CN103216358A - Hot cylinder door control Stirling engine - Google Patents
Hot cylinder door control Stirling engine Download PDFInfo
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- CN103216358A CN103216358A CN2013100377041A CN201310037704A CN103216358A CN 103216358 A CN103216358 A CN 103216358A CN 2013100377041 A CN2013100377041 A CN 2013100377041A CN 201310037704 A CN201310037704 A CN 201310037704A CN 103216358 A CN103216358 A CN 103216358A
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Abstract
The invention discloses a hot cylinder door control Stirling engine which comprises a cylinder piston mechanism; the cylinder of the cylinder piston mechanism is provided with a reciprocating circulation hole; the reciprocating circulation hole is provided with a reciprocating circulation control door; the cylinder of the cylinder piston mechanism is internally provided with an internal combustion chamber; the cylinder of the cylinder piston mechanism is provided with an oxidizing agent inlet and a fuel inlet; the oxidizing agent inlet is communicated with an oxygen source by a control valve; the fuel inlet is communicated with a fuel source by a control valve; the reciprocating circulation hole is communicated with a timing pulse gas mechanism by a heat regenerator; and a working medium leading-out hole is arranged in the timing pulse gas mechanism or a channel where the heat regenerator is communicated with the timing pulse gas mechanism. The hot cylinder door control Stirling engine improves the utilization efficiency of a working medium and reduces the energy waste.
Description
Technical field
The present invention relates to a kind of heat engine, especially a kind of hot cylinder gate heat engine.
Background technique
The hot cylinder of traditional heat engine adopts the external combustion heating, and its efficiency of heating surface loss is very big, and specific power is low, therefore, needs a kind of novel hot machine of invention.
Summary of the invention
In order to address the above problem, the technological scheme that the present invention proposes is as follows:
Scheme one: a kind of hot cylinder gate heat engine, comprise cylinder piston mechanism, on the cylinder of described cylinder piston mechanism, establish the reversing current port, establish reciprocal circulation control gate at described reversing current passage port, in the cylinder of described cylinder piston mechanism, establish the internal combustion firing chamber, on the cylinder of described cylinder piston mechanism, establish oxidant inlet and fuel inlet, described oxidant inlet is communicated with oxygen source through control valve, described fuel inlet is communicated with fuel source through control valve, described reversing current port is through regenerator and timing pulse gas mechanism connection, and establishing the working medium export mouth on the communication passage of described regenerator and described timing pulse gas mechanism or in described timing pulse gas mechanism.
Scheme two: on the basis of scheme one, described timing pulse gas mechanism is made as attached cylinder piston mechanism.
Scheme three: on the basis of scheme two, the piston of the piston of described attached cylinder piston mechanism and described cylinder piston mechanism is by same crank-driven, and the V-shaped setting of cylinder of the cylinder of described attached cylinder piston mechanism and described cylinder piston mechanism.
Scheme four: on the basis of scheme one, described timing pulse gas mechanism is made as the gas holder that is subjected to the control of timing control mechanism.
Scheme five: on the basis of scheme two, described attached cylinder piston mechanism is made as gas compressor, and described regenerator is communicated with the pressurized gas outlet of described gas compressor.
Scheme six: on the basis of scheme five, the intake duct of described gas compressor is provided with supercharging device.
Scheme seven: on the basis of scheme five, the piston of the piston of described gas compressor and described cylinder piston mechanism is by same crank-driven, and the V-shaped setting of cylinder of the cylinder of described gas compressor and described cylinder piston mechanism.
Scheme eight: on the basis of scheme one, described hot cylinder gate heat engine also comprises turbo-power mechanism and impeller gas compressor, described working medium export mouth is communicated with the working medium inlet of described turbo-power mechanism, the sender property outlet of described turbo-power mechanism is communicated with the sender property outlet of described impeller gas compressor and working medium circuit communication through cooler with the working medium inlet of described impeller gas compressor; On the passage between the working medium inlet of the sender property outlet of described turbo-power mechanism and described impeller gas compressor, be provided with attached working medium export mouth.
Scheme nine: on the basis of scheme one, described cylinder piston mechanism is made as piston liquid mechanism, and described piston liquid mechanism comprises gas-liquid cylinder and gas-liquid isolation structure, and described gas-liquid isolation structure is located in the described gas-liquid cylinder.
Scheme ten: on the basis of scheme two, 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 isolation structure, and described gas-liquid isolation structure is located in the described gas-liquid cylinder.
Scheme 11: on the basis of scheme nine, the inertial force sum the when gas working medium in the described gas-liquid cylinder moves reciprocatingly greater than the liquid in the described gas-liquid cylinder and described gas-liquid isolation structure to the pressure of described gas-liquid isolation structure.
Scheme 12: on the basis of scheme ten, the inertial force sum the when gas working medium in the described gas-liquid cylinder moves reciprocatingly greater than the liquid in the described gas-liquid cylinder and described gas-liquid isolation structure to the pressure of described gas-liquid isolation structure.
Scheme 13: on the basis of scheme one, described hot cylinder gate heat engine also comprises oxygenant sensor and oxygenant control gear, described oxygenant sensor is located in the working medium loop, described oxygenant sensor provides signal to described oxygenant control gear, and described oxygenant control gear is controlled the control valve between described oxidant inlet and the described oxygen source.
Scheme 14: on the basis of scheme one, described hot cylinder gate heat engine also comprises four class door cylinder piston mechanisms, the air supply opening of described four class door cylinder piston mechanisms is communicated with described oxidant inlet, and the mouth that recharges of described four class door cylinder piston mechanisms is communicated with described working medium export mouth.
Scheme 15: on the basis of scheme one, the mass flow rate of the material that discharge described internal combustion firing chamber is greater than the mass flow rate that imports the material of described internal combustion firing chamber outside the working medium loop.
Scheme 16: on the basis of scheme one, described hot cylinder gate heat engine also comprises low temperature cold source, described low temperature cold source is used to provide cryogenic substance, and described cryogenic substance is used for cooling off described timing pulse gas mechanism or is about to enter the working medium of described timing pulse gas mechanism.
Scheme 17: in scheme one to 16 on the basis of arbitrary scheme, be provided with cooler on the reciprocation cycle passage between described regenerator and the described timing pulse gas mechanism and/or in described timing pulse gas mechanism.
Scheme 18: on the basis of arbitrary scheme, described oxygen source is gaseous state or the pure oxygen source of liquid state or the liquid air source of high pressure of high pressure in scheme one to 16.
Scheme 19: on the basis of scheme 18, the pressure of described oxygen source is at least 2MPa.
Scheme 20: on the basis of scheme one, the bearing capacity in working medium loop is greater than 2MPa.
Principle of the present invention is: under described reciprocal circulation control gate closed condition, to there be the oxygenant of pressing in the oxygen source and the fuel in the fuel source to import in the cylinder of described cylinder piston mechanism, and make it that combustion chemistry reaction take place, after promoting the descent of piston acting, open described reciprocal circulation control gate, make the combustion gas in the cylinder flow into described timing pulse gas mechanism through described regenerator, enter the Stirling thermodynamic cycle, its essence is equivalent to use as the working medium in the hot cylinder of Stirling engine with the high temperature refrigerant after the internal-combustion engine acting.
Among the present invention, so-called timing pulse gas mechanism is meant can provide gas and can be from described cylinder piston mechanism receiver gases to described cylinder piston mechanism by the timing relation, together finishes the device of [thermodynamic with described cylinder piston mechanism and correlation unit (for example regenerator etc.).So-called timing relation is meant the logical relation that cooperates described cylinder piston mechanism and described timing pulse gas mechanism to finish [thermodynamic.
Among the present invention, described working medium loop is meant the space that working medium that cylinder, described timing pulse gas mechanism and the communication passage between the two by described cylinder piston mechanism constitutes can circulate.
Among the present invention, described fuel can be hydrocarbon, hydrocarbon oxygen compound or solid carbon.Solid carbon have do not have after the burning water to generate and the burning afterproduct in the gas concentration lwevel height, easy advantage such as liquefaction; Solid carbon can adopt spray into after solid assembled in advance, the powdered or powdered after import heat engine with the mode that sprays into after liquid or the atmospheric carbon dioxide fluidisation again.
Among the present invention, described gas-liquid cylinder is meant and can holds 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 isolation 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 flow of liquid port, and described flow of liquid port is used for being communicated with hydraulic power mechanism and/or liquid working substance send-back system.
Among the present invention, described gas-liquid isolation structure is meant the structure that can move reciprocatingly in described gas-liquid cylinder, as isolating plate, isolating film, piston etc., its effect is the gas working medium and the liquid of isolating in the described gas-liquid cylinder, preferably, described gas-liquid isolation structure and described gas-liquid cylinder sealed sliding are movingly.In described piston liquid mechanism working procedure, be in diverse location in the described gas-liquid cylinder according to described gas-liquid isolation structure, may all be gas working medium in the described gas-liquid cylinder, may all be liquid also, perhaps gas working medium and liquid exist simultaneously.
Among the present invention, liquid in the described gas-liquid cylinder is different with traditional piston crank mechanism with described gas-liquid isolation structure, piston in traditional piston crank mechanism can be stopped by the thrust of connecting rod or pulling force, thereby realize restriction to piston stroke, and in described gas-liquid cylinder, when the gas working medium in the described gas-liquid cylinder is done positive work, described gas-liquid isolation structure is stressed and moves to the lower dead center direction, liquid is discharged described gas-liquid cylinder with high voltage style and promote 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 the described gas-liquid cylinder is no longer reduced, this moment, liquid can apply braking force to the described gas-liquid isolation structure in the described gas-liquid cylinder, and it is stopped, and clashed into the wall of the liquid bottom portion of gas-liquid cylinder to prevent it; When constantly in described gas-liquid cylinder, importing liquid, described gas-liquid isolation structure can constantly move to the top dead center direction, in the time of near arriving top dead center, stop in described gas-liquid cylinder, to import liquid or make the liquid in the described gas-liquid cylinder reduce (outflow), however, liquid and described gas-liquid isolation structure in the described gas-liquid cylinder still can be owing to inertia moves to the top dead center direction, at this moment, if the pressure of the gas working medium in the described gas-liquid cylinder is not high enough, then can cause described gas-liquid isolation structure to continue to move upward and clash into the wall at gas-liquid cylinder top, for fear of this bump, need make in the gas-liquid cylinder pressure of gas working medium enough high, the inertial force sum when it is moved reciprocatingly greater than the liquid in the described gas-liquid cylinder and described gas-liquid isolation structure to the pressure of described gas-liquid isolation structure.
Among the present invention, inertial force sum when liquid in gas-liquid cylinder described in the working procedure of described hot cylinder gate heat engine and described gas-liquid isolation structure move reciprocatingly changes, therefore in engineering design, should guarantee all to satisfy constantly the condition of " the inertial force sum the when gas working medium in the described gas-liquid cylinder moves reciprocatingly greater than the liquid in the described gas-liquid cylinder and described gas-liquid isolation structure to the pressure of described gas-liquid isolation structure " in any work, for example by adjusting the working pressure in the described working medium loop, adjust the quality of gas-liquid isolation structure, the modes such as fluid density or adjustment liquid depth of adjusting realize, wherein, described liquid depth is meant the degree of depth of the liquid of liquid on the direction that moves reciprocatingly.
So-called " adjusting the working pressure in the described working medium loop " is to realize by the volume flowrate that adjust to flow into and/or flow out the gas working medium in described working medium loop, for example can realize by the switch gap of adjusting described working medium export mouth, each time of opening and/or the openings of sizes of described working medium export mouth place control valve.
Among the present invention, described four class door cylinder piston mechanisms are meant that cylinder is provided with suction port, relief opening, air supply opening and recharges mouth, in described suction port, described relief opening, described air supply opening and the described corresponding successively cylinder piston mechanism that intake valve, exhaust valve, air feed door is set and recharges door in mouthful place that recharges.
Among the present invention, described oxygenant sensor is meant the device that the content to the oxygenant in the described working medium loop detects.Described oxygenant sensor provides signal to described oxygenant control gear, static or dynamic oxygenate content setting value is controlled to increase or to reduce the amount of supplying with oxygenant in described working medium loop the control valve between described oxidant inlet and the described oxygen source in signal that described oxygenant control gear provides according to described oxygenant sensor and the predefined described working medium loop, reaches the purpose of the content of oxygenant in the described working medium of the regulation and control loop.
The setting value of described oxygenate content can be a numerical value, also can be a numerical value interval, and for example: the setting value of the oxygenate content in the described working medium loop can be 5%, 10% or 10%～12% etc.
Described oxygenant sensor can be located on the described working medium loop away from described internal combustion firing chamber, can guarantee that whole described working medium loop is work under oxygen enrichment (oxygen content is greater than zero) state, make the stable combustion chemistry reaction of generation in the described internal combustion firing chamber, can also prevent the generation of carbon distribution simultaneously.
Among the present invention, the discharge capacity of working pressure (for example can realize) by adjusting described working medium loop and described cylinder piston mechanism by cracking pressure or the switching time of adjusting described working medium export mouth, to control the quality discharge capacity of described cylinder piston mechanism, make the flow mass M of the material that described internal combustion firing chamber discharges
2Greater than the flow mass M that outside described working medium loop, imports the material of described internal combustion firing chamber
1That is to say except from described working medium loop, importing outside the material of described internal combustion firing chamber, some material imports described internal combustion firing chamber from described working medium loop, because described internal combustion firing chamber is arranged in the described working medium loop, have at least a part to flow back to described internal combustion firing chamber so that is to say the material of discharging, promptly realized working medium back and forth flowing between described cylinder piston mechanism and described timing pulse gas mechanism from described internal combustion firing chamber.The material that export-oriented described internal combustion firing chamber imports from described working medium loop can be oxygenant, fuel or pressurized gas etc.
Among the present invention, described low temperature cold source is meant can 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 commercial buying pattern to obtain, described cryogenic substance can be liquid nitrogen, liquid oxygen, liquid helium or liquefied air etc.When oxygenant among the present invention was liquid oxygen, liquid oxygen can be directly as described cryogenic substance.
Among the present invention, described low temperature cold source is in the direct mode that described cryogenic substance is mixed with described working medium circuit communication with the working medium in the described working medium loop, perhaps making the mode of the working medium heat exchange in described cryogenic substance and the described working medium loop through heat-exchanger rig, in the described timing pulse gas mechanism or the working medium that is about to enter timing pulse gas mechanism carry out cooling processing.Heat engine is the power mechanism of a kind of work cycle near Carnot's cycle, and the calculating of its thermal efficiency can be with reference to Kano thermal efficiency of cycle 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, promptly sink temperature is very low, and then thermal efficiency η is very high, and is very little to the heat of low-temperature receiver discharging.Infer that thus the cryogenic substance that usable temp is quite low makes sink temperature T
2Decline to a great extent, thereby significantly reduce the heat that discharges to low-temperature receiver, effectively improve engine efficiency.
The cryogenic substance that temperature is low more (for example liquid oxygen, liquid nitrogen or liquid helium etc.), in manufacture process, need to consume many more energy, but with regard to unit mass, the contribution that engine thermal efficiency η is promoted is big more, like storing the energy in the very low material of temperature, the notion that is equivalent to a kind of novel battery, described cryogenic substance can use the very low energy of cost such as rubbish electricity to make, thereby effectively reduce the user cost of motor.
Among the present invention, fuel burning in described cylinder piston mechanism may be that the compression ignite mode also may be an ignition combustion mode, if adopt the mode of ignition, and also need in described cylinder piston mechanism, set up an office fiery device, for example spark plug.
Among the present invention, the pressure of described oxygen source is at least 2MPa, 2.5MPa, 3MPa, 3.5MPa, 4MPa, 4.5MPa, 5MPa, 5.5MPa, 6MPa, 6.5MPa, 7MPa, 7.5MPa, 8MPa, 8.5MPa, 9MPa, 9.5MPa or is at least 10MPa.
Among the present invention, working medium in the described working medium loop need be through overcompression, heat temperature raising boosts, acting and the process that is cooled, this just requires described working medium loop energy 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.
Among the present invention, power pressure and its bearing capacity in described working medium loop are complementary, and the maximum pressure of the working medium in promptly described working medium loop reaches its bearing capacity.
The inventor proposes the new elaboration mode of the 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, not having to be that the out-of-phase diagram of coordinate is used for the research to thermodynamic process and thermodynamic cycle with pressure P and temperature T.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 remarkable advantages than P-V figure commonly used and T-S figure, it more constitutionally the variation of working medium state in thermodynamic process and the thermodynamic cycle is described, make everybody more deep understanding be arranged to thermodynamic process and thermodynamic cycle.Utilize out-of-phase diagram, the inventor has summed up the new elaboration mode of ten second laws of thermodynamics, though 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 the 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 thermodynamic (al) development and hot machine progress of 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 is that coordinate has been drawn out-of-phase diagram with pressure P and temperature T, and Carnot Cycle and Otto Cycle are identified in the out-of-phase diagram.Clearly, out-of-phase diagram makes the variation of working medium state in thermodynamic process and the thermodynamic cycle more apparent, and the essence of thermodynamic process and thermodynamic cycle is more readily understood.The out-of-phase diagram of Carnot Cycle for example, can make everybody easily draw such conclusion: the mission of the reversible adiabatic compression process of Carnot Cycle is in the mode of reversible adiabatic compression the temperature of working medium to be increased to 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, everybody can also find out significantly: when the temperature of the high temperature heat source of Carnot Cycle raises, 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 the 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 a constant, and k is the adiabatic index of working medium).According to mathematical analysis,, 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 is meant the process with heat transfer, i.e. the process of heat release and the process of heat absorption).If a thermal procession or a series of interconnective thermal procession are from an A point of arrival B, then 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.The inventor can draw such conclusion: on adiabatic process curve at an A place, then tie point A is adiabatic process with the process of some B as a B; As the right side of a B at adiabatic process curve at an A place, then tie point A is an endothermic process with the process of some B; As the left side of a B at adiabatic process curve at an A place, then tie point A is an exothermic process with the process of some B.Because the process of tie point A and some B may be exothermic process, adiabatic process or endothermic process, so the inventor is reference with a B, 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, so the inventor is reference with an A, 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 new elaboration modes about the second law of thermodynamics:
1, do not have the participation of endothermic process, exothermic process can not be returned to its initial point.
2, do not have the participation of exothermic process, endothermic process can not be returned to its initial point.
3, do not have 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 recovery of endothermic process arrive the pressure of its initial point with the thermal procession beyond the exothermic process, its temperature necessarily is higher than the temperature of its initial point.
When 6, making the pressure recovery of exothermic process arrive the pressure of its initial point with the thermal procession beyond the endothermic process, its temperature necessarily is 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 hot machine of not heat release can not reach Carnot Cycle's Efficiency.
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 about the new elaboration mode of the second law of thermodynamics exploitation to thermodynamic (al) progress and high efficiency thermal machine is significant.
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?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.
Among the present invention, should necessary parts, unit or system be set in the place of necessity according to the known technology in motor, heat engine and heat power field.
Beneficial effect of the present invention is as follows:
The present invention can improve the utilization ratio of working medium, reduces the waste of the energy.
Description of drawings
Fig. 1 is the structural representation of the embodiment of the invention 1;
Fig. 2 is the structural representation of the embodiment of the invention 2;
Fig. 3 is the structural representation of the embodiment of the invention 3;
Fig. 4 is the structural representation of the embodiment of the invention 4;
Fig. 5 is the structural representation of the embodiment of the invention 5;
Fig. 6 is the structural representation of the embodiment of the invention 6;
Fig. 7 is the structural representation of the embodiment of the invention 7;
Fig. 8 is the structural representation of the embodiment of the invention 8;
Fig. 9 is the structural representation of the embodiment of the invention 9;
Figure 10 is the structural representation of the embodiment of the invention 10;
Figure 11 is the structural representation of the embodiment of the invention 11;
Figure 12 is the structural representation of the embodiment of the invention 12;
Figure 13 is the structural representation of the embodiment of the invention 13;
Figure 14 is the structural representation of the embodiment of the invention 14;
Figure 15 is the structural representation of the embodiment of the invention 15;
Figure 16 is the structural representation of the embodiment of the invention 16;
Figure 17 is the structural representation of the embodiment of the invention 17,
Among the figure:
1 cylinder piston mechanism, 11 reversing current ports, 12 reciprocal circulation control gates, 13 oxidant inlets, 14 fuel inlets, 15 control valves, 16 oxygen sources, 17 control valves, 18 fuel source, 19 working medium export mouths, 20 control valves, 3 timing pulse gas mechanisms, 4 regenerators, 5 coolers, 6 timing control mechanisms, 31 attached cylinder piston mechanisms, 32 gas holder, 33 gas compressors, 71 turbo-power mechanisms, 72 impeller gas compressors, 73 attached working medium export mouths, 8 low temperature cold sources, 106 oxygenant storage tanks, 111 gas-liquid cylinders, 112 gas-liquid isolation structures, 113 flow of liquid ports, 96 hydraulic power mechanisms, 97 liquid send-back systems, 99 process control mechanisms, 200 4 class door cylinder piston mechanisms, 201 suction ports, 202 relief openings, 203 air supply openings, 204 recharge mouth, 301 oxygenant sensors, 302 oxygenant control gear.
Embodiment
Hot cylinder gate heat engine as shown in Figure 1, comprise cylinder piston mechanism 1, on the cylinder of described cylinder piston mechanism 1, establish reversing current port 11,11 places establish reciprocal circulation control gate 12 at described reversing current port, establish the internal combustion firing chamber in the cylinder of described cylinder piston mechanism 1, on the cylinder of described cylinder piston mechanism 1, establish oxidant inlet 13 and fuel inlet 14, described oxidant inlet 13 is communicated with oxygen source 16 through control valve 15, described fuel inlet 14 is communicated with fuel source 18 through control valve 17, described reversing current port 11 is communicated with timing pulse gas mechanism 3 through regenerator 4, and on the communication passage of described regenerator 4 and described timing pulse gas mechanism 3, establish working medium export mouth 19, and on the pipeline of described working medium export mouth 19, be provided with control valve 20.Described control valve 15, described control valve 16, described control valve 20 are controlled by timing mechanism.
The working procedure of present embodiment is: under described reciprocal circulation control gate 12 closed conditions, oxygenant in the described oxygen source 16 and the fuel in the described fuel source 18 import in the cylinder of described cylinder piston mechanism 1, then, described control valve 15 and described control valve 17 are closed; The combustion chemistry reaction takes place in described oxygenant and described fuel in the cylinder of described cylinder piston body 1, the high temperature and high pressure gas working medium of generation promotes the descent of piston acting; When described piston arrives lower dead center, described reciprocal circulation control gate 12 is opened, described piston stroking upward, gas working medium in the cylinder of described cylinder piston mechanism 1 is flowed in the described timing pulse gas mechanism 3 through described regenerator 4, described gas working medium is stayed heat in the described regenerator 4 when flowing through described regenerator 4; Described timing pulse gas mechanism 3 offers described cylinder piston mechanism 1 by the timing relation with described gas working medium, when described gas working medium refluxes through described regenerator 4, heat in the described regenerator 4 is brought back in the described cylinder piston mechanism 1, promote described piston acting, when described piston is moved to top dead center by lower dead center, promote gas working medium in the described cylinder and enter described timing pulse gas mechanism 3 once more, described gas working medium repeats above-mentioned circulation between described cylinder piston mechanism 1 and described timing pulse gas mechanism 3, finally, described gas working medium is derived by described working medium export mouth 19; After described gas working medium is derived from working medium export mouth 19, close described control valve 20 and described reciprocal circulation control gate 12, open described control valve 15 and described control valve 17, enter next circulation.
Described working medium export mouth 19 can be derived the part heat when deriving working medium.
In the present embodiment, described internal combustion firing chamber is made as intermittent combustion; Described oxygen source 16 is the gaseous state pure oxygen of high pressure; The pressure of described oxygen source 16 is at least 2MPa.
Selectively, described internal combustion firing chamber is made as continuous burning; Described oxygen source 16 is made as the liquid pure oxygen source or the liquid air source of high pressure; The pressure of described oxygen source 16 is made as greater than 2.5MPa, 3MPa, 3.5MPa, 4MPa, 4.5MPa, 5MPa, 6MPa or greater than 10MPa.
Embodiment 2
Hot cylinder gate heat engine as shown in Figure 2, itself and embodiment's 1 difference is: described timing pulse gas mechanism 3 is made as attached cylinder piston mechanism 31, and establishes cooler 5 on the reciprocation cycle passage between described regenerator 4 and the described working medium export mouth 19.
When the high temperature and high pressure gas working medium of described cylinder piston mechanism 1 flows into described attached cylinder piston mechanism 31 through described regenerator 4, the descent of piston in the described attached cylinder piston mechanism 31, externally outputting power; Piston in described attached cylinder piston mechanism 31, is promoted gas and enters in the described cylinder piston mechanism 1 when top dead center moves by lower dead center.
Hot cylinder gate heat engine as shown in Figure 3, itself and embodiment's 2 difference is: described cooler 5 is located in the described attached cylinder piston mechanism 31.
Identical with embodiment 2, described cooler 5 all is the effect of playing cooling working medium.
Hot cylinder gate heat engine as shown in Figure 4, itself and embodiment's 2 difference is: all be provided with cooler 5 on the passage between described regenerator 4 and the described attached cylinder piston mechanism 31 and in the described attached cylinder piston mechanism 31.
Hot cylinder gate heat engine as shown in Figure 5, itself and embodiment's 3 difference is: the piston of the piston of described attached cylinder piston mechanism 31 and described cylinder piston mechanism 1 is by same crank-driven, and the V-shaped setting of cylinder of the cylinder of described attached cylinder piston mechanism 31 and described cylinder piston mechanism 1, at this moment, the structure of described hot cylinder gate heat engine and traditional α type Stirling engine structural similarity.
In the process of implementing; those skilled in the art can inspire according to the technology of present embodiment; hot cylinder gate heat engine of the present invention is designed to β type or γ type heat engine structure; but enlighten resulting embodiment based on the technology of present embodiment, should be considered as in protection scope of the present invention.
Hot cylinder gate heat engine as shown in Figure 6, itself and embodiment's 5 difference is: described cooler 5 is located on the reciprocation cycle passage between described regenerator 4 and the described attached cylinder piston mechanism 31, and described working medium export mouth 19 is located on the cylinder of described attached cylinder piston mechanism 31.
Embodiment 7
Hot cylinder gate heat engine as shown in Figure 7, itself and embodiment's 5 difference is: all be provided with cooler 5 on the reciprocation cycle passage between described regenerator 4 and the described attached cylinder piston mechanism 31 and in the described attached cylinder piston mechanism 31.
Embodiment 8
Hot cylinder gate heat engine as shown in Figure 8, itself and embodiment's 1 difference is: described timing pulse gas mechanism 3 is made as the gas holder 32 that is subjected to 6 controls of timing control mechanism, all is being provided with cooler 5 on the reciprocation cycle passage between described regenerator 4 and the described gas holder 32 He on the described gas holder 32.
In the process of implementing, the cooler 5 at two places can be according to actual needs, as long as can satisfy the requirement of cooling, optional one gets final product.
Embodiment 9
Hot cylinder gate heat engine as shown in Figure 9, itself and embodiment's 1 difference is: described timing pulse gas mechanism 3 is made as the gas compressor 33 of cylinder piston type, described regenerator 4 is communicated with the pressurized gas outlet of described gas compressor 33, all is provided with cooler 5 on the reciprocation cycle passage between described regenerator 4 and the described gas compressor 33 He on the described gas compressor 33.
The piston of described gas compressor 33 by lower dead center in the process of top dead center motion, the IC Intake Valve Closes of described gas compressor 33, the piston of described gas compressor 33 compresses the working medium in the described gas compressor 33, thereby the pressure in the whole working medium loop is further raise.
In the process of implementing, the cooler 5 at two places can be according to actual needs, as long as can satisfy the requirement of cooling, optional one gets final product.
Embodiment 10
Hot cylinder gate heat engine as shown in figure 10, itself and embodiment's 9 difference is: establish supercharging device on the intake duct of described gas compressor 33, described supercharging device is made as impeller gas compressor 72.
Selectively, described supercharging device is made as roots blower or screw type gas compressor.
Hot cylinder gate heat engine as shown in figure 11, itself and embodiment's 9 difference is: the piston of the piston of described gas compressor 33 and described cylinder piston mechanism 1 is by same crank-driven, and the V-shaped setting of cylinder of the cylinder of described gas compressor 33 and described cylinder piston mechanism 1.
Hot cylinder gate heat engine as shown in figure 12, itself and embodiment's 11 difference is: have additional the impeller gas compressor 72 that plays pressurization on the intake duct of described gas compressor 33.
Selectively, described impeller gas compressor 72 can be replaced with supercharging equipments such as roots blower or screw type gas compressors.
Hot cylinder gate heat engine as shown in figure 13, itself and embodiment's 4 difference is: described hot cylinder gate heat engine also comprises turbo-power mechanism 71 and impeller gas compressor 72, described working medium export mouth 19 is located on the cylinder of described attached cylinder piston mechanism 31, described working medium export mouth 19 is communicated with the working medium inlet of described turbo-power mechanism 71, the sender property outlet of described turbo-power mechanism 71 is communicated with the working medium inlet of described impeller gas compressor 72 through cooler 5, the sender property outlet of described impeller gas compressor 72 and described working medium circuit communication, specifically be with described cylinder piston mechanism 1 and described attached cylinder piston mechanism 31 between communication passage be communicated with; Passage between described cooler 5 between described turbo-power mechanism 71 and the described impeller gas compressor 72 and the working medium of described impeller gas compressor 72 inlet is provided with attached working medium export mouth 73.
Selectively, on the passage between described attached working medium export mouth 73 sender property outlet that is located at described turbo-power mechanism 71 and the described cooler 5 that it directly is communicated with; 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 working medium export mouth 19 are located at the diverse location on the described working medium loop.
Hot cylinder gate heat engine as shown in figure 14, itself and embodiment's 11 difference is: described hot cylinder gate heat engine also comprises low temperature cold source 8, described low temperature cold source 8 is the storage tanks that store liquid nitrogen, and the liquid nitrogen in the storage tank is used for cooling off the working medium of described gas compressor 33.
In the present embodiment, described low temperature cold source 8 directly is communicated with described gas compressor 33, is provided with control valve on the communication passage between described low temperature cold source 8 and the described gas compressor 33.
Optionally, described low temperature cold source 8 can also be through the working medium heat exchange in heat-exchanger rig makes described cryogenic substance and described working medium loop.
Hot cylinder gate heat engine as shown in figure 15, itself and embodiment's 8 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 isolation structure 112 is located in the described gas-liquid cylinder 111, the flow of liquid port 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 flow of liquid port 113 of the liquid end of described gas-liquid cylinder 111; Described hydraulic power mechanism 96 and described liquid send-back system 97 are subjected to 99 controls of process control mechanism.
In the present embodiment, the inertial force sum the when gas working medium in the described gas-liquid cylinder 111 moves reciprocatingly greater than the liquid in the described gas-liquid cylinder 111 and described gas-liquid isolation structure 112 to the pressure of described gas-liquid isolation structure 112.
Optionally, described gas-liquid isolation structure 112 can be made as platy structure, membrane structure or piston-like structure etc.Preferably, described gas-liquid isolation structure 112 and described gas-liquid cylinder 111 sealed sliding are movingly.
Be made as in the structure of attached cylinder piston mechanism 31 in described timing pulse gas mechanism 3, attached cylinder piston mechanism 31 is made as piston liquid mechanism, or described cylinder piston mechanism 1 and attached cylinder piston mechanism 31 are made as piston liquid mechanism simultaneously.
Hot cylinder gate heat engine as shown in figure 16, itself and embodiment's 8 difference is: described hot cylinder gate heat engine also comprises four class door cylinder piston mechanisms 200, the cylinder of described four class door cylinder piston mechanisms 200 is provided with suction port 201, relief opening 202, air supply opening 203 and recharges mouthfuls 204, described suction port 201, described relief opening 202, described air supply opening 203 and described recharge mouthful 204 places successively correspondence intake valve, exhaust valve, air feed door are set and recharge door; Described air supply opening 203 is communicated with described oxidant inlet 13 through oxygenant storage tank 106, describedly recharges mouthfuls 204 and is communicated with described working medium export mouth 19.
Optionally, described air supply opening 203 also can directly be communicated with described oxidant inlet 13.
By the oxygenant after 200 compressions of described four class door cylinder piston mechanisms, enter in the described cylinder piston mechanism 1 through described air supply opening 203, fuel enters in the described cylinder piston mechanism 1 through fuel inlet 14, the combustion chemistry reaction takes place in described oxygenant and described fuel in described cylinder piston mechanism 1, the big energy thing that produces promotes 1 acting of described cylinder piston mechanism, the working medium that flows out from described cylinder piston mechanism 1 enters described four class door cylinder piston mechanisms 200 through described working medium export mouth 19, the waste heat of described working medium is discharged described four class door cylinder piston mechanisms through described relief opening 202 after promoting 200 actings of described four class door cylinder piston mechanisms.
Hot cylinder gate heat engine as shown in figure 17, itself and embodiment's 3 difference is: described hot cylinder gate heat engine also comprises oxygenant sensor 301 and oxygenant control gear 302, described oxygenant sensor 301 is located in the described working medium loop, 301 pairs of described oxygenant control gear 302 of described oxygenant sensor provide signal, the control valve 15 between described oxygenant control gear 302 described oxidant inlets 13 of control and the described oxygen source 16.
Optionally, described oxygenant sensor 301 can be located on the working medium loop away from described internal combustion firing chamber, for example is arranged in the communication passage near described attached cylinder piston mechanism 31.
Among the above embodiment, the mass flow rate of the material that discharge described internal combustion firing chamber is greater than the mass flow rate that imports the material of described internal combustion firing chamber outside described working medium loop.
Obviously, the invention is not restricted to above embodiment, according to the known technology and the technological scheme disclosed in this invention of related domain, can derive or association goes out many flexible programs, all these flexible programs also should be thought protection scope of the present invention.
Claims (10)
1. hot cylinder gate heat engine, comprise cylinder piston mechanism (1), it is characterized in that: on the cylinder of described cylinder piston mechanism (1), establish reversing current port (11), locate to establish reciprocal circulation control gate (12) at described reversing current port (11), in the cylinder of described cylinder piston mechanism (1), establish the internal combustion firing chamber, on the cylinder of described cylinder piston mechanism (1), establish oxidant inlet (13) and fuel inlet (14), described oxidant inlet (13) is communicated with oxygen source (16) through control valve (15), described fuel inlet (14) is communicated with fuel source (18) through control valve (17), described reversing current port (11) is communicated with timing pulse gas mechanism (3) through regenerator (4), and on the communication passage of described regenerator (4) and described timing pulse gas mechanism (3) or in described timing pulse gas mechanism (3), establish working medium export mouth (19).
2. hot according to claim 1 cylinder gate heat engine is characterized in that: described timing pulse gas mechanism (3) is made as attached cylinder piston mechanism (31).
3. as hot cylinder gate heat engine as described in the claim 2, it is characterized in that: the piston of the piston of described attached cylinder piston mechanism (31) and described cylinder piston mechanism (1) is by same crank-driven, and the V-shaped setting of cylinder of the cylinder of described attached cylinder piston mechanism (31) and described cylinder piston mechanism (1).
4. hot according to claim 1 cylinder gate heat engine is characterized in that: described timing pulse gas mechanism (3) is made as the gas holder (32) that is subjected to timing control mechanism (6) control.
5. as hot cylinder gate heat engine as described in the claim 2, it is characterized in that: described attached cylinder piston mechanism (31) is made as gas compressor (33), and described regenerator (4) is communicated with the pressurized gas outlet of described gas compressor (33).
6. as hot cylinder gate heat engine as described in the claim 5, it is characterized in that: the intake duct of described gas compressor (33) is provided with supercharging device.
7. as hot cylinder gate heat engine as described in the claim 5, it is characterized in that: the piston of the piston of described gas compressor (33) and described cylinder piston mechanism (1) is by same crank-driven, and the V-shaped setting of cylinder of the cylinder of described gas compressor (33) and described cylinder piston mechanism (1).
8. hot according to claim 1 cylinder gate heat engine, it is characterized in that: described hot cylinder gate heat engine also comprises turbo-power mechanism (71) and impeller gas compressor (72), described working medium export mouth (19) is communicated with the working medium inlet of described turbo-power mechanism (71), the sender property outlet of described turbo-power mechanism (71) is communicated with the sender property outlet of described impeller gas compressor (72) and working medium circuit communication through cooler (5) with the working medium inlet of described impeller gas compressor (72); On the passage between the working medium inlet of the sender property outlet of described turbo-power mechanism (71) and described impeller gas compressor (72), be provided with attached working medium export mouth (73).
9. hot according to claim 1 cylinder gate heat engine, it is characterized in that: described cylinder piston mechanism (1) is made as piston liquid mechanism, described piston liquid mechanism comprises gas-liquid cylinder (111) and gas-liquid isolation structure (112), and described gas-liquid isolation structure (112) is located in the described gas-liquid cylinder (111).
10. as hot cylinder gate heat engine as described in the claim 2, it is characterized in that: described attached cylinder piston mechanism (31) is made as attached piston liquid mechanism, described attached piston liquid mechanism comprises gas-liquid cylinder and gas-liquid isolation structure, and described gas-liquid isolation structure is located in the described gas-liquid cylinder.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2013100377041A CN103216358A (en) | 2012-01-31 | 2013-01-31 | Hot cylinder door control Stirling engine |
Applications Claiming Priority (9)
| Application Number | Priority Date | Filing Date | Title |
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| CN201210021916.6 | 2012-01-31 | ||
| CN201210021916 | 2012-01-31 | ||
| CN201210130354 | 2012-04-27 | ||
| CN201210130354.9 | 2012-04-27 | ||
| CN201210144384.5 | 2012-05-10 | ||
| CN201210144384 | 2012-05-10 | ||
| CN201210307097.1 | 2012-08-25 | ||
| CN201210307097 | 2012-08-25 | ||
| CN2013100377041A CN103216358A (en) | 2012-01-31 | 2013-01-31 | Hot cylinder door control Stirling engine |
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| CN103216358A true CN103216358A (en) | 2013-07-24 |
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| CN2013100377041A Pending CN103216358A (en) | 2012-01-31 | 2013-01-31 | Hot cylinder door control Stirling engine |
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| CN104632466A (en) * | 2014-01-06 | 2015-05-20 | 摩尔动力(北京)技术股份有限公司 | Stamping impinging stream engine |
| CN107762660A (en) * | 2017-11-27 | 2018-03-06 | 品孚罗特过滤设备（北京）有限公司 | Backheat structure and the Stirling engine for including the backheat structure |
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Application publication date: 20130724 |