CN103089486A - Three-valve hot-air engine - Google Patents
Three-valve hot-air engine Download PDFInfo
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- CN103089486A CN103089486A CN2013100313942A CN201310031394A CN103089486A CN 103089486 A CN103089486 A CN 103089486A CN 2013100313942 A CN2013100313942 A CN 2013100313942A CN 201310031394 A CN201310031394 A CN 201310031394A CN 103089486 A CN103089486 A CN 103089486A
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Abstract
The invention discloses a three-valve hot-air engine, and the three-valve hot-air engine includes an air cylinder piston mechanism and a combustion chamber. An air cylinder of the air cylinder piston mechanism is provided with an air inlet. An air inlet valve is arranged at the position of the air inlet. The air cylinder of the air cylinder piston mechanism is provided with a reciprocating flow mouth which is provided with a reciprocating flow control valve. The reciprocating flow mouth is communicated with a timing pulse air mechanism through a reciprocating communicating channel. A heat regenerator is arranged on the reciprocating communicating channel. An exhaust air outlet is formed on the air cylinder of the cylinder piston mechanism, and an exhaust valve is arranged at the position of the exhaust air outlet. The combustion chamber is arranged inside the air cylinder piston mechanism. Due to the facts that the combustion motor is combined with the thermomotor, and the air exhausted from combustion motor is regarded as a circular working medium of a thermomotor, the further utility of the waste heat in the exhaust of the engine has the advantages of effectively improving thermal efficiency of the engine, and being simple in structure, strong in practicability, and broad in application prospect.
Description
Technical field
The present invention relates to heat power field, especially 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.
Traditional combustion engine is generally that high-temperature tail gas is directly emitted, and causes thermal losses serious.Yet in traditional heat engine, gas working medium needs heat to heat, conventional mode of heating is external-burning type, the utilization efficiency of fuel is also lower, therefore for the fuel utilization efficiency of existing internal-combustion engine and heat engine, need to provide a kind of can carry out the further motor of utilization to waste heat in engine exhaust.
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 three class door hot-air engines, comprise cylinder piston mechanism and firing chamber, establish suction port on the cylinder of described cylinder piston mechanism, described suction port place establishes intake 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, described reversing current port is through reciprocal communicating passage and timing pulse gas mechanism connection, establish regenerator on described reciprocal communicating passage, establishing weary gas exhaust port on the cylinder of described cylinder piston mechanism and/or on the described reciprocal communicating passage between described regenerator and described timing pulse gas mechanism, described weary gas exhaust port place establishes weary valve, described firing chamber be located in described cylinder piston mechanism and/or described reversing current port and described regenerator between described reciprocal communicating passage in, described cylinder piston mechanism, described timing pulse gas mechanism and described reciprocal communicating passage consist of the working medium loop.
Scheme 2: on the basis of scheme 1, described timing pulse gas mechanism is made as attached cylinder piston mechanism.
Scheme 3: on the basis of scheme 2, described cylinder piston mechanism and described attached cylinder piston mechanism are coaxial setting, and are the V-type layout.
Scheme 4: on the basis of scheme 2, described cylinder piston mechanism and described attached cylinder piston mechanism are α type or the setting of β type.
Scheme 5: on the basis of scheme 2, establishing cooler on described attached cylinder piston mechanism and/or on the described reciprocal communicating passage between described regenerator and described attached cylinder piston mechanism.
Scheme 6: on the basis of scheme 2, establish attached suction port and attached reversing current port on the cylinder of described attached cylinder piston mechanism, described attached suction port place establishes attached intake valve, described attached reversing current passage port is established attached reciprocal circulation control gate, and described reversing current port is through being communicated with described attached reversing current port toward described multiply-connected circulation passage.
Scheme 7: on the basis of scheme 6, described attached suction port is communicated with the pressurized gas outlet of supercharging device.
Scheme 8: on the basis of scheme 1, described timing pulse gas mechanism is made as the gas holder with timing control mechanism.
Scheme 9: on the basis of scheme 8, described regenerator is communicated with described gas holder through described timing control mechanism.
Scheme 10: on the basis of scheme 1, described timing pulse gas mechanism is made as gas compressor, and described regenerator is communicated with the pressurized gas outlet of described gas compressor.
Scheme 11: on the basis of scheme 10, the intake duct of described gas compressor is provided with supercharging device.
Scheme 12: on the basis of scheme 1, described three class door hot-air engines also comprise turbo-power mechanism and impeller gas compressor, described weary gas exhaust port 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 cooler, the sender property outlet of described impeller gas compressor and described working medium circuit communication; Passage between the sender property outlet of described turbo-power mechanism and the working medium entrance of described impeller gas compressor is provided with the working medium export mouth.
Scheme 13: on the basis of scheme 1, 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 14: on the basis of scheme 2, described attached cylinder piston mechanism is made as attached piston liquid mechanism, and described attached 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 15: on the basis of scheme 13 or 14, 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 16: on the basis of scheme 1, described three class door hot-air engines also comprise four class door cylinder piston mechanisms, the air supply opening of described four class door cylinder piston mechanisms is communicated with suction port on the cylinder of described cylinder piston mechanism, and recharging of described four class door cylinder piston mechanisms mouthful is communicated with described weary gas exhaust port.
Scheme 17: on the basis of scheme 1, 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 18: on the basis of scheme 1, described three class door hot-air engines also comprise low temperature cold source, described low temperature cold source is used for providing cryogenic substance, and described cryogenic substance is used for cooling described timing pulse gas mechanism or is about to enter the working medium of described timing pulse gas mechanism.
Scheme 19: on the basis of scheme 1, be provided with cooler on the described reciprocal communicating passage between described regenerator and described timing pulse gas mechanism.
Scheme 20: on the basis of scheme 1, be provided with cooler in described timing pulse gas mechanism.
Scheme 21: on the basis of scheme 1, a plurality of described cylinder piston mechanisms and a described timing pulse gas mechanism connection.
Scheme 22: on the basis of scheme 1, the high impulse air pressure of described timing pulse gas mechanism is greater than 0.5MPa.
Scheme 23: on the basis of scheme 7 or 11, the bearing capacity of the gas outlet of described supercharging device is greater than 0.3MPa.
Principle of the present invention is: in the structure in described firing chamber is located at described cylinder piston mechanism, described cylinder piston mechanism is first with engine cycle work, and after work cycle in will be in the described cylinder piston mechanism of exhaust stroke as the hot cylinder of heat engine, with the described timing pulse gas mechanism cooling cylinder as heat engine, carry out heat engine circulation at least one times; Thereby the circulation of internal-combustion engine and the circulation of heat engine are combined; Discharge from described weary gas exhaust port through the working medium after the heat engine circulation, complete a cycle period.
In structure in described firing chamber is located at described reciprocal communicating passage between described reversing current port and described regenerator, described cylinder piston mechanism is first as gas compressor work, pressurized gas feeds the combustion chemistry reaction occurs in described firing chamber, after work cycle described in cylinder piston mechanism as the hot cylinder of heat engine, described timing pulse gas mechanism carries out heat engine circulation at least one times as the cooling cylinder of heat engine between hot cylinder and cooling cylinder; Discharge from described weary gas exhaust port through the working medium after the heat engine circulation, complete a cycle period.
Wherein, the working medium of heat engine circulation is the high-temperature gas in the I. C. engine exhaust stroke or 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.
In the present invention, so-called weary gas exhaust port refers to described three class door hot-air engines experience with the combination circulation of engine cycle and heat engine circulation combination, and the working medium in system passes to few relief opening after once at described reversing current circulation passage reversing current.
In the present invention, the described cylinder piston mechanism in described three class door hot-air engines can be according to suction stroke-compression stroke-combustion explosion expansion stroke-air feed stroke-recharge six-stroke circulation mode work of expansion stroke-exhaust stroke.
In the present invention, when described timing pulse gas mechanism is made as attached cylinder piston mechanism, can the coaxial and V-shaped setting with the described cylinder piston mechanism that is provided with described firing chamber.
In the present invention, when described timing pulse gas mechanism is made as attached cylinder piston mechanism, can arranges in the α mode or arrange in the β mode with the described cylinder piston mechanism that is provided with described firing chamber.
In the present invention, the setting of described cooler is in order to improve the utilization ratio to heat in exhaust.
In the present invention, the setting of described supercharging device is in order to improve the pressure of described timing pulse gas mechanism.
In the present invention, so-called timing pulse gas mechanism refers to and can provide gas and can be from described cylinder piston mechanism receiver gases to described cylinder piston mechanism by the timing relation, together complete the device of [thermodynamic with described cylinder piston mechanism and correlation unit (such as regenerator etc.), such as attached cylinder piston mechanism, with the gas holder of timing control mechanism, gas compressor etc.So-called timing relation refers to that described cylinder piston mechanism and described timing pulse gas mechanism complete the logical relation of [thermodynamic.
In the present invention, the space that the working medium that described working medium loop refers to by described cylinder piston mechanism, described timing pulse gas mechanism and the communicating passage both consists of can circulate.
In the present invention, the fuel that the combustion chemistry reaction occurs in described firing chamber can be hydrocarbon, hydrocarbon oxygen compound or solid carbon.Solid carbon does not have the gas concentration lwevel in water generation and burning afterproduct high after having burning, the advantages such as easy liquefaction; Solid carbon can adopt spray into after solid assembled in advance, powdered or powdered after input 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 device 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 openings of sizes of the switch gap of adjusting described weary gas exhaust port, each time of opening and/or described weary gas exhaust port place control valve.
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 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 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 timing pulse gas 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, described low temperature cold source refers to provide the device of temperature at the cryogenic substance below 0 ℃, mechanism or storage tank, the storage tank that stores cryogenic substance that for example adopts the business buying pattern to obtain, described cryogenic substance can be liquid nitrogen, liquid oxygen, liquid helium or liquefied air etc.When oxygenant in the present invention was liquid oxygen, liquid oxygen can be directly as described cryogenic substance.
In the present invention, the mode of described low temperature cold source directly described cryogenic substance is mixed with described working medium circuit communication with the working medium in described working medium loop, perhaps making the mode of the working medium heat exchange in described cryogenic substance and described working medium loop through heat-exchanger rig, in described timing pulse gas mechanism or the working medium that is about to enter timing pulse gas mechanism carry out cooling processing.Heat engine be a kind of work cycle near the power mechanism of Carnot's cycle, the calculating of its thermal efficiency can be with reference to the Carnot cycle Thermal efficiency formula:
Therefrom as can be known, as sink temperature T
2During decline, thermal efficiency η raises, and reduces to the heat of low-temperature receiver discharging, if sink temperature T
2Decline by a big margin, namely sink temperature is very low, and thermal efficiency η is very high, and is very little to the heat of low-temperature receiver discharging.Infer thus, the cryogenic substance that usable temp is quite low makes sink temperature T
2Decline to a great extent, thereby significantly reduce to the heat of low-temperature receiver discharging, effectively improve engine efficiency.
The cryogenic substance that temperature is lower (such as liquid oxygen, liquid nitrogen or liquid helium etc.), need to consume more energy in manufacture process, but with regard to unit mass, the contribution that engine thermal efficiency η is promoted is larger, like storing the energy in the very low material of temperature, the concept that is equivalent to a kind of novel battery, described cryogenic substance can wait the very low energy of cost to make with the rubbish electricity, thereby effectively reduces the user cost of motor.
In the present invention, described four class door cylinder piston mechanisms refer to that cylinder is provided with suction port, relief opening, air supply opening and recharges mouth, described suction port, described relief opening, described air supply opening and described recharge mouthful place corresponding successively intake valve, exhaust valve are set, for valve with recharge the cylinder piston mechanism of door.
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, fuel combustion may be that ignition may be also compression ignite in described cylinder piston mechanism, if adopt the mode of ignition, also need to set up an office in described firing chamber fiery device, for example spark plug.
In the present invention, so-called coaxial referring to when described timing pulse gas mechanism is made as the device that comprises cylinder piston mechanism, described cylinder piston mechanism all is connected with the same rod journal of same bent axle with the cylinder piston mechanism of being connected in timing pulse gas mechanism, and the axis of two cylinders is made as V-type; Or referring to that two cylinders are connected with two rod journals of same bent axle out of phase, the axis angle of two cylinders is less than 90 degree.
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 28.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 28, 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 29.According to mathematical analysis, and as shown in figure 29, 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 30, 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 30, 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?heatinjection?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.Itis?impossible?to?return?a?non-adiabatic?process?to?its?initial?state?only?by?adiabatic?process.
5.If?the?final?pressure?of?heat?injection?process?is?returned?to?its?initial?pressure?by?process?other?than?heat?rejection?process,the?temperature?of?that?state?is?higher?than?that?of?the?initial?state.
6.If?the?final?pressure?of?heat?rejection?process?is?returned?to?its?initial?pressure?by?process?other?than?heat?injection?process,the?temperature?of?that?state?is?lower?than?that?of?the?initial?state.
7.It?is?impossible?to?make?heat?injection?process?not?generate?excess-temperature.
8.It?is?impossible?to?make?heat?rejection?process?not?generate?insufficient-temperature.
9.It?is?impossible?for?any?device?that?operates?on?a?cycle?to?reach?the?efficiency?indicated?by?Carnot?cycle?without?heat?rejection?in?compression?process.
10.The?difference?between?heat?injection?process?and?compression?process?which?are?applied?to?working?fluid?of?thermodynamic?process?or?cycle?is?that?heat?injection?process?must?generate?excess-temperature,but?compression?process?must?not.
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 High Temperature High Pressure working medium after I. C. engine exhaust or burning as the cycle fluid of heat engine, thereby realized the energy in engine exhaust is further utilized, compare with conventional engines, the thermal efficiency and the power of motor have been improved, be conducive to energy saving, and simple in structure, practical, have broad application prospects.
Description of drawings
Fig. 1 and 2 is the structure principle chart of three class door hot-air engines of the present invention;
Fig. 3 is the structural representation of the described three class door hot-air engines of embodiment 1;
Fig. 4 is the structural representation of the described three class door hot-air engines of embodiment 2;
Fig. 5 is the structural representation of the described three class door hot-air engines of embodiment 3;
Fig. 6 is the structural representation of the described three class door hot-air engines of embodiment 4;
Fig. 7 is the structural representation of the described three class door hot-air engines of embodiment 5;
Fig. 8 is the structural representation of the described three class door hot-air engines of embodiment 6;
Fig. 9 is the structural representation of the described three class door hot-air engines of embodiment 7;
Figure 10 is the structural representation of the described three class door hot-air engines of embodiment 8;
Figure 11 is the structural representation of the described three class door hot-air engines of embodiment 9;
Figure 12 is the structural representation of the described three class door hot-air engines of embodiment 10;
Figure 13 is the structural representation of the described three class door hot-air engines of embodiment 11;
Figure 14 is the structural representation of the described three class door hot-air engines of embodiment 12;
Figure 15 is the structural representation of the described three class door hot-air engines of embodiment 13;
Figure 16 is the structural representation of the described three class door hot-air engines of embodiment 14;
Figure 17 is the structural representation of the described three class door hot-air engines of embodiment 15;
Figure 18 is the structural representation of the described three class door hot-air engines of embodiment 16;
Figure 19 is the structural representation of the described three class door hot-air engines of embodiment 17;
Figure 20 is the structural representation of the described three class door hot-air engines of embodiment 18;
Figure 21 is the structural representation of the described three class door hot-air engines of embodiment 19;
Figure 22 is the structural representation of the described three class door hot-air engines of embodiment 20;
Figure 23 is the structural representation of the described three class door hot-air engines of embodiment 21;
Figure 24 is the structural representation of the described three class door hot-air engines of embodiment 22;
Figure 25 is the structural representation of the described three class door hot-air engines of embodiment 23;
Figure 26 is the structural representation of the described three class door hot-air engines of embodiment 24;
Figure 27 is the structural representation of opposed pistons cylinder mechanism;
Shown in Figure 28 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 29 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 30 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, 10 suction ports, 11 intake valves, 12 weary valves, 13 reversing current ports, 14 reciprocal circulation control gates, 15 weary gas exhaust ports, 16 advance row shares gas port, 17 advance to arrange shared air valve, 2 attached cylinder piston mechanisms, 20 attached suction ports, 21 attached intake valves, 22 gas compressors, 23 attached reversing current ports, 24 attached reciprocal circulation control gates, 25 coolers, 3 timing pulse gas mechanisms, 301 gas holder, 4 regenerators, 5 firing chambers, 6 timing control mechanisms, 71 turbo-power mechanisms, 72 impeller gas compressors, 73 working medium export mouths, 74 coolers, 8 low temperature cold sources, 96 hydraulic power mechanisms, 97 liquid send-back systems, 99 process control mechanisms, 111 gas-liquid cylinders, 112 gas-liquid interrupters, 113 liquid communication mouths, 200 4 class door cylinder piston mechanisms, 201 suction ports, 202 relief openings, 203 air supply openings, 204 recharge mouth.
Embodiment
Three class door hot-air engines as shown in Figure 3 comprise cylinder piston mechanism 1 and firing chamber 5, and described firing chamber 5 is located in described cylinder piston mechanism 1; Described cylinder piston mechanism 1 is provided with suction port 10, and described suction port 10 places are provided with intake valve 11, and described cylinder piston mechanism 1 is provided with reversing current port 13, and described reversing current port 13 places are provided with reciprocal circulation control gate 14; Described cylinder piston mechanism 1 is provided with weary gas exhaust port 15, described weary gas exhaust port 15 places are provided with weary valve 12, described reversing current port 13 is communicated with timing pulse gas mechanism 3 through reciprocal communicating passage 100, establish regenerator 4 on described reciprocal communicating passage 100, be equivalent to described regenerator 4 and be communicated with described reversing current port 13 through described reciprocal communicating passage 100 1 ends, the other end is communicated with timing pulse gas mechanism 3.Wherein, described timing pulse gas mechanism 3 is made as attached cylinder piston mechanism 2, and the described cylinder piston mechanism 1 of described three class door hot-air engines can be according to suction stroke-compression stroke-combustion explosion expansion stroke-air feed stroke-recharge six-stroke circulation mode work of expansion stroke-exhaust stroke.
Can after recharging expansion stroke in above-mentioned circulating working mode, can be back to the air feed stroke according to actual needs, repeat the work cycle of heat engine, enter again exhaust stroke after circulation repeatedly.
Wherein, be 0.6MPa as the high impulse air pressure in the described attached cylinder piston mechanism 2 of described timing pulse gas mechanism 3, optionally, described high impulse air pressure can be selected as required greater than 0.5MPa, 1MPa, 1.5MPa, 2MPa, 2.5MPa or greater than the arbitrary value of 3MPa.
Three class door hot-air engines as shown in Figure 4, itself and embodiment's 1 difference is: be provided with cooler 25 on the described attached cylinder piston mechanism 2 as described timing pulse gas mechanism 3, and also be provided with cooler 25 on the described reciprocal communicating passage 100 between described regenerator 4 and described attached cylinder piston mechanism 2.
Optionally, above-mentioned two coolers 25 also can only arrange any one.
Wherein, be 0.8MPa as the high impulse air pressure in the described attached cylinder piston mechanism 2 of described timing pulse gas mechanism 3.
Three class door hot-air engines as shown in Figure 5, itself and embodiment's 1 difference is: described timing pulse gas mechanism 3 is made as the gas holder 301 with timing control mechanism 6, and described regenerator 4 is communicated with described gas holder 301 through described timing control mechanism 6.Be subjected to the control of described timing control mechanism 6, described gas holder 21 is sent into gas according to the timing relation in the cylinder of described cylinder piston mechanism 1 of described three class door hot-air engines, and receive gas in the cylinder of described cylinder piston mechanism 1 by the timing relation, can be according to suction stroke-compression stroke-combustion explosion expansion stroke-air feed stroke-recharge six-stroke circulation mode work of expansion stroke-exhaust stroke to guarantee described motor.
Wherein, the high impulse air pressure in described gas holder 301 is 1MPa.
Three class door hot-air engines as shown in Figure 6, itself and embodiment's 3 difference is: described gas holder 21 is provided with cooler 25, and the described reciprocal communicating passage 100 between described regenerator 4 and described gas holder 301 is provided with weary gas exhaust port 15, and described weary gas exhaust port 15 places are provided with weary valve 12.
Wherein, the high impulse air pressure in described gas holder 301 is 1.5MPa.
Three class door hot-air engines as shown in Figure 7, itself and embodiment's 1 difference is: described attached cylinder piston mechanism 2 is provided with attached suction port 20, and described attached suction port 10 places are provided with intake valve 21; Described attached cylinder piston mechanism 2 is provided with attached reversing current port 23, and described attached reversing current port 23 places are provided with attached reciprocal circulation control gate 24, and described reversing current port 13 is communicated with described attached reversing current port 23 through described reciprocal communicating passage 100.
Wherein, the high impulse air pressure in described attached cylinder piston mechanism 2 is 1.2MPa.
Three class door hot-air engines as shown in Figure 8, its difference with embodiment 5 is: the described attached suction port 20 of described attached cylinder piston mechanism 2 is communicated with gas outlet as the impeller gas compressor 72 of supercharging device.
Wherein, the high impulse air pressure in described attached cylinder piston mechanism 2 is 1.4MPa; The bearing capacity of the gas outlet of described impeller gas compressor 72 is 0.6MPa, optionally, the bearing capacity of the gas outlet of described impeller gas compressor 72 can be selected as required greater than 0.3MPa, 0.5MPa, 0.7MPa, 0.9MPa or greater than the arbitrary value of 1MPa.
Embodiment 7
Three class door hot-air engines as shown in Figure 9, itself and embodiment's 5 difference is: the described reciprocal communicating passage 100 between described regenerator 4 and described attached cylinder piston mechanism 2 is provided with cooler 25.
Wherein, the high impulse air pressure in described attached cylinder piston mechanism 2 is 1.3MPa.
Three class door hot-air engines as shown in figure 10, itself and embodiment's 5 difference is: the described reciprocal communicating passage 100 between the described attached reversing current port 23 of described regenerator 4 and described attached cylinder piston mechanism 2 is provided with weary gas exhaust port 15, and described weary gas exhaust port 15 places are provided with weary valve 12.
Wherein, the high impulse air pressure in described attached cylinder piston mechanism 2 is 1.8MPa.
Embodiment 9
Three class door hot-air engines as shown in figure 11, its difference with embodiment 8 is: the described attached suction port 20 of described attached cylinder piston mechanism 2 is communicated with gas outlet as the impeller gas compressor 72 of supercharging device.
Wherein, the high impulse air pressure in described attached cylinder piston mechanism 2 is 2MPa; The bearing capacity of the gas outlet of described impeller gas compressor 72 is 0.8MPa.
Three class door hot-air engines as shown in figure 12, its difference with embodiment 2 is: the described reversing current port 13 of two described cylinder piston mechanisms 1 is communicated with same described attached cylinder piston mechanism 2 through described regenerator 4 and described cooler 25 respectively successively.
Wherein, the high impulse air pressure in described attached cylinder piston mechanism 2 is 2.2MPa.
Three class door hot-air engines as shown in figure 13, itself and embodiment's 5 difference is: the described suction port 10 of described cylinder piston mechanism 1 and described weary gas exhaust port 15 integrated setting share gas port 16 for advancing row, and described intake valve 11 and described weary valve 12 integrated setting are for advancing to arrange shared air valve 17.
Three class door hot-air engines as shown in figure 14, its difference with embodiment 5 is: the described reversing current port 13 of three described cylinder piston mechanisms 1 is communicated with the described attached reversing current port 23 of same described attached cylinder piston mechanism 2 through described regenerator 4 respectively, and described attached cylinder piston mechanism 2 is provided with cooler 25.
Three class door hot-air engines as shown in figure 15, itself and embodiment's 2 difference is: the coaxial and V-shaped setting of described cylinder piston mechanism 1 and described attached cylinder piston mechanism 2; Described cylinder piston mechanism 1 shown in figure and described attached cylinder piston mechanism 2 according to actual needs, also can be made as β type structure for the α type arranges.
Three class door hot-air engines as shown in figure 16, itself and embodiment's 1 difference is: cancelled the described weary gas exhaust port 15 that is arranged on described cylinder piston mechanism 1, establish described weary gas exhaust port 15 on the described reciprocal communicating passage 100 between described regenerator 4 and described attached cylinder piston mechanism 2, described weary gas exhaust port 15 places are provided with weary valve 12.
Three class door hot-air engines as shown in figure 17, itself and embodiment's 14 difference is: the described reciprocal communicating passage 100 between described regenerator 4 and described weary gas exhaust port 15 is provided with cooler 25.
Wherein, the high impulse air pressure in described attached cylinder piston mechanism 2 is 2.6MPa.
Three class door hot-air engines as shown in figure 18, itself and embodiment's 15 difference is: described timing pulse gas mechanism 3 is made as the gas compressor 22 of cylinder piston type.
Wherein, the high impulse air pressure in described gas compressor 22 is 2.3MPa.
Three class door hot-air engines as shown in figure 19, itself and embodiment's 16 difference is: the intake duct of described gas compressor 22 is provided with the impeller gas compressor 72 as supercharging device.
Wherein, the high impulse air pressure of described gas compressor 22 is 2.8MPa; The bearing capacity of the gas outlet of described impeller gas compressor 72 is 1MPa, optionally, the bearing capacity of the gas outlet of described impeller gas compressor 72 can be selected as required greater than 0.3MPa, 0.5MPa, 0.7MPa, 0.9MPa or greater than the arbitrary value of 1MPa.
Embodiment 18
Three class door hot-air engines as shown in figure 20, itself and embodiment's 11 difference is: also comprise impeller gas compressor 72 and turbo-power mechanism 71, the described row of advancing shares gas port 16 and is communicated with the gas access of the gas outlet of described impeller gas compressor 72 and described turbo-power mechanism 71 simultaneously.
Embodiment 19
Three class door hot-air engines as described in Figure 21, itself and embodiment's 1 difference is: described firing chamber 5 is arranged in described reciprocal communicating passage 100 between described reversing current port 13 and described regenerator 4, in this structure, described cylinder piston mechanism 1 portion of time is used as the hot cylinder of heat engine as gas compressor, portion of time, the discharge of also undertaking simultaneously weary gas in system.Fresh air first enters described cylinder piston mechanism 1 by described suction port 10, and the interior generation combustion chemistry reaction in the described firing chamber 5 of infeed after compression within it, enter subsequently the circulation of the heat engine that is formed by described cylinder piston mechanism 1 and described attached cylinder piston mechanism 2, after through one or more heat engine circulations, becoming weary gas is discharged by described weary gas exhaust port 15, wherein, described cylinder piston mechanism 1 is according to suction stroke-compression air feed stroke-recharge expansion stroke-air feed stroke-recharge circulation mode work of expansion stroke-exhaust stroke.
Optionally, in a work cycle of described cylinder piston mechanism 1, can comprise the process unit of a plurality of " air feed strokes-recharge expansion stroke " after recharging expansion stroke.
Three class door hot-air engines as described in Figure 22, itself and embodiment's 19 difference is: also be provided with another firing chamber 5 in described cylinder piston mechanism 1, described cylinder piston mechanism 1 is according to suction stroke-compression air feed stroke-clearance gaseous combustion expansion stroke-air feed stroke-recharge expansion stroke-air feed stroke-recharge circulation mode work of expansion stroke-exhaust stroke.
Optionally, described cylinder piston mechanism 1 also can be according to suction stroke-compression air feed stroke-clearance gaseous combustion expansion stroke-exhaust stroke-recharge expansion stroke-air feed stroke-recharge circulation mode work of expansion stroke-exhaust stroke; In a work cycle of described cylinder piston mechanism 1, can comprise the process unit of a plurality of " air feed strokes-recharge expansion stroke " after recharging expansion stroke.
Three class door hot-air engines as shown in figure 23, on embodiment 16 basis: described three class door hot-air engines also comprise turbo-power mechanism 71 and impeller gas compressor 72, described weary gas exhaust port 15 is communicated with the working medium entrance of described turbo-power mechanism 71, the sender property outlet of described turbo-power mechanism 71 is communicated with the working medium entrance of described impeller gas compressor 72 through cooler 74, the sender property outlet of described impeller gas compressor 72 and described working medium circuit communication, specifically with described cooler 25 and described regenerator 4 between described reciprocal communicating passage 100 be communicated with; Passage between described cooler 74 between described turbo-power mechanism 71 and described impeller gas compressor 72 and the working medium entrance of described impeller gas compressor 72 is provided with working medium export mouth 73.
Described working medium export mouth 73 selectively is located on the sender property outlet and the passage between described cooler 74 of described turbo-power mechanism 71.The sender property outlet of described impeller gas compressor 72 is communicated with connecting port on being located at described working medium loop, and this connecting port and described weary gas exhaust port 15 are located at the diverse location on described working medium loop.
Three class door hot-air engines as shown in figure 24, on embodiment 11 basis: described three class door hot-air engines also comprise low temperature cold source 8, described low temperature cold source 8 is the storage tanks that store liquid nitrogen, and the liquid nitrogen in storage tank is used for the working medium of cooling described attached cylinder piston mechanism 2.
In the present embodiment, described low temperature cold source 8 directly is communicated with described attached cylinder piston mechanism 2, is provided with control valve on the communicating passage between described low temperature cold source 8 and described attached cylinder piston mechanism 2.
Optionally, the working medium heat exchange that described low temperature cold source 8 can also be in heat-exchanger rig makes described cryogenic substance and described working medium loop.After described cryogenic substance performance cooling action in described low temperature cold source 8, both can import in described working medium loop, as the cycle fluid of three class door hot-air engines, also can not import in described working medium loop.
Three class door hot-air engines as shown in figure 25, itself and embodiment's 19 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.
Three class door hot-air engines as shown in figure 26, on embodiment 14 basis: described three class door hot-air engines also comprise four class door cylinder piston mechanisms 200, the suction port 201 on the cylinder of described four class door cylinder piston mechanisms 200, relief opening 202, air supply opening 203 and recharge mouthful 204 places successively correspondence intake valve, exhaust valve are set, for valve with recharge door; Suction port 10 on the cylinder of described air supply opening 203 and described cylinder piston mechanism 1 is communicated with, and describedly recharges mouthfuls 204 and is communicated with described weary gas exhaust port 15.
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.
Optionally, the above timing pulse gas mechanism 3 is made as in the embodiment of described attached cylinder piston mechanism 2, described attached cylinder piston mechanism 2 can be made as attached piston liquid mechanism, described attached 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.
Optionally, firing chamber 5 described in above embodiment all can be located on communicating passage between described reversing current port 13 and described regenerator 4 as shown in figure 21.
Optionally, the cylinder piston mechanism 1 in above embodiment all can be made as opposed cylinder piston mechanism as shown in figure 27.
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 firing chamber (5), establish suction port (10) on the cylinder of described cylinder piston mechanism (1), described suction port (10) locates to establish intake valve (11), 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 (14), described reversing current port (13) is communicated with timing pulse gas mechanism (3) through reciprocal communicating passage (100), establish regenerator (4) on described reciprocal communicating passage (100), establishing weary gas exhaust port (15) on the cylinder of described cylinder piston mechanism (1) and/or on the described reciprocal communicating passage (100) between described regenerator (4) and described timing pulse gas mechanism (3), described weary gas exhaust port (15) locates to establish weary valve (12), described firing chamber (5) be located in described cylinder piston mechanism (1) and/or described reversing current port (13) and described regenerator (4) between described reciprocal communicating passage (100) in, described cylinder piston mechanism (1), described timing pulse gas mechanism (3) and described reciprocal communicating passage (100) consist of the working medium loop.
2. three class door hot-air engines as claimed in claim 1, it is characterized in that: described timing pulse gas mechanism (3) is made as attached cylinder piston mechanism (2).
3. three class door hot-air engines as claimed in claim 2, it is characterized in that: described cylinder piston mechanism (1) and described attached cylinder piston mechanism (2) are coaxial setting, and are the V-type layout.
4. three class door hot-air engines as claimed in claim 2 is characterized in that: described cylinder piston mechanism (1) and described attached cylinder piston mechanism (2) arrange for α type or β type.
5. three class door hot-air engines as claimed in claim 2 is characterized in that: upper and/or establish cooler (25) on the described reciprocal communicating passage (100) between described regenerator (4) and described attached cylinder piston mechanism (2) at described attached cylinder piston mechanism (2).
6. three class door hot-air engines as claimed in claim 2, it is characterized in that: establish attached suction port (20) and attached reversing current port (23) on the cylinder of described attached cylinder piston mechanism (2), described attached suction port (20) locates to establish attached intake valve (21), described attached reversing current port (23) locates to establish attached reciprocal circulation control gate (24), and described reversing current port (13) is through being communicated with described attached reversing current port (23) toward described multiply-connected circulation passage (100).
7. three class door hot-air engines as claimed in claim 6, it is characterized in that: described attached suction port (20) is communicated with the pressurized gas outlet of supercharging device.
8. three class door hot-air engines as claimed in claim 1, it is characterized in that: described timing pulse gas mechanism (3) is made as the gas holder (301) of band timing control mechanism (6).
9. three class door hot-air engines as claimed in claim 8, it is characterized in that: described regenerator (4) is communicated with described gas holder (301) through described timing control mechanism (6).
10. three class door hot-air engines as claimed in claim 1, it is characterized in that: described timing pulse gas mechanism (3) is made as gas compressor (22), and described regenerator (4) is communicated with the pressurized gas outlet of described gas compressor (22).
Priority Applications (1)
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| CN2013100313942A CN103089486A (en) | 2012-01-28 | 2013-01-28 | Three-valve hot-air engine |
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| CN201210019663 | 2012-01-28 | ||
| CN201210019663.9 | 2012-01-28 | ||
| CN201210020475 | 2012-01-29 | ||
| CN201210020475.8 | 2012-01-29 | ||
| CN201210021071.0 | 2012-01-30 | ||
| CN201210021071 | 2012-01-30 | ||
| CN201210021890.5 | 2012-01-31 | ||
| CN201210021890 | 2012-01-31 | ||
| CN201210030622.X | 2012-02-11 | ||
| CN201210030622 | 2012-02-11 | ||
| CN201210133561 | 2012-04-28 | ||
| CN201210133561.X | 2012-04-28 | ||
| CN201210204396.2 | 2012-06-16 | ||
| CN201210204396 | 2012-06-16 | ||
| CN201210211978.3 | 2012-06-22 | ||
| CN201210211978 | 2012-06-22 | ||
| CN201210217811.8 | 2012-06-27 | ||
| CN201210217811 | 2012-06-27 | ||
| CN201210232558 | 2012-07-05 | ||
| CN201210232558.3 | 2012-07-05 | ||
| CN201210299878.0 | 2012-08-21 | ||
| CN2013100313942A CN103089486A (en) | 2012-01-28 | 2013-01-28 | Three-valve hot-air engine |
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Application publication date: 20130508 |