CN103104371A - Three-type-gate hot air engine - Google Patents
Three-type-gate hot air engine Download PDFInfo
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- CN103104371A CN103104371A CN2013100299894A CN201310029989A CN103104371A CN 103104371 A CN103104371 A CN 103104371A CN 2013100299894 A CN2013100299894 A CN 2013100299894A CN 201310029989 A CN201310029989 A CN 201310029989A CN 103104371 A CN103104371 A CN 103104371A
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Abstract
The invention discloses a three-type-gate hot air engine which comprises an air cylinder piston mechanism and an auxiliary air cylinder piston mechanism. An air inlet and an air exhaust opening are formed in an air cylinder of the air cylinder piston mechanism. An air inlet gate is arranged on the position of the air inlet. An air exhaust gate is arranged on the position of the air exhaust opening. A combustion chamber is arranged in the air cylinder piston mechanism. A reciprocating circulating opening is arranged on the air cylinder of the air cylinder piston mechanism. A reciprocating circulating control gate is arranged on the position of the reciprocating circulating opening. An auxiliary reciprocating circulating opening and an exhaust gas discharging opening are formed in an air cylinder of the auxiliary air cylinder piston mechanism. An auxiliary reciprocating circulating control gate is arranged on the position of the auxiliary reciprocating circulating opening. An exhaust gas gate is arranged on the position of the exhaust gas discharging opening. According to the three-type-gate hot air engine, circulation of an internal combustion engine and circulation of a hot-air engine are combined, exhaust gas of the internal combustion engine is used as circulation working media of the hot-air engine, further using of waste heat in the exhaust gas of the internal combustion engine is achieved, and heat efficiency of the engine is effectively improved.
Description
Technical field
The invention belongs to heat power field, particularly a kind of hot-air engine.
Background technique
In recent years, the high energy consumption of traditional combustion engine, high pollution emission problem day show outstanding, so, heat engine has obtained extensive attention, yet heat engine all heats working medium with the external combustion mode of heating, and well-known, external combustion heating process is difficult to obtain the higher working medium of temperature, therefore, cause a large amount of chemistry
Loss.Moreover, because the speed of external combustion heating is limited, high to material requirements, load responding is poor, so seriously restricted single-machine capacity and the complete machine specific power of heat engine, finally makes the purposes of heat engine seriously limited.Therefore, need a kind of new work engine of invention.
Summary of the invention
In order to solve above-mentioned problems of the prior art, the technological scheme that the present invention proposes is as follows:
scheme 1: a kind of three class door hot-air engines, comprise cylinder piston mechanism and attached cylinder piston mechanism, the cylinder of described cylinder piston mechanism is provided with suction port and relief opening, described suction port place establishes intake valve, described exhaust ports is established exhaust valve, be provided with the firing chamber in described cylinder piston mechanism, establish the reversing current port on the cylinder of described cylinder piston mechanism, described reversing current passage port is established reciprocal circulation control gate, establish attached reversing current port and weary gas exhaust port on the cylinder of described attached cylinder piston mechanism, described attached reversing current passage port is established attached reciprocal circulation control gate, described weary gas exhaust port place establishes weary valve, described reversing current port is communicated with described attached reversing current port through reciprocal communicating passage, described cylinder piston mechanism, described attached cylinder piston mechanism and described reciprocal communicating passage consist of the working medium loop.
Scheme 2: on the basis of scheme 1, establish regenerator on described reciprocal communicating passage.
Scheme 3: on the basis of scheme 1, establishing cooler on described reciprocal communicating passage and/or on described attached cylinder piston mechanism.
Scheme 4: on the basis of scheme 3, establish regenerator on the described reciprocal communicating passage between described cooler and described reversing current port.
scheme 5: a kind of three class door hot-air engines, comprise cylinder piston mechanism and attached cylinder piston mechanism, the cylinder of described cylinder piston mechanism is provided with suction port and relief opening, described suction port place establishes intake valve, described exhaust ports is established exhaust valve, establish the reversing current port on the cylinder of described cylinder piston mechanism, described reversing current passage port is established reciprocal circulation control gate, establish attached reversing current port and weary gas exhaust port on the cylinder of described attached cylinder piston mechanism, described attached reversing current passage port is established attached reciprocal circulation control gate, described weary gas exhaust port place establishes weary valve, described reversing current port is communicated with described attached reversing current port through reciprocal communicating passage, establish the firing chamber in described cylinder piston mechanism and in described reciprocal communicating passage, described cylinder piston mechanism, described attached cylinder piston mechanism and described reciprocal communicating passage consist of the working medium loop.
Scheme 6: on the basis of scheme 5, establish regenerator on the described reciprocal communicating passage between the firing chamber in described reciprocal communicating passage and described attached reversing current port.
Scheme 7: on the basis of scheme 5, on the described reciprocal communicating passage between the firing chamber in described reciprocal communicating passage and described attached reversing current port and/or establish cooler on described attached cylinder piston mechanism.
Scheme 8: on the basis of scheme 7, establish regenerator on the described reciprocal communicating passage between described cooler and described reversing current port.
Scheme 9: on the basis of scheme 1 or 5, described cylinder piston mechanism and/or described attached cylinder piston mechanism are 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 10: on the basis of scheme 9, 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.
Scheme 11: on the basis of scheme 1 or 5, the mass flow rate of the material that discharge described firing chamber is greater than the mass flow rate from the material of the described firing chamber of outer importing, described working medium loop.
Scheme 12: on the basis of scheme 1 or 5, there are the work phase difference in the piston of described cylinder piston mechanism and the piston of described attached cylinder piston mechanism.
Scheme 13: on the basis of scheme 1 or 5, described cylinder piston mechanism and the coaxial setting of described attached cylinder piston mechanism.
Scheme 14: on the basis of scheme 1 or 5, described cylinder piston mechanism and/or described attached cylinder piston mechanism are made as opposed cylinder piston mechanism.
Scheme 15: on the basis of scheme 1 or 5, described cylinder piston mechanism and described attached cylinder piston mechanism are α type or the setting of β type.
Principle of the present invention is: in described firing chamber only is located at mechanism in described cylinder piston mechanism, described cylinder piston mechanism is at first with the internal combustion engine periodic duty, in the combustion explosion expansion stroke, import in described attached cylinder piston mechanism by the working medium of described reversing current port with the part High Temperature High Pressure, the piston that remaining working medium promotes described cylinder piston mechanism externally does work, and is discharged by described relief opening when exhaust stroke.Importing working medium in described attached cylinder piston mechanism passes at reversing current between the cylinder of the cylinder of described cylinder piston mechanism and described attached cylinder piston mechanism through described reciprocal communicating passage and discharges from described relief opening and/or described weary gas exhaust port after once less.Working medium in described reciprocal communicating passage back and forth during circulation, be the equal of will be in exhaust stroke the described cylinder piston mechanism of internal-combustion engine as the hot cylinder of Stirling engine, described attached cylinder piston mechanism is as the cooling cylinder of Stirling engine; Thereby circulation and the heat engine circulation of internal-combustion engine are combined, and wherein, the working medium of heat engine circulation is the High Temperature High Pressure working medium that directly produces through the internal combustion burning, can significantly improve like this thermal efficiency and the power of system.
be equipped with in the structure of firing chamber in described cylinder piston mechanism He in described reciprocal communicating passage, described cylinder piston mechanism is at first with the internal combustion engine periodic duty, after through suction stroke and compression stroke, by described reversing current port, the part high-pressure working medium is imported described firing chamber in described reciprocal communicating passage, and the described firing chamber internal combustion in described reciprocal communicating passage, resulting High Temperature High Pressure working medium after work cycle in described reciprocal communicating passage reversing current pass to and few once discharge from described relief opening and/or described weary gas exhaust port afterwards.The interior high-pressure working medium of cylinder that is deposited in described cylinder piston mechanism after described cylinder piston mechanism compression stroke is exploded in described cylinder piston mechanism internal combustion, the piston that promotes described cylinder piston mechanism externally does work, and is discharged by described relief opening when exhaust stroke.
In the present invention, the space that the working medium that described working medium loop refers to by described cylinder piston mechanism, described attached cylinder piston mechanism and the described reciprocal communicating passage both consists of can circulate.
In the present invention, the fuel of the burning of blasting in described cylinder piston mechanism 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 enter described firing chamber with the mode that sprays into after liquid or atmospheric carbon dioxide fluidisation again.
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 devices or the mechanism connection with described working medium loop; 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 three class door hot-air engines 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 loop, 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 loop " is to flow into and/or the volume flowrate that flows out the gas working medium in described working medium loop realizes by adjustment, for example can realize by the switch gap of adjusting described weary gas port, each time of opening and/or the openings of sizes of described weary gas port.
In the present invention, working pressure (for example can realize by the switching time of adjusting described weary gas port) by adjusting described working medium loop and the discharge capacity of described cylinder piston mechanism, to control the quality discharge capacity of described cylinder piston mechanism, make the flow mass M of the material of described firing chamber discharge
2Greater than import the flow mass M of the material of described firing chamber outside described working medium loop
1That is to say except importing from described working medium loop outside the material of described firing chamber, some material imports described internal combustion firing chamber from described working medium loop, because described firing chamber is arranged in described working medium loop, so that is to say that the material of discharging from described firing chamber has at least a part to flow back to described firing chamber, namely realized working medium back and forth flowing between described cylinder piston mechanism and described attached cylinder piston mechanism.The material that imports from export-oriented described firing chamber, described working medium loop can be oxygenant, fuel or pressurized gas etc.
In the present invention, the setting of so-called two cylinder piston mechanism α types refers to the set-up mode of two cylinder piston mechanisms in α type Stirling engine, and the setting of so-called two cylinder piston mechanism β types refers to the set-up mode of two cylinder piston mechanisms in β type Stirling engine.
In the present invention, the so-called regenerator of establishing on described reciprocal communicating passage comprises that described regenerator is arranged on the structure in described reciprocal communicating passage.
In the present invention, it may be that the compression ignite mode may be also ignition combustion mode that fuel burns in described cylinder piston mechanism, if adopt the mode of ignition, also need to set up an office fiery device, for example spark plug on described cylinder piston mechanism.
in the present invention, working medium in described working medium loop need to be through overcompression, heat temperature raising boosts, acting and the process that is cooled, this just requires the described working medium loop can bearing certain pressure, optionally, the bearing capacity in described working medium loop can be made as greater than 2MPa, 2.5MPa, 3MPa, 3.5MPa, 4MPa, 4.5MPa, 5MPa, 5.5MPa, 6MPa, 6.5MPa, 7MPa, 7.5MPa, 8MPa, 8.5MPa, 9MPa, 9.5MPa, 10MPa, 10.5MPa, 11MPa, 11.5MPa, 12MPa, 12.5MPa, 13MPa, 13.5MPa, 14MPa, 14.5MPa, 15MPa, 15.5MPa, 16MPa, 16.5MPa, 17MPa, 17.5MPa, 18MPa, 18.5MPa, 19MPa, 19.5MPa, 20MPa, 20.5MPa, 21MPa, 22MPa, 23MPa, 24MPa, 25MPa, 26MPa, 27MPa, 28MPa, 29MPa, 30MPa, 31MPa, 32MPa, 33MPa, 34MPa, 35MPa, 36MPa, 37MPa, 38MPa, 39MPa or greater than 40MPa.
In the present invention, power pressure and its bearing capacity in described working medium loop are complementary, and namely the maximum pressure of the working medium in described working medium loop reaches its bearing capacity.
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 14.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 CarnotCycle shown in Figure 14, 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 15.According to mathematical analysis, and as shown in figure 15, 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 16, 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 16, 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?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?rej?ection?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.
In the present invention, should according to the known technology in motor, heat engine and heat power field, necessary parts, unit or system be set in the place of necessity.
Beneficial effect of the present invention is as follows:
three class door hot-air engines disclosed by the invention are by combining engine cycle with the heat engine circulation, embed one or more heat engine circulations in a work cycle of internal-combustion engine, utilize the part working medium in expansion stroke in engine cycle, or the part working medium after compression stroke imports the formed working medium of combustion chambers burn in described reciprocal communicating passage, cycle fluid as heat engine, thereby realized that the energy in the combustion motor exhaust further utilizes, thereby make the thermal efficiency of motor be improved, be conducive to energy saving, and simple in structure, practical, have broad application prospects.
Description of drawings
Fig. 1 is the structural representation of the described three class door hot-air engines of the embodiment of the present invention 1;
Fig. 2 is the structural representation of the described three class door hot-air engines of the embodiment of the present invention 2;
Fig. 3 is the structural representation of the described three class door hot-air engines of the embodiment of the present invention 3;
Fig. 4 is the structural representation of the described three class door hot-air engines of the embodiment of the present invention 4;
Fig. 5 is the structural representation of the described three class door hot-air engines of the embodiment of the present invention 5;
Fig. 6 is the structural representation of the described three class door hot-air engines of the embodiment of the present invention 6;
Fig. 7 is the structural representation of the described three class door hot-air engines of the embodiment of the present invention 7;
Fig. 8 is the structural representation of the described three class door hot-air engines of the embodiment of the present invention 8;
Fig. 9 is the structural representation of the described three class door hot-air engines of the embodiment of the present invention 9;
Figure 10 is the structural representation of the described three class door hot-air engines of the embodiment of the present invention 10;
Figure 11 is the structural representation of the described three class door hot-air engines of the embodiment of the present invention 11;
Figure 12 is the structural representation of the described three class door hot-air engines of the embodiment of the present invention 12;
Figure 13 is the structural representation of described opposed cylinder piston mechanism;
Shown in Figure 14 is the out-of-phase diagram of Carnot's cycle and Alto circulation, 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 the Alto circulation;
Shown in Figure 15 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 16 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 attached cylinder piston mechanisms, 11 suction ports, 12 relief openings, 13 reversing current ports, 21 attached reversing current ports, 22 weary gas exhaust ports, 3 coolers, 4 regenerators, 5 firing chambers, 96 hydraulic power mechanisms, 97 liquid send-back systems, 99 process control mechanisms, 100 reciprocal communicating passage, 111 gas-liquid cylinders, 112 gas-liquid interrupters, 113 liquid communication mouths.
Embodiment
three class door hot-air engines as shown in Figure 1, comprise cylinder piston mechanism 1 and attached cylinder piston mechanism 2, the cylinder of described cylinder piston mechanism 1 is provided with suction port 11, relief opening 12 and reversing current port 13, described suction port 11 places establish intake valve, described relief opening 12 places establish exhaust valve, described reversing current port 13 places establish reciprocal circulation control gate, be provided with firing chamber 5 in described cylinder piston mechanism 1, the cylinder of described attached cylinder piston mechanism 2 is provided with attached reversing current port 21 and weary gas exhaust port 22, described attached reversing current port 21 places establish attached reciprocal circulation control gate, described weary gas exhaust port 22 places establish weary valve, described reversing current port 13 is communicated with described attached reversing current port 21 through reciprocal communicating passage 100.
wherein, described intake valve, described exhaust valve, described reciprocal circulation control gate, described attached reciprocal circulation control gate and described weary valve controlled mechanism controls processed, make described cylinder piston mechanism 1 according to suction stroke-compression stroke-combustion explosion acting air feed stroke-exhaust stroke-recharge six-stroke circulation mode work of stroke-air feed stroke, open described reciprocal circulation control gate in described combustion explosion acting air feed stroke, the working medium of a part of High Temperature High Pressure is imported in described attached cylinder piston mechanism 2 by described reciprocal communicating passage 100, the piston that remaining High Temperature High Pressure working medium promotes described cylinder piston mechanism 1 externally does work.Requirement according to above-mentioned work cycle, the control mechanism of selecting to be fit to is controlled the piston movement in cylinder piston mechanism described in the present invention 1 and described attached cylinder piston mechanism 2, makes described attached cylinder piston mechanism 2 according to the circulation mode work corresponding with described cylinder piston mechanism 1.Air feed stroke in the six-stroke circulation mode of described cylinder piston mechanism 1-recharge stroke is corresponding to recharging stroke-air feed stroke in the work cycle of described attached cylinder piston mechanism 2, these two described working strokes consist of the heat engine circulation mode, make the described reciprocal communicating passage 100 interior reversing current of working medium between described cylinder piston mechanism 1 and described attached cylinder piston mechanism 2 pass to few once, the weary gas exhaust port from the cylinder of described attached cylinder piston mechanism 2 is discharged at last.Selectively, the working medium that passes to after lacking once at the interior reversing current of described reciprocal communicating passage 100 also can be discharged from described relief opening.
Can embed as required a plurality of this kind heat engine circulations in the work cycle of described cylinder piston mechanism 1 and described attached cylinder piston mechanism 2.
In the present embodiment, the bearing capacity in described working medium loop can be made as greater than 2MPa.
Three class door hot-air engines as shown in Figure 2 are on embodiment 1 basis: establish regenerator 4 on described reciprocal communicating passage 100.
In the present embodiment, open described exhaust valve in the compression stroke of described cylinder piston mechanism 1 after suction stroke and discharge a part of working medium, that like this can realize described cylinder piston mechanism 1 does not wait stroke work, be equivalent to piston stroke in expansion stroke greater than the motor of the piston stroke in aspirating stroke, realized that the acting allowance for expansion of working medium is greater than admission space, make the working medium acting more thorough, concrete running can be with reference to miller cycle engine.
In the present embodiment, the bearing capacity in described working medium loop can be made as greater than 5MPa.
Three class door hot-air engines as shown in Figure 3 are on embodiment 1 basis: establish cooler 3 on described reciprocal communicating passage 100.
Optionally, described cooler 3 can be located on described attached cylinder piston mechanism 2.
Optionally, establishing simultaneously described cooler 3 on described reciprocal communicating passage 100 He on described attached cylinder piston mechanism 2.
Three class door hot-air engines as shown in Figure 4 are on embodiment 3 basis: also be provided with cooler 3 on described attached cylinder piston mechanism 2, establish regenerator 4 on the described reciprocal communicating passage 100 between described cooler 3 and described reversing current port 13.
Three class door hot-air engines as shown in Figure 5, itself and embodiment's 4 difference is: cancelled the cooler 3 that is located on described reciprocal communicating passage 100, coaxial and the V-shaped setting with described attached cylinder piston mechanism 2 of described cylinder piston mechanism 1, the piston of the piston of described cylinder piston mechanism 1 and described attached cylinder piston mechanism 2 is rotationally connected through the same rod journal of connecting rod and bent axle.
Embodiment 6
three class door hot-air engines as shown in Figure 6, comprise cylinder piston mechanism 1 and attached cylinder piston mechanism 2, the cylinder of described cylinder piston mechanism 1 is provided with suction port 11 and relief opening 12, described suction port 11 places establish intake valve, described relief opening 12 places establish on the cylinder of the described cylinder piston mechanism 1 of exhaust valve and establish reversing current port 13, described reversing current port 13 places establish reciprocal circulation control gate, the cylinder of described attached cylinder piston mechanism 2 is provided with attached reversing current port 21 and weary gas exhaust port 22, described attached reversing current port 21 places establish attached reciprocal circulation control gate, described weary gas exhaust port 22 places establish weary valve, described reversing current port 13 is communicated with described attached reversing current port 21 through reciprocal communicating passage 100, establish firing chamber 5 in described cylinder piston mechanism 1 with in described reciprocal communicating passage 100, described cylinder piston mechanism 1, described attached cylinder piston mechanism 2 and described reciprocal communicating passage 100 consists of the working medium loop.
wherein, described intake valve, described exhaust valve, described reciprocal circulation control gate, described attached reciprocal circulation control gate and described weary valve controlled mechanism controls processed, make described cylinder piston mechanism 1 according to suction stroke-compression air feed stroke-combustion explosion expansion stroke-exhaust stroke-recharge six-stroke circulation mode work of stroke-air feed stroke, open described reciprocal circulation control gate when described compression air feed stroke, make the working medium of a part of high pressure by in the firing chamber 5 in the described reciprocal communicating passage 100 described reversing current circulation passage 100 of importing, and enter in described attached cylinder piston mechanism 2 after burning expansion in this firing chamber 5, remaining part is deposited in high-pressure working medium in the cylinder of described cylinder piston mechanism 1 in described cylinder piston mechanism 1 internal combustion blast, and the piston that promotes described cylinder piston mechanism 1 externally does work, and when exhaust stroke by described relief opening discharge.
Requirement according to above-mentioned work cycle, the control mechanism of selecting to be fit to is controlled the piston movement in cylinder piston mechanism described in the present invention 1 and described attached cylinder piston mechanism 2, makes described attached cylinder piston mechanism 2 according to the circulation mode work corresponding with described cylinder piston mechanism 1.air feed stroke in the six-stroke circulation mode of described cylinder piston mechanism 1-recharge stroke is corresponding to recharging stroke-air feed stroke in the work cycle of described attached cylinder piston mechanism 2, these two described working strokes consist of the heat engine circulation mode, the described reciprocal communicating passage 100 interior reversing current of High Temperature High Pressure working medium between described cylinder piston mechanism 1 and described attached cylinder piston mechanism 2 that in firing chamber 5 in described reciprocal communicating passage 100, burning produces passed to less once, weary gas exhaust port from the cylinder of described attached cylinder piston mechanism 2 22 is discharged at last.Selectively, passing to few working medium once at the interior reversing current of described reciprocal communicating passage 100 also can discharge from described relief opening 12.
Can embed as required a plurality of this kind heat engine circulations in the work cycle of described cylinder piston mechanism 1 and described attached cylinder piston mechanism 2.
Embodiment 7
Three class door hot-air engines as shown in Figure 7 are on embodiment 6 basis: establish regenerator 4 on described reciprocal communicating passage 100.
Embodiment 8
Three class door hot-air engines as shown in Figure 8 are on embodiment 6 basis: establish cooler 3 on described reciprocal communicating passage 100.
Embodiment 9
Three class door hot-air engines as shown in Figure 9 are on embodiment 8 basis: also be provided with cooler 3 on described attached cylinder piston mechanism 2, establish regenerator 4 on the described reciprocal communicating passage 100 between described cooler 3 and described reversing current port 13.
Three class door hot-air engines as shown in figure 10, itself and embodiment's 9 difference is: cancelled the cooler 3 that is located on described reciprocal communicating passage 100, coaxial and the V-shaped setting with described attached cylinder piston mechanism 2 of described cylinder piston mechanism 1, the piston of the piston of described cylinder piston mechanism 1 and described attached cylinder piston mechanism 2 is rotationally connected through the same rod journal of connecting rod and bent axle.
three class door hot-air engines as shown in figure 11, itself and embodiment's 4 difference is: cancelled the cooler 3 that is located on described attached cylinder piston mechanism 2, described cylinder piston mechanism 1 is made as piston liquid mechanism, described piston liquid mechanism comprises gas-liquid cylinder 111 and gas-liquid interrupter 112, described gas-liquid isolating structure 112 is located in described gas-liquid cylinder 111, the liquid communication mouth 113 of the liquid end of described gas-liquid cylinder 111 is communicated with hydraulic power mechanism 96, described hydraulic power mechanism 96 is communicated with liquid send-back system 97, described liquid send-back system 97 is communicated with the liquid communication mouth 113 of the liquid end of described gas-liquid cylinder 111, described hydraulic power mechanism 96 and described liquid send-back system 97 are controlled by process control mechanism 99.
Inertial force sum when the gas working medium in described gas-liquid cylinder 111 moves reciprocatingly greater than the liquid in described gas-liquid cylinder 111 and described gas-liquid isolating structure 112 to the pressure of described gas-liquid isolating structure 112.
Optionally, described gas-liquid isolating structure 112 can be made as platy structure, membrane structure or piston-like structure etc.Preferably, described gas-liquid isolating structure 112 and described gas-liquid cylinder 111 sealed sliding are movingly.
Selectively, described attached cylinder piston mechanism 2 is made as piston liquid mechanism, or described cylinder piston mechanism 1 and described attached cylinder piston mechanism 2 all are made as piston liquid mechanism.
Three class door hot-air engines as shown in figure 12, itself and embodiment's 9 difference is: described cylinder piston mechanism 1 is made as piston liquid mechanism, described piston liquid mechanism comprises gas-liquid cylinder 111 and gas-liquid interrupter 112, described gas-liquid isolating structure 112 is located in described gas-liquid cylinder 111, the liquid communication mouth 113 of the liquid end of described gas-liquid cylinder 111 is communicated with hydraulic power mechanism 96, described hydraulic power mechanism 96 is communicated with liquid send-back system 97, and described liquid send-back system 97 is communicated with the liquid communication mouth 113 of the liquid end of described gas-liquid cylinder 111; Described hydraulic power mechanism 96 and described liquid send-back system 97 are controlled by process control mechanism 99.
Inertial force sum when the gas working medium in described gas-liquid cylinder 111 moves reciprocatingly greater than the liquid in described gas-liquid cylinder 111 and described gas-liquid isolating structure 112 to the pressure of described gas-liquid isolating structure 112.
Optionally, described gas-liquid isolating structure 112 can be made as platy structure, membrane structure or piston-like structure etc.Preferably, described gas-liquid isolating structure 112 and described gas-liquid cylinder 111 sealed sliding are movingly.
Selectively, described attached cylinder piston mechanism 2 is made as piston liquid mechanism, or described cylinder piston mechanism 1 and described attached cylinder piston mechanism 2 all are made as piston liquid mechanism.
In above embodiment, the mass flow rate of the material that discharge described firing chamber 5 is greater than the mass flow rate from the material of the described firing chamber 5 of outer importing, described working medium loop.
In above embodiment, described cylinder piston mechanism 1 and described attached cylinder piston mechanism 2 are that α type or β type arrange.
Optionally, the cylinder piston mechanism 1 in above embodiment and/or described attached cylinder piston mechanism 2 can be made as opposed cylinder piston mechanism as shown in figure 13.
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. class door hot-air engine, comprise cylinder piston mechanism (1) and attached cylinder piston mechanism (2), the cylinder of described cylinder piston mechanism (1) is provided with suction port (11) and relief opening (12), described suction port (11) locates to establish intake valve, described relief opening (12) locates to establish exhaust valve, be provided with firing chamber (5) in described cylinder piston mechanism (1), it is characterized in that: establish reversing current port (13) on the cylinder of described cylinder piston mechanism (1), described reversing current port (13) locates to establish reciprocal circulation control gate, establish attached reversing current port (21) and weary gas exhaust port (22) on the cylinder of described attached cylinder piston mechanism (2), described attached reversing current port (21) locates to establish attached reciprocal circulation control gate, described weary gas exhaust port (22) locates to establish weary valve, described reversing current port (13) is communicated with described attached reversing current port (21) through reciprocal communicating passage (100), described cylinder piston mechanism (1), described attached cylinder piston mechanism (2) and described reciprocal communicating passage (100) consist of the working medium loop.
2. three class door hot-air engines as claimed in claim 1, is characterized in that: establish regenerator (4) on described reciprocal communicating passage (100).
3. three class door hot-air engines as claimed in claim 1 is characterized in that: upper and/or establish cooler (3) on described attached cylinder piston mechanism (2) in described reciprocal communicating passage (100).
4. three class door hot-air engines as claimed in claim 3, is characterized in that: establish regenerator (4) on the described reciprocal communicating passage (100) between described cooler (3) and described reversing current port (13).
5. class door hot-air engine, comprise cylinder piston mechanism (1) and attached cylinder piston mechanism (2), the cylinder of described cylinder piston mechanism (1) is provided with suction port (11) and relief opening (12), described suction port (11) locates to establish intake valve, described relief opening (12) locates to establish exhaust valve, it is characterized in that: establish reversing current port (13) on the cylinder of described cylinder piston mechanism (1), described reversing current port (13) locates to establish reciprocal circulation control gate, establish attached reversing current port (21) and weary gas exhaust port (22) on the cylinder of described attached cylinder piston mechanism (2), described attached reversing current port (21) locates to establish attached reciprocal circulation control gate, described weary gas exhaust port (22) locates to establish weary valve, described reversing current port (13) is communicated with described attached reversing current port (21) through reciprocal communicating passage (100), establish firing chamber (5) in described cylinder piston mechanism (1) and in described reciprocal communicating passage (100), described cylinder piston mechanism (1), described attached cylinder piston mechanism (2) and described reciprocal communicating passage (100) consist of the working medium loop.
6. three class door hot-air engines as claimed in claim 5, is characterized in that: establish regenerator (4) on the firing chamber (5) in described reciprocal communicating passage (100) and the described reciprocal communicating passage (100) between described attached reversing current port (21).
7. three class door hot-air engines as claimed in claim 5 is characterized in that: establish cooler (3) on the upper and/or described attached cylinder piston mechanism (2) of the firing chamber (5) in described reciprocal communicating passage (100) and the described reciprocal communicating passage (100) between described attached reversing current port (21).
8. three class door hot-air engines as claimed in claim 7, is characterized in that: establish regenerator (4) on the described reciprocal communicating passage (100) between described cooler (3) and described reversing current port (13).
9. as three class door hot-air engines as described in claim 1 or 5, it is characterized in that: described cylinder piston mechanism (1) and/or described attached cylinder piston mechanism (2) are made as piston liquid mechanism, described piston liquid mechanism comprises gas-liquid cylinder (111) and gas-liquid isolating structure (112), and described gas-liquid isolating structure (112) is located in described gas-liquid cylinder (111).
10. three class door hot-air engines as claimed in claim 9 is characterized in that: the gas working medium in described gas-liquid cylinder (111) to the pressure of described gas-liquid isolating structure (112) greater than liquid and the inertial force sum of described gas-liquid isolating structure (112) when moving reciprocatingly in described gas-liquid cylinder (111).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2013100299894A CN103104371A (en) | 2012-05-22 | 2013-01-28 | Three-type-gate hot air engine |
Applications Claiming Priority (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210160851.3 | 2012-05-22 | ||
| CN201210160851 | 2012-05-22 | ||
| CN201210167360 | 2012-05-25 | ||
| CN201210167360.1 | 2012-05-25 | ||
| CN2013100299894A CN103104371A (en) | 2012-05-22 | 2013-01-28 | Three-type-gate hot air engine |
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| CN103104371A true CN103104371A (en) | 2013-05-15 |
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| CN2013100299894A Pending CN103104371A (en) | 2012-05-22 | 2013-01-28 | Three-type-gate hot air engine |
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|---|---|---|---|---|
| US20050166869A1 (en) * | 2002-02-28 | 2005-08-04 | Nikolay Shkolnik | Liquid piston internal combustion power system |
| CN1821557A (en) * | 2005-09-12 | 2006-08-23 | 李岳 | Continuous combustion constant power engine |
| CN201560839U (en) * | 2009-08-25 | 2010-08-25 | 刘贺青 | Internal combustion stirling engine |
| WO2010115636A2 (en) * | 2009-04-09 | 2010-10-14 | Willi Fechner Gmbh | Internal combustion engine |
| JP2010285964A (en) * | 2009-06-15 | 2010-12-24 | Aritomi Okuno | Internal combustion stirling engine |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20050166869A1 (en) * | 2002-02-28 | 2005-08-04 | Nikolay Shkolnik | Liquid piston internal combustion power system |
| CN1821557A (en) * | 2005-09-12 | 2006-08-23 | 李岳 | Continuous combustion constant power engine |
| WO2010115636A2 (en) * | 2009-04-09 | 2010-10-14 | Willi Fechner Gmbh | Internal combustion engine |
| JP2010285964A (en) * | 2009-06-15 | 2010-12-24 | Aritomi Okuno | Internal combustion stirling engine |
| CN201560839U (en) * | 2009-08-25 | 2010-08-25 | 刘贺青 | Internal combustion stirling engine |
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Application publication date: 20130515 |