of the present invention 10;
Shown in Figure 11 is the structural representation of the embodiment of the present invention 11;
Shown in Figure 12 is the structural representation of the embodiment of the present invention 12;
Shown in Figure 13 is the structural representation of the embodiment of the present invention 13;
Shown in Figure 14 is the structural representation of the embodiment of the present invention 14;
Shown in Figure 15 is the structural representation of the embodiment of the present invention 15;
Shown in Figure 16 is the structural representation of the embodiment of the present invention 16;
Shown in Figure 17 is the structural representation of the embodiment of the present invention 17;
Shown in Figure 180 is the structural representation of the embodiment of the present invention 18;
Shown in Figure 19 is the out-of-phase diagram of Carnot's cycle and Otto cycle, wherein, and 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 20 is the out-of-phase diagram of many different adiabatic process curves, wherein, and 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 21 is the out-of-phase diagram of adiabatic process curve, and wherein, C is constant, and k is adiabatic index, and A and B are state points,
in figure: 1 cylinder piston mechanism, 2 timing pulse liquid mechanisms, 3 vaporizers, 4 condensers, 41 attached coolers, 5 regenerators, 50 heat exchanger type regenerators, 51 material filling type regenerators, 301 internal combustion firing chambers, 3001 working medium export mouths, 302 external combustion heat exchangers, 303 residual heat exchangers, 304 solar energy heat exchangers, 22 piston type liquid reciprocators, 202 timing liquor pumps, 201 liquid storage spaces, 203 liquor pumps, 204 timing control valves, 600 gas working medium timing control valves, 100 turbo-power mechanisms, 200 impeller gas compressors, 3002 attached working medium export mouths, 3003 oxidizer sources, 3004 reducing agent sources, 3005 oxygenant control valves, 3006 oxygenant sensors, 3007 oxygenant control gear, 101 gas-liquid cylinders, 102 gas-liquid isolating structures, 96 hydraulic power mechanisms, 97 liquid working substance send-back systems, 99 process control mechanisms, 5001 connecting ports.
Embodiment
Hot cylinder phase cycle engine as shown in Figure 1, comprise cylinder piston mechanism 1, vaporizer 3 and condenser 4, the cylinder of described cylinder piston mechanism 1 is communicated with described condenser 4, described condenser 4 is communicated with timing pulse liquid mechanism 2, and described vaporizer 3 is arranged on communicating passage between described condenser 4 and described cylinder piston mechanism 1.
the working procedure of the present embodiment: make overheated and/or criticalization of liquid working substance generating gasification in described vaporizer 3, intrasystem pressure is increased, the piston that the high temperature and high pressure gas working medium that produces promotes in described cylinder piston mechanism 1 moves and externally acting to lower dead center, enter described condenser 4 after in described piston is crossed the process of the continuous convergence top dead center of lower dead center, gas working medium directly being lowered the temperature, and interior liquefaction of described condenser 4, liquid working substance after liquefaction is collected by described timing pulse liquid mechanism 2, in the time of near described piston is in top dead center, described timing pulse liquid mechanism 2 directly turns back to liquid working substance described vaporizer 3, enter next circulation external outputting power that goes round and begins again.
Selectively, described vaporizer 3 is arranged in described cylinder piston mechanism 1.
hot cylinder phase cycle engine as shown in Figure 2, itself and embodiment's 1 difference are: establish regenerator 5 on the passage between described vaporizer 3 and described condenser 4, purpose is to cross in the process of the continuous convergence top dead center of lower dead center at described piston, make the heat of High Temperature High Pressure working medium leave described regenerator 5 for, enter described timing pulse liquid mechanism 2 by described condenser 4 more at last, in the time of near described piston is in top dead center, liquid working substance in described timing pulse liquid mechanism 2 turns back in described vaporizer 3 through described regenerator 5 heat absorptions again, a work cycle is completed, effectively improved the efficient of hot cylinder phase cycle engine.
Hot cylinder phase cycle engine as shown in Figure 3, itself and embodiment's 2 differences are: described vaporizer 3 is made as internal combustion firing chamber 301, establishes working medium export mouth 3001 on the working medium conduit wall; Described working medium export mouth 3001 is arranged on communicating passage between described condenser 4 and described regenerator 5.
Selectively, described working medium export mouth 3001 is arranged in described timing pulse liquid mechanism 2.
Hot cylinder phase cycle engine as shown in Figure 4, itself and embodiment's 2 differences are: described vaporizer 3 is made as and take the external combustion firing chamber as the external combustion heat exchanger 302 of thermal source.
Hot cylinder phase cycle engine as shown in Figure 5, itself and embodiment's 2 differences are: described vaporizer 3 is made as the residual heat exchanger 303 take waste heat as thermal source.
Embodiment 6
Hot cylinder phase cycle engine as shown in Figure 6, itself and embodiment's 2 differences are: described vaporizer 3 is made as the solar energy heat exchanger 304 take solar energy as thermal source.
Embodiment 7
hot cylinder phase cycle engine as shown in Figure 7, itself and embodiment 2 differences are: described timing pulse liquid mechanism 2 is made as piston type liquid reciprocator 22, the piston of described piston type liquid reciprocator 22 and the piston of described cylinder piston mechanism 1 are by the interlock of timing relation, working medium is overheated and/or criticalization in the interior generating gasification of described vaporizer 3, intrasystem pressure is increased, the descent of piston that promotes in described cylinder piston mechanism 1 externally does work, in crossing the process of the continuous convergence top dead center of lower dead center, described piston make working medium enter described condenser 4 after described regenerator 5 is lowered the temperature, and interior liquefaction of described condenser 4, liquid working substance after liquefaction is collected by described piston type liquid reciprocator 22, in the time of near described piston is in top dead center, described piston type liquid reciprocator 22 sends into described regenerator 5 with liquid working substance through endothermic process, after further absorbing heat intensification or heat absorption phase transformation, described regenerator 5 enters described vaporizer 3 again, enter next circulation external outputting power that goes round and begins again.
Hot cylinder phase cycle engine as shown in Figure 8, itself and embodiment 1 difference is: described timing pulse liquid mechanism 2 is made as timing liquor pump 202, shown in the entrance of timing liquor pump 202 be communicated with described condenser 4, the outlet of described timing liquor pump 202 is communicated with described vaporizer 3.
In the present embodiment, during the working medium after interior liquefaction of described condenser 4 sends back to described vaporizer 3 through described timing liquor pump 202.
Embodiment 9
Hot cylinder phase cycle engine as shown in Figure 9, itself and embodiment's 8 differences are: establish regenerator 5 on the passage between described vaporizer 3 and described condenser 4, the outlet of described timing liquor pump 202 is communicated with described vaporizer 3 through described regenerator 5.
Embodiment 10
Hot cylinder phase cycle engine as shown in figure 10, itself and embodiment's 9 differences are: described regenerator 5 is made as heat exchanger type regenerator 50, the liquid outlet of described timing liquor pump 202 is communicated with the entrance that is heated the fluid passage of described heat exchanger type regenerator 50, and the outlet that is heated the fluid passage of described heat exchanger type regenerator 50 is communicated with described vaporizer 3.
Embodiment 11
Hot cylinder phase cycle engine as shown in figure 11, itself and embodiment's 10 differences are: establish liquid storage space 201 on the passage between described timing liquor pump 202 and described condenser 4.
Embodiment 12
hot cylinder phase cycle engine as shown in figure 12, itself and embodiment 10 differences are: described timing pulse liquid mechanism 2 is made as by liquor pump 203, heat exchanger type regenerator 50 and timing control valve 204 consist of, the entrance of described liquor pump 203 is communicated with described condenser 4, the outlet of described liquor pump 203 is communicated with the entrance that is heated the fluid passage of described heat exchanger type regenerator 50, the outlet that is heated the fluid passage of described heat exchanger type regenerator 50 is communicated with described timing control valve 204, described timing control valve 204 is communicated with described vaporizer 3, the zone of heat liberation that adds of described heat exchanger type regenerator 50 arranges on communicating passage between described vaporizer 3 and described condenser 4.
Embodiment 13
Hot cylinder phase cycle engine as shown in figure 13, itself and embodiment's 12 differences are: described liquor pump 203 is made as liquid piston mechanism.
Embodiment 14
Hot cylinder phase cycle engine as shown in figure 14, itself and embodiment's 9 differences are: described timing pulse liquid mechanism 2 is made as by liquor pump 203 and timing control valve 204 and consists of; Described regenerator 5 is made as material filling type regenerator 51; Establish gas working medium timing control valve 600 on the passage between described material filling type regenerator 51 and described condenser 4.
Embodiment 15
Hot cylinder phase cycle engine, be with embodiment's 14 differences: described timing liquor pump 202 replacement liquor pumps 203 and 204 uses of described timing control valve as shown in figure 15.
Embodiment 16
Hot cylinder phase cycle engine as shown in figure 16, be with embodiment 3 difference: described hot cylinder phase cycle engine also comprises turbo-power mechanism 100 and impeller gas compressor 200, described working medium export mouth 3001 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 41, and the sender property outlet of described impeller gas compressor 200 and described cooler 4 are communicated with communicating passage between described regenerator 5; 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 passage between the working medium entrance of described attached cooler 41 and described impeller gas compressor 200.Selectively, described attached working medium export mouth 3002 is located on the sender property outlet and the passage between described attached cooler 41 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 3001 are located at the diverse location on described working medium passage.
Embodiment 17
hot cylinder phase cycle engine as shown in figure 17, be with embodiment 16 difference: described hot cylinder phase cycle engine comprises oxidizer source 3003, reducing agent source 3004, oxygenant sensor 3006 and oxygenant control gear 3007, described oxygenant sensor 3006 is located in described working medium passage, described reducing agent source 3004 and described working medium channel connection, 3006 pairs of described oxygenant control gear 3007 of described oxygenant sensor provide signal, described oxidizer source 3003 is subjected to described oxygenant control gear 3007 to control to realize adjusting to enter the amount of the oxygenant of described internal combustion firing chamber 301.Described attached working medium export mouth 3002 is located on the sender property outlet and the passage between described attached cooler 41 of described turbo-power mechanism 100.
Embodiment 18
Hot cylinder phase cycle engine as shown in figure 18, itself and embodiment's 10 difference is: described cylinder piston 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.
Inertial force sum when the gas working medium in described gas-liquid cylinder 101 moves reciprocatingly greater than the liquid in described gas-liquid cylinder 101 and described gas-liquid isolating structure 102 to the pressure of described gas-liquid isolating structure 102.
In the embodiment who is provided with internal combustion firing chamber 301, the mass flow rate of the material that discharge described internal combustion firing chamber 301 is greater than the mass flow rate from the material of the described internal combustion of outer importing firing chamber, described working medium loop 301.
Selectively, the working medium of described hot cylinder phase cycle engine is made as water or is made as organic substance.
Selectively, all can establish gas working medium timing control valve 600 on the passage between described vaporizer 3 and described condenser 4.
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. hot cylinder phase cycle engine, comprise cylinder piston mechanism (1), vaporizer (3) and condenser (4), it is characterized in that: the cylinder of described cylinder piston mechanism (1) is communicated with described condenser (4), described condenser (4) is communicated with timing pulse liquid mechanism (2), and described vaporizer (3) is arranged in described cylinder piston mechanism (1) and/or is arranged on communicating passage between described condenser (4) and described cylinder piston mechanism (1).
2. hot cylinder phase cycle engine as claimed in claim 1, it is characterized in that: described vaporizer (3) is made as internal combustion firing chamber (301), establishes working medium export mouth (3001) on the working medium conduit wall.
3. hot cylinder phase cycle engine as claimed in claim 2, it is characterized in that: establish regenerator (5) on the communicating passage between described vaporizer (3) and described condenser (4), described working medium export mouth (3001) is arranged on communicating passage between described condenser (4) and described regenerator (5), or is arranged in described timing pulse liquid mechanism (2).
4. hot cylinder phase cycle engine as claimed in claim 1 is characterized in that: described vaporizer (3) is made as and take the external combustion firing chamber as the external combustion heat exchanger (302) of thermal source.
5. hot cylinder phase cycle engine as claimed in claim 1, it is characterized in that: described vaporizer (3) is made as the residual heat exchanger (303) take waste heat as thermal source.
6. hot cylinder phase cycle engine as claimed in claim 1, it is characterized in that: described vaporizer (3) is made as the solar energy heat exchanger (304) take solar energy as thermal source.
7. as hot cylinder phase cycle engine as described in claim 1,2,4,5 or 6, it is characterized in that: establish regenerator (5) on the communicating passage between described vaporizer (3) and described condenser (4).
8. hot cylinder phase cycle engine as claimed in claim 7, it is characterized in that: described regenerator (5) is made as material filling type regenerator (51).
9. as hot cylinder phase cycle engine as described in claim 1,2,4,5 or 6, it is characterized in that: described timing pulse liquid mechanism (2) is made as piston type liquid reciprocator (22), and the piston of the piston of described piston type liquid reciprocator (22) and described cylinder piston mechanism (1) is by the interlock of timing relation.
10. as hot cylinder phase cycle engine as described in claim 1,2,4,5 or 6, it is characterized in that: described timing pulse liquid mechanism (2) is made as timing liquor pump (202), the entrance of described timing liquor pump (202) is communicated with described condenser (4), and the outlet of described timing liquor pump (202) is communicated with described vaporizer (3).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
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| CN2013100392751A CN103147878A (en) | 2012-02-11 | 2013-01-31 | Phase cycling engine for hot cylinder |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201210030600.3 | 2012-02-11 | ||
| CN201210030600 | 2012-02-11 | ||
| CN201210031878.2 | 2012-02-13 | ||
| CN201210031878 | 2012-02-13 | ||
| CN201210033186 | 2012-02-14 | ||
| CN201210033186.1 | 2012-02-14 | ||
| CN201210129915.3 | 2012-04-27 | ||
| CN201210129915 | 2012-04-27 | ||
| CN201210180550.7 | 2012-06-01 | ||
| CN201210180550 | 2012-06-01 | ||
| CN201210204087 | 2012-06-16 | ||
| CN201210204087.5 | 2012-06-16 | ||
| CN201210213329.7 | 2012-06-22 | ||
| CN201210213329 | 2012-06-22 | ||
| CN201210217969.5 | 2012-06-27 | ||
| CN201210217969 | 2012-06-27 | ||
| CN201210233061 | 2012-07-05 | ||
| CN201210233061.3 | 2012-07-05 | ||
| CN201210300069.7 | 2012-08-21 | ||
| CN201210300069 | 2012-08-21 | ||
| CN2013100392751A CN103147878A (en) | 2012-02-11 | 2013-01-31 | Phase cycling engine for hot cylinder |
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| CN103147878A true CN103147878A (en) | 2013-06-12 |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106523182A (en) * | 2016-05-11 | 2017-03-22 | 刘良存 | External combustion type liquid engine |
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Application publication date: 20130612 |