WO2013078775A1

WO2013078775A1 - Dual-conduit entropy-cycle engine

Info

Publication number: WO2013078775A1
Application number: PCT/CN2012/001620
Authority: WO
Inventors: 靳北彪
Original assignee: Jin Beibiao
Priority date: 2011-12-01
Filing date: 2012-12-03
Publication date: 2013-06-06

Abstract

A dual-conduit entropy-cycle engine, comprising: a piston-type gas-compression mechanism (9), a piston-type gas work mechanism (10), and two communication conduits (1). The working-medium outlet of the piston-type gas-compression mechanism (9) is in communication with the working-medium inlet of the piston-type gas work mechanism (10) via a communication conduit (1). The working-medium outlet of the piston-type gas work mechanism (10) is in communication with the working-medium inlet of the piston-type gas-compression mechanism (9) via the other communication conduit (1). The piston-type gas-compression mechanism (9) is in communication with the piston-type gas work mechanism (10) via the two communication conduits (1) in such a manner as to form a closed circuit for a working medium. A combustion chamber (3) is provided inside said closed circuit. A working-medium lead-out port (6) is provided on said closed circuit. The present dual-conduit entropy-cycle engine is highly efficient and conserves energy.

Description

Description Book Dual Channel Entropy Cycle Engine Technical Field

The invention relates to the field of thermal energy and power, and in particular to a hot air machine.

Background technique

In recent years, the problem of high energy consumption and high pollution emission of traditional internal combustion engines has become increasingly prominent. Therefore, hot air machines have received extensive attention. However, hot air machines are heated by external combustion heating methods. It is well known that external combustion heating processes are difficult. A higher temperature working fluid is obtained, thus causing a large amount of chemical labor loss. Not only that, because the rate of external combustion heating is limited, the material requirements are high, and the load response is poor, so the single machine power and the whole machine power density of the heat engine are severely restricted, and the use of the heat engine is severely limited. Therefore, it is necessary to invent a new type of engine.

Summary of the invention

The invention provides a dual-channel entropy cycle engine with high power and high power density, which solves the problem that the temperature and pressure of the conventional heat engine are difficult to be heated to the proper height and affect the power and power density.

The technical solution proposed by the present invention is as follows:

A dual-channel entropy cycle engine includes a piston gas compression mechanism, a piston gas work mechanism, and two communication passages, and a working fluid outlet of the piston gas compression mechanism passes through the communication passage and the piston a working gas inlet of the gas working mechanism is connected, and a working medium outlet of the piston gas working mechanism is connected to a working medium inlet of the piston gas compression mechanism via another communication passage; the piston gas compression mechanism is The two communication passages are connected to the piston gas working mechanism to form a working fluid closed circuit; an internal combustion combustion chamber is disposed in the working fluid closed circuit, and a working fluid outlet is disposed on the working fluid closed circuit.

According to the second aspect of the invention, further, the internal combustion combustion chamber is disposed at an outlet of the working fluid outlet of the piston type gas compression mechanism and a working outlet of the piston gas working mechanism. The downstream working fluid is closed in the circuit.

Solution 3. On the basis of the first or second aspect, the internal combustion combustion chamber is further set as a side internal combustion combustion chamber.

Solution 4. On the basis of the solution 1, the dual-channel entropy cycle engine further includes a cooler, and the cooler is disposed on the working fluid closed circuit.

On the basis of the fourth aspect, the dual-channel entropy cycle engine further includes a direct connection channel, and the direct connection channel communicates with the working fluid outlet of the piston gas working mechanism and the piston type a working fluid inlet of the compression mechanism, the cooler being disposed on the direct connection passage or the communication between the working fluid outlet of the piston gas working mechanism and the working fluid inlet of the piston gas compression mechanism On the passage, a control width is provided on the direct passage and on the communication passage between the working fluid outlet of the piston gas working mechanism and the working fluid inlet of the piston gas compression mechanism.

On the basis of the fourth aspect, further optionally, the two-channel entropy cycle engine further includes an oxidant source, and the cooler is disposed at a working fluid outlet of the piston gas working mechanism and the piston gas Compression mechanism Said communication channel between said mass inlets, said oxidant source being in communication with said communication passage between said oxidant inlet and said cooler and said working inlet of said piston-type gas compression mechanism, said cooler The communication passage between the oxidant inlet and the oxidant inlet is provided with a cooling liquid discharge port, and a liquid carbon dioxide outlet is provided on the communication passage between the oxidant inlet and the piston type gas compression mechanism.

According to the fourth aspect, further, the cooler is disposed upstream of the working fluid outlet of the piston gas working mechanism and downstream of the working fluid inlet of the internal combustion combustion chamber. The working fluid is closed on the circuit.

Scheme 8. On the basis of Scheme 4, further optionally, the cooler is configured as a radiator, a gas-liquid direct mixing cooler, an adsorption refrigerator or a non-direct mixer cooler.

In a further aspect of the invention, the dual-channel entropy cycle engine further includes an oxidant source, the oxidant source passing through the heated fluid passage of the non-direct-mixing cooler and the internal combustion chamber Connected.

Scheme 10. On the basis of the scheme 8 or the scheme 9, further optionally, a cryogenic liquid discharge port is provided on the non-direct mixer cooler.

According to the solution 4, the solution 5, the solution 7, the solution 8 or the solution 9, the dual-channel entropy cycle engine further includes a cooling liquid discharge port, and the cooling liquid discharge port is disposed at The communication passage between the cooler and the working fluid outlet.

Scheme 12. Further, based on the scheme 1 or the scheme 2, the dual-channel entropy cycle engine further includes an oxidant source, and the oxidant source is in communication with the working fluid closed loop.

Scheme 13. Further based on the scheme 12, the oxidant source is in communication with the internal combustion chamber. On the basis of the scheme 12, further optionally, the entropy cycle engine further includes a direct mixing condensing cooler, wherein the cooled fluid inlet of the direct mixing condensing cooler is in communication with the working fluid outlet. The oxidant source is in communication with the heated fluid inlet of the direct mixing condensing cooler and is in communication with the working fluid closed circuit via the heated fluid outlet of the direct mixing condensing cooler.

In a further aspect of the invention, the oxidant source is in communication with the internal combustion combustion chamber via a heated fluid outlet of the direct mixing condensing cooler.

Scheme 16. Based on Scheme 12, further optionally, the pressure of the oxidant source is greater than 2 MPa. According to the second aspect of the invention, further, the working fluid outlet is disposed upstream of the working fluid outlet of the piston gas working mechanism (10) and the working fluid of the internal combustion combustion chamber The inlet is closed on the downstream working fluid.

According to the first aspect, further, the dual-channel entropy cycle engine further includes a non-direct-mixing condensing cooler, the cooled working fluid inlet of the non-direct-mixing condensing cooler and the working fluid The outlet is connected.

Scheme 19. Based on the scheme 14, further optionally, the direct mixing condensing cooler is provided with a cryogenic liquid discharge port.

Scheme 20. Based on Scheme 18, further optionally, the non-direct mixing condensing cooler is provided with a cryogenic liquid discharge port.

Scheme 21. Based on the scheme 19 or the scheme 20, further optionally, the dual channel entropy cycle engine The description also includes a cryogenic liquid working fluid storage tank in communication with the cryogenic liquid discharge port.

Scheme 22. Based on the scheme 14, further optionally, the direct mixing condensing cooler is provided with a non-condensing gas outlet. Scheme 23. On the basis of the scheme 18, further optionally, the non-direct mixing condensing cooler is provided with a non-condensing gas outlet. Scheme 24. On the basis of Option 22 or Scheme 23, further optionally, the non-condensable gas outlet is in communication with the closed circuit of the working fluid.

In a further aspect, the entropy cycle engine further includes an oxidant source, the oxidant source being in communication with the internal combustion combustion chamber via a heated fluid passage of the non-direct mixing condensing cooler .

Scheme 26. On the basis of Option 1, a control valve is further provided on the working fluid outlet.

According to the solution 26, further, the control valve is set to be pressure controlled, and the pressure control valve controls the pressure of the working fluid outlet in the closed loop of the working fluid to exceed a set value. The working fluid is exported when the limit is reached.

Solution 28. On the basis of the solution 26, further optionally, the pressure control valve is controlled by a control mechanism that causes a minimum pressure in the working fluid closed circuit to be greater than 0.2 MPa.

On the basis of the solution 26, further optionally, the control valve is controlled by an opening degree control mechanism, and the opening degree control mechanism controls the control valve according to a pressure setting range in the working fluid closed circuit. The degree of opening allows the working fluid outlet to be in a normally open state at a certain degree of opening.

According to the first aspect or the seventh aspect, the dual-channel entropy cycle engine further includes an auxiliary gas working mechanism, and the working fluid outlet is connected to the working fluid inlet of the auxiliary gas working mechanism. .

According to the first aspect or the seventh aspect, the two-channel entropy cycle engine further includes a gas storage tank, and the gas storage tank is in communication with the working fluid outlet.

Solution 32. On the basis of the solution 1, further optionally, a check valve is arranged on the communication passage.

The solution 33 is further selected, wherein the working fluid outlet of the piston gas working mechanism is upstream and the working fluid inlet of the piston gas compression mechanism is downstream. Another piston gas working mechanism is arranged on the closed circuit.

Solution 34. On the basis of the first or the third aspect, the piston gas working mechanism further outputs power to the piston gas compression mechanism.

Scheme 35. On the basis of the scheme 1, further optionally, in the closed circuit of the working fluid, a part of the gas participating in the circulation is non-condensable.

The solution 36 is further optional. The dual-channel entropy cycle engine further includes a non-condensable storage tank, and the non-condensable storage tank is connected to the working fluid closed circuit via a control device.

In a further aspect, the dual-channel entropy cycle engine further includes a non-condensable gas returning compressor, the air inlet of the non-condensing gas returning compressor and the working fluid The closed loop is in communication, and the gas outlet of the non-condensable gas returning compressor is in communication with the non-condensable gas storage tank.

Scheme 38. Based on the scheme 1, further optionally, a three-way catalyst is disposed in the closed loop of the working fluid. According to the solution 1, further, the angle between the cylinder center line of the piston gas compression mechanism and the cylinder center line of the piston gas working mechanism is less than 180 degrees, the piston Gas compression The piston of the book mechanism and the piston of the piston gas working mechanism are respectively connected to the same connecting rod journal of the same crankshaft via a connecting rod.

Solution 40. Based on the solution 39, further optionally, an angle between a cylinder center line of the piston type gas compression mechanism and a cylinder center line of the piston gas working mechanism is 90 degrees.

On the basis of the first aspect, the piston of the piston type gas compression mechanism and the piston of the piston type gas working mechanism are respectively connected to the different connecting rod journals on the same crankshaft via a connecting rod. The phase difference between the two connecting rod journals is greater than 0 degrees and less than 180 degrees.

In a further aspect, the dual-channel entropy cycle engine further includes a low-temperature cold source for providing a low-temperature substance, and the low-temperature substance is used for cooling the piston type. The working fluid in the gas compression mechanism or about to enter the piston gas compression mechanism.

On the basis of the first aspect, the dual-channel entropy cycle engine further includes a turbine power mechanism and an impeller compressor, and the working fluid outlet is connected to the working fluid inlet of the turbine power mechanism. The working fluid outlet of the turbine power mechanism is connected to the working fluid inlet of the impeller compressor via an auxiliary cooler, and the working fluid outlet of the impeller compressor is in communication with the working fluid closed circuit; An auxiliary working fluid outlet is disposed on the passage between the mass outlet and the working fluid inlet of the impeller compressor.

According to the solution 1, further, the dual-channel entropy cycle engine further includes a four-type door cylinder piston mechanism, and the air supply port of the four-type door cylinder piston mechanism and the working fluid closed circuit In communication, the refill port of the four-type door cylinder piston mechanism is in communication with the working fluid outlet.

Scheme 45. Based on the scheme 44, further optionally, the dual channel entropy cycle engine further includes an oxidant source, and the oxidant source is configured as the four types of door cylinder piston mechanism.

According to the solution 3, further, the side internal combustion combustion chamber is set as a four-type door cylinder piston mechanism, and the air supply port of the four types of door cylinder piston mechanism and the piston gas work The cylinders of the mechanism are in communication, and the refilling port of the four types of door cylinder piston mechanisms is in communication with the working fluid outlet.

In a further aspect, the dual-channel entropy cycle engine further includes an oxidant sensor and an oxidant control device, the oxidant sensor being disposed in the working fluid closed circuit, the oxidant sensor A signal is provided to the oxidant control device, the oxidant source being in communication with the working fluid closed circuit via an oxidant control valve, the oxidant control device controlling the oxidant control valve.

According to the first aspect, the piston gas compression mechanism is further configured as a piston liquid mechanism, and the piston liquid mechanism comprises a gas liquid cylinder and a gas-liquid isolation structure, wherein the gas-liquid isolation structure is Inside the gas-liquid cylinder.

According to the solution 1, further, the piston gas working mechanism is set as a piston liquid mechanism, and the piston liquid mechanism comprises a gas liquid cylinder and a gas-liquid isolation structure, wherein the gas-liquid isolation structure is Inside the gas-liquid cylinder.

In a further aspect, the gas working fluid of the gas-liquid cylinder has a pressure greater than the liquid in the gas-liquid cylinder and the gas-liquid liquid. Isolation of the isolation structure when doing reciprocating motion Explain the sum of the power of the book.

In a further aspect, based on the solution 1, the mass flow rate of the substance discharged from the internal combustion combustion chamber is greater than the mass flow rate of the substance introduced into the internal combustion combustion chamber from outside the closed circuit of the working medium.

Scheme 52. On the basis of the scheme 3, further, the mass flow rate of the working fluid flowing into the piston gas working mechanism is greater than the mass flow rate of the material discharged from the bypass internal combustion combustion chamber.

Programme 53. On the basis of Option 1, furthermore, the pressure-bearing capacity of the closed loop of the working fluid is greater than 2 MPa.

According to the solution 1, further, optionally, a regenerator is disposed on the communication passage, a working fluid outlet of the piston gas working mechanism and a working fluid inlet of the piston gas compression mechanism The communication passage between the two is set as the cooled fluid passage of the regenerator, and the communication passage between the working fluid outlet of the piston type gas compression mechanism and the working fluid inlet of the piston gas working mechanism is It is the heated fluid passage of the regenerator.

Solution 55. On the basis of the solution 1, further optionally, the internal combustion combustion chamber is disposed in the communication passage in the form of a separate cavity.

The principle of the present invention is: replacing the conventional hot air machine with the internal combustion combustion chamber (that is, introducing an oxidant, a fuel into a working fluid of a hot air machine that needs to be heated, and causing a combustion chemical reaction to increase the temperature of the working medium) The working fluid of all types of hot air compressors such as Stirling engine heats the heat exchanger, so that the temperature and pressure of the working fluid can reach a higher level, achieving the essential improvement of the efficiency and power density of the hot air machine, and can be greatly improved. Reduce the size, weight and manufacturing costs of the mechanism.

Using the internal combustion combustion chamber to perform internal combustion heating on the working fluid in the closed circuit of the working fluid, and pushing the piston of the piston gas working mechanism to perform external work, and realizing the work by guiding part of the working fluid from the closed loop of the working fluid In the closed loop, the working medium is balanced, and part of the heat can be derived while the working fluid in the closed circuit of the working fluid is derived; the function of the cooler and the regenerator in the present invention is compared with the traditional Stirling engine The function of the chiller and the regenerator is the same; the function of the condensing cooler in the present invention is to condense and liquefy part of the working fluid in the closed circuit, and to export it from the closed loop of the working fluid in the form of liquid, so that The working medium balance in the closed circuit of the working fluid can be realized, and the function of not discharging the gas to the environment can be realized, and the overall zero emission of the engine is formed.

In the present invention, the so-called accessory gas work mechanism refers to any mechanism that can generate power by gas working fluid expansion and/or flow, such as a piston gas work mechanism, an impeller gas work mechanism, a Roots gas work mechanism, etc. The function is to perform work by using the gas working medium in the high energy state in the two-channel entropy cycle engine.

In the present invention, the so-called communication passage means a passage through which the working fluid of the piston type gas compression mechanism and the piston type gas working mechanism communicate.

In the present invention, the working fluid in the closed circuit of the working fluid may be a flue gas formed by the combustion of the oxidant and the fuel, or a mixture of the flue gas and other gases previously stored, such as a mixture of flue gas and helium, and smoke. a mixture of gas and argon, and the like.

In the present invention, the working fluid closed circuit refers to a space in which the working fluid can circulate in the communication passage of the piston type gas compression mechanism and the piston type gas work mechanism and the communication. In the present invention, the internal combustion combustion chamber means that the high temperature product formed by the combustion chemical reaction between the oxidant and the fuel is directly used as a circulating working medium or mixed with other gases existing in the closed circuit of the working fluid as a circulating working medium. The combustion chamber.

In the present invention, the "internal combustion combustion chamber in the working fluid closed circuit" includes directly arranging the internal combustion combustion chamber in the working fluid closed circuit, and also includes the high temperature combustion product of the internal combustion combustion chamber. The structure in which the working fluid is closed in a loop, that is, the structure of the side-by-side internal combustion combustor.

In the present invention, the side-by-side internal combustion combustion chamber means that the internal combustion combustion chamber is an independent combustion space in which a passage is connected to the working fluid closed circuit.

In the present invention, the internal combustion combustion chamber may be an internal combustion continuous combustion chamber, an internal combustion intermittent combustion chamber or an internal combustion timing combustion chamber; the internal combustion continuous combustion chamber refers to an internal combustion combustion chamber in which an exothermic chemical reaction may continuously occur; The internal combustion intermittent combustion chamber refers to an internal combustion combustion chamber that does not continuously generate an exothermic chemical reaction, and the internal combustion intermittent combustion chamber may be a timing intermittent combustion chamber, and only occurs in the combustion chamber in each working cycle of the two-channel entropy circulation engine. An exothermic chemical reaction, the exothermic chemical reaction occurs only in one stroke; or may be a positive-time intermittent combustion chamber in which an exothermic chemical reaction occurs in a plurality of working cycles: or may be long In the timing intermittent combustion chamber, the two-channel entropy cycle engine continuously generates an exothermic chemical reaction in the combustion chamber in a plurality of working cycles.

In the present invention, the term "oxidant source" means a device, mechanism or storage tank which can supply an oxidant, and the oxidant in the oxidant source should have a higher pressure than the pressure in the internal combustion combustion chamber when entering the internal combustion combustion chamber.

In the present invention, the oxidizing agent refers to a substance which can react with a fuel in a liquid or high-pressure gas state, such as liquid oxygen, high-pressure oxygen, high-pressure compressed air, liquefied air, hydrogen peroxide, aqueous hydrogen peroxide, and the like. When the oxidant is in a liquid state, it is supplied by a high pressure liquid pump; when the oxidant is in a high pressure gas state, it can be directly fed in a high pressure form.

In the present invention, not only the oxidant should be supplied to the internal combustion combustion chamber but also the internal combustion combustion chamber should be supplied with fuel according to known techniques. The fuel source refers to a device, a mechanism or a storage tank that can provide fuel, and when the fuel in the fuel source enters the internal combustion combustion chamber, the pressure thereof should be higher than the pressure in the internal combustion combustion chamber, and the fuel is a substance capable of undergoing a combustion chemical reaction with an oxidant, such as a hydrocarbon, a carbon oxyhydroxide or a solid carbon; wherein the hydrocarbon includes gasoline, diesel, heavy oil, kerosene, aviation kerosene, and the like; The hydroxide includes methanol, ethanol, methyl ether, diethyl ether, etc.; the solid carbon has the advantages of high concentration of carbon dioxide in the product after combustion and combustion, and is easy to liquefy; the solid carbon can be pre-assembled, powdered and injected into the solid. Or powdered, and then injected into the hot air machine by fluidization of liquid or gaseous carbon dioxide.

In the present invention, the so-called working fluid outlet refers to the outlet of a part of the working fluid from the two-channel entropy circulating engine working fluid system, the purpose of which is to balance the excess of the introduced oxidant and reducing agent. The working fluid to maintain the balance of the dual channel entropy cycle engine working fluid system.

In the present invention, the working fluid outlet may be a continuous derivation working medium, and may be an intermittent derivation working medium (that is, the working medium is derivatized according to the working medium accumulated in the closed circuit of the working medium), or may be The working fluid is exported according to the timing relationship.

In the present invention, the derived working medium may be in each working cycle of the two-channel entropy cycle engine, the working fluid outlet When the pressure at the specification is low, the working medium is exported; or the working medium is derived at the timing, and the working is performed intermittently after the working pressure is low at the working outlet of the two-channel entropy cycle engine after multiple working cycles It is also possible to use a pressure limiting device such as a pressure limiting valve to derive the working medium when the pressure in the working fluid closed circuit exceeds a certain limit.

In the present invention, a control valve is provided on the working fluid outlet: the control valve is controlled by a peak pressure control mechanism, and the peak pressure control mechanism causes the pressure in the closed circuit of the working fluid to exceed a set value The control is wide open, and the control valve is closed when the pressure in the closed circuit drops back to the set value; or the control valve is controlled by the valley pressure control mechanism, and the working fluid is closed The control valve is opened when the pressure inside is in the valley pressure state, and the control is closed when the pressure in the working fluid closed circuit is to 0.2 MPa; or the control valve is controlled by the opening degree control mechanism, The opening degree control mechanism controls the opening degree of the control valve according to the pressure setting range in the working fluid closed circuit, so that the working fluid outlet is in a normally open state under a certain opening degree.

In the present invention, the working fluid in the closed loop of the working fluid may be derived in the form of a gas or may be derived in the form of a liquid.

In the present invention, the gas storage tank that communicates with the working fluid outlet can be used as a compressed gas source.

In the present invention, the cooler refers to any device capable of cooling the working fluid, such as a direct mixing type, a heat exchanger type, and a radiator type cooler. The direct-mixing cooler refers to a device that directly mixes a heated fluid with a cooled working fluid, and directly performs heat exchange to achieve working fluid cooling; the heat exchanger refers to a receiving medium that uses other fluids as heat. And a device for performing heat exchange with the working medium to reach a cooling medium; the heat sink is a device that uses an ambient gas as a heat receiving medium to diffuse the heat of the working medium into the environment to reach a cooling working medium. Wherein the heat exchanger and the heat sink are both non-direct mixed coolers, that is, the heated fluid is not mixed with the cooled working medium.

In the present invention, the condensing cooler comprises a direct mixing condensing cooler and a non-direct mixing condensing cooler, wherein the straight mixed condensing cooler means that the heated fluid and the cooled fluid are mixed therein to cause a portion of the cooled fluid to be generated or a device that condenses all of the temperature to heat the heated fluid; the non-direct mixed condensing cooler means having a heated fluid passage and a cooled fluid passage, the heated fluid in the heated fluid passage and the cooled fluid passage Means in which the cooled fluid is subjected to heat exchange but not mixed, such as a heat exchanger type and a radiator type condensing cooler; the non-direct mixed condensing cooler and the direct mixing condensing cooler may have when necessary The function of the gas-liquid separator.

In the present invention, the circulating gas in the working fluid closed circuit may be selected from the group consisting of argon gas, helium gas, oxygen gas and the like.

In the present invention, the term "non-condensable gas" means a gas which is not liquefied after being cooled in the two-channel entropy cycle engine by an inert gas, nitrogen gas or the like, and preferably the non-condensable gas is argon gas.

In the present invention, the function of providing the non-condensable gas returning compressor is to extract non-condensable gas from the working fluid closed circuit and store it in the non-condensable gas storage tank when the system is not operating.

In the present invention, the low-temperature cold source refers to a device, a mechanism or a storage tank capable of providing a low-temperature substance having a temperature below 0 ° C, for example, a storage tank stored with a low-temperature substance obtained by a commercially available method, the low-temperature substance may be It is liquid nitrogen, liquid oxygen, liquid helium or liquefied air. When the oxidizing agent in the present invention is liquid oxygen, liquid oxygen can be directly used as the low temperature substance.

In the present invention, the low-temperature cold source is directly connected to the working fluid closed circuit to mix the low-temperature substance with the working medium in the working fluid closed circuit, or to make the low-temperature substance through a heat exchange device In the closed loop with the working fluid The working medium heat exchange mode cools the working fluid in the piston type gas compression mechanism or is about to enter the piston type gas compression mechanism. The two-channel entropy cycle engine is a power mechanism with a working cycle close to the Carnot cycle. The calculation of the thermal efficiency can refer to the calculation formula of the Carnot cycle thermal efficiency: β ⁼ ' It can be seen that when the temperature of the cold source ⁷ decreases, the thermal efficiency increases. Moreover, the amount of heat discharged to the cold source is reduced. If the temperature of the cold source is greatly decreased, that is, the temperature of the cold source is low, the thermal efficiency ^{77 is} high, and the amount of heat discharged to the cold source is small. It is inferred that the cold source temperature ⁷ ^ can be greatly reduced by using a relatively low temperature low temperature substance, thereby greatly reducing the amount of heat discharged to the cold source and effectively improving the engine efficiency.

The lower the temperature, the lower the temperature (such as liquid oxygen, liquid nitrogen or liquid helium), the more energy is consumed in the manufacturing process, but in terms of unit mass, the contribution to the efficiency of the engine heat is greater, just like The storage of energy in a substance having a very low temperature corresponds to the concept of a novel battery which can be manufactured using a low-cost energy source such as garbage electricity, thereby effectively reducing the operating cost of the engine.

In the present invention, after the low-temperature substance in the low-temperature cold source exhibits a cooling action, it may be introduced into the working fluid closed circuit as a circulating medium of a two-channel entropy cycle engine, or may not be introduced into the working medium. In the loop.

In the present invention, the so-called two devices are in communication, meaning that the fluid can flow in one or two directions between the two devices. By communication is meant direct communication or indirect communication via a control mechanism, control unit or other control component.

Book

In the present invention, the four-type door cylinder piston mechanism means that an air inlet, an exhaust port, a gas supply port and a refill port are provided on the cylinder, and the air inlet, the exhaust port, and the supply port are provided The air port and the refill port are correspondingly arranged with a cylinder piston mechanism of an intake valve, an exhaust valve, a supply valve and a refill door.

In the present invention, the liquid oxygen includes commercial liquid oxygen or liquid oxygen prepared in the field.

In the present invention, by adjusting the working pressure of the working fluid closed circuit and the displacement of the hot end mechanism to control the mass displacement of the hot end mechanism, the mass flow rate Μ ₂ of the substance discharged from the internal combustion combustion chamber is greater than The mass flow rate M of the substance introduced into the internal combustion combustion chamber outside the closed circuit of the working fluid means that, in addition to the substance introduced into the internal combustion combustion chamber from the closed circuit of the working fluid, a part of the substance is from the working medium Introducing the internal combustion combustion chamber into the closed circuit, since the internal combustion combustion chamber is disposed in the working fluid closed circuit, that is, at least a portion of the material discharged from the internal combustion combustion chamber flows back to the internal combustion The combustion chamber, that is, the working medium has a reciprocating flow between the hot end mechanism and the cold end mechanism. The substance introduced from the outside of the working fluid closed circuit to the internal combustion combustion chamber may be an oxidant, a reducing agent, a compressed gas or a high temperature gas.

In the present invention, the hot end mechanism refers to a gas working mechanism in which the internal combustion combustion chamber is disposed, or a working medium generated in a combustion chemical reaction in the internal combustion combustion chamber first enters, for example, the piston gas. Work organization.

In the present invention, the cold end mechanism refers to a gas compression mechanism into which the working medium flows out from the hot end mechanism, for example, the piston type gas compression mechanism.

In the present invention, the oxidant sensor refers to a device that detects the content of the oxidant in the closed circuit of the working fluid. The oxidant sensor provides a signal to the oxidant control device, the oxidant control device according to a signal provided by the oxidant sensor and a preset static or dynamic oxidant content setting value in the working fluid closed circuit The oxidant control valve is controlled to increase or decrease the amount of oxidant supplied to the working fluid closed circuit for the purpose of regulating the content of the oxidant in the closed loop of the working fluid. The set value of the oxidant content in the specification may be a value or a numerical interval, for example: the oxidant content in the closed loop of the working fluid may be set at 5%, 10% or 10%~12%. Wait.

The oxidant sensor may be disposed on a closed circuit remote from the internal combustion combustion chamber to ensure that the entire working fluid closed circuit operates in an oxygen-rich (oxygen content greater than zero) state, so that the internal combustion combustion chamber is stable. Combustion of chemical reactions while preventing carbon deposits.

In the present invention, the gas-liquid cylinder refers to a container which can accommodate a gas working medium and/or a liquid and can withstand a certain pressure, and the gas-liquid cylinder is divided into a gas end and a liquid end by the gas-liquid separating structure. The gas end of the gas cylinder is provided with a gas working fluid circulation port for communicating with other devices or mechanisms in the closed circuit of the working fluid; the liquid end of the gas liquid cylinder is provided with a liquid A flow port for communicating with a hydraulic power mechanism and/or a liquid working fluid return system.

In the present invention, the gas-liquid insulation structure refers to a structure that can reciprocate in the gas-liquid cylinder, such as a separator, a separator, a piston, etc., and functions to isolate the gas in the gas-liquid cylinder. Preferably, the gas-liquid insulation structure and the gas-liquid cylinder are sealingly fitted. During the operation of the piston liquid mechanism, according to the gas-liquid isolation structure being at different positions in the gas-liquid cylinder, the gas-liquid cylinder may all be a gas working medium, or may be all liquid, or a gas worker. Both the substance and the liquid are present at the same time.

In the present invention, the liquid in the gas-liquid cylinder and the gas-liquid isolation structure are different from the conventional piston linkage mechanism, and the piston in the conventional piston linkage mechanism can be stopped by the thrust or pulling force of the connecting rod, thereby realizing Limiting the stroke of the piston, and in the gas-liquid cylinder, when the gas working fluid in the gas-liquid cylinder is doing positive work, the gas-liquid isolation structure is moved by the pressure to the bottom dead center, and the liquid is pressurized Forming the gas-liquid cylinder and pushing a hydraulic power mechanism (such as a liquid motor) to perform external work. When the liquid is about to be exhausted, changing the liquid motor working mode or starting the liquid working fluid returning system, so that the liquid in the gas-liquid cylinder is not Further reducing, at this time, the liquid applies a braking force to the gas-liquid insulation structure in the gas-liquid cylinder to stop it to prevent it from hitting the wall of the bottom of the liquid end of the gas-liquid cylinder; When the liquid is input into the cylinder, the gas-liquid isolation structure continuously moves toward the upper dead center, and when the vicinity of the top dead center is reached, the liquid is input into the gas cylinder or the liquid in the gas cylinder is stopped. Reducing (flowing out), however, the liquid in the gas-liquid cylinder and the gas-liquid isolation structure still move due to the inertia to the dead center direction, and at this time, if the gas working fluid in the gas-liquid cylinder is not sufficiently pressurized High, the gas-liquid isolation structure continues to move upwards and hits the wall of the top of the gas cylinder. In order to avoid such impact, the pressure of the gas working fluid in the gas-liquid cylinder needs to be sufficiently high to make the gas-liquid The pressure of the isolation structure is greater than the sum of the inertial forces of the liquid in the gas cylinder and the gas-liquid isolation structure during reciprocation.

In the present invention, the sum of the inertial forces of the liquid in the gas-liquid cylinder and the gas-liquid isolation structure during reciprocation during the operation of the two-channel entropy cycle engine is varied, and therefore should be It is ensured that at any working moment, the inertia of the gas working fluid in the gas-liquid cylinder to the gas-liquid isolation structure is greater than the inertia of the liquid in the gas-liquid cylinder and the gas-liquid isolation structure. The condition of the sum of forces is achieved, for example, by adjusting the working pressure in the closed circuit of the working fluid, adjusting the mass of the gas-liquid isolating structure, adjusting the density of the liquid, or adjusting the depth of the liquid, wherein the liquid depth refers to a liquid The depth of the liquid in the direction of reciprocation.

The so-called "adjusting the working pressure in the closed circuit of the working fluid" is to adjust the inflow and/or outflow of the working fluid. The volume flow rate of the gaseous working fluid of the combined circuit can be realized, for example, by adjusting the switching interval of the working fluid outlet, the time of each opening, and/or the opening opening size of the working fluid outlet. .

In the present invention, the position of the internal combustion combustion chamber and the cooler on the closed circuit of the working fluid should be set according to a well-known thermodynamic cycle.

In the present invention, the working fluid in the working fluid closed circuit needs to be subjected to compression, heating, temperature rising and boosting, work and cooling, which requires the working fluid closed circuit to withstand a certain pressure, optionally, The pressure capacity of the closed loop of the working fluid can be set to be greater than 2 MPa, 2.5 MPa, 3 MPa, 3.5 MPa, 4 MPa, 4.5 MPa, 5 MPa, 5.5 MPa, 6 MPa, 6.5 MPa, 7 MPa, 7.5 MPa > 8 MPa, 8.5 MPa, 9 MPa, 9.5. MPa, 10 MPa, 10.5 MPa, l lMPa, 11.5 MPa, 12 MPa, 12.5 MPa, 13 MPa, 13.5 MPa, 14 MPa, 14.5 MPa, 15 MPa, 15.5 MPa, 丽 Pa, 16.5 MPa, 17 MPa, 17.5 MPa, 18 MPa, 18.5 MPa, 19 MPa 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 more than 40MPa. Accordingly, the pressure bearing capacity of the oxidant source and the fuel source is also set to the same numerical range as described above.

In the present invention, the control valve is controlled by a minimum pressure in the closed circuit of the working fluid of more than 0.2 MPa, 0.3 MPa, 0.5 MPa, 1 MPa, 1.5 MPa, 2 MPa, 2.5 MPa, 3 MPa, 5 MPa, 8 MPa or more than 10 MPa. Controlled.

In the present invention, the piston type gas compression mechanism and the piston type gas work mechanism may not be wide, but rely on the phase difference between each other to form the compression and expansion work of the system.

The inventors propose a new way of clarifying the P-T diagram and the second law of thermodynamics as follows:

Pressure and temperature are the most basic and important state parameters of the working fluid. However, in the thermodynamic studies to date, P-T diagrams with pressure P and temperature T as coordinates have not been used in the study of thermodynamic processes and thermodynamic cycles. For more than two hundred years since the birth of thermodynamics, the inventors have for the first time proposed the idea of studying thermodynamic processes and thermodynamic cycles using P-T diagrams. In the study of thermodynamic processes and thermodynamic cycles using PT maps, the inventors have found that PT maps have obvious advantages over commonly used PV maps and τ-s maps, which can more fully describe the working conditions of thermodynamic processes and thermodynamic cycles. The changes have enabled the inventors to have a deeper understanding of thermodynamic processes and thermodynamic cycles. Using the PT diagram, the inventors summarized ten new ways of elaboration of the second law of thermodynamics. These new elaborations are equivalent to the previous methods of thermodynamics of Kelvin and Clausius, but more clearly reveal the work. The difference between the quality heating process and the compression process also points the way for the development of high-efficiency heat engines. This new method and new law will greatly promote the development of thermodynamics and the advancement of the heat engine industry. details as follows:

The PV map and the TS map have been widely used in thermodynamic research. However, since P and T are the most important state parameters of the working fluid, the inventors plotted the PT map with the pressure P and the temperature T as coordinates, and will take the Camot Cycle. And the Otto Cycle is identified in the PT diagram shown in FIG. Obviously, the PT map makes the changes in the working state of the thermodynamic process and the thermodynamic cycle more obvious, and makes the nature of the thermodynamic process and the thermodynamic cycle easier to understand. For example: The PT diagram of the Carnot Cycle shown in Figure 26 allows the inventors to easily conclude that the mission of the reversible adiabatic compression process of Carnot Cycle is to increase the temperature of the working fluid to a reversible adiabatic compression. The temperature of its high temperature heat source to achieve high temperature Explain that the temperature of the heat source of the book is consistent with the constant temperature endothermic expansion process from the high temperature heat source. Furthermore, the inventors can clearly see that when the temperature of the high temperature heat source of the Carnot Cycle rises, the inventors must compress the working medium to a deeper level in the reversible adiabatic compression process of the Carnot Cycle to make it higher. The temperature is reached to reach the temperature of the high-temperature heat source after the temperature rise, so as to achieve the constant temperature endothermic expansion process of the high-temperature heat source after self-heating on the premise of keeping the temperature of the high-temperature heat source after the temperature rise, thereby achieving efficiency.

According to the adiabatic process equation /» ₌ C ^ (where ^C is a constant, which is the adiabatic index of the working fluid), the inventors plotted the curves of the adiabatic process equations of different C values in Fig. 27. According to the mathematical analysis, and as shown in Fig. 27, any two adiabatic process curves do not intersect. This means that the process on the same adiabatic process curve is an adiabatic process, and the process of intersecting any adiabatic process curve is a non-adiabatic process. In other words, any process connecting two different adiabatic process curves is a non-adiabatic process (so-called A non-adiabatic process refers to a process with heat transfer, that is, an exothermic process and an endothermic process). In Fig. 28, the inventors have marked two state points, point A and point B. If a thermal process or a series of interconnected thermal processes arrives from point A to point B, the inventors refer to the process of connecting point A and point B, whereas the inventors refer to the process of connecting point B and point A. According to Fig. 28, the inventors can conclude that if point B is on the adiabatic process curve where point A is located, the process of connecting point A and point B is an adiabatic process; if point B is at point A On the right side of the adiabatic process curve, the process of connecting point A and point B is an endothermic process; if point B is to the left of the adiabatic process curve where point A is located, the process of connecting point A and point B is an exothermic process. Since the process of connecting the point A and the point B may be an exothermic process, an adiabatic process or an endothermic process, the inventors have defined point A as having a surplus temperature, an ideal temperature, and an insufficient temperature, respectively, with reference to point B. Similarly, the process of connecting point B and point A may be an exothermic process, an adiabatic process or an endothermic process, so the inventors have defined point B as having an excess temperature, an ideal temperature, and an insufficient temperature, respectively, with reference to point A.

Through these analyses and definitions, the inventors have come up with the following ten new ways of clarifying the second law of thermodynamics:

1. Without the participation of the endothermic process, it is impossible to restore the exothermic process to its starting point.

2. Without the participation of the exothermic process, it is impossible to restore the endothermic process to its starting point.

3. Without the participation of non-adiabatic processes, it is impossible to restore the non-adiabatic process to its starting point.

4. It is impossible to restore the non-adiabatic process to its starting point using only the adiabatic process.

5. When the pressure of the endothermic process is restored to the pressure at the starting point by a thermal process other than the exothermic process, the temperature must be higher than the temperature at the starting point.

6. When the pressure of the exothermic process is restored to the pressure at the starting point by a thermal process other than the endothermic process, the temperature must be lower than the temperature at the starting point.

7. It is impossible for the endothermic process to not generate excess temperature.

8. The exothermic process is unlikely to produce insufficient temperature.

9. The efficiency of any heat engine that does not exotherm during compression cannot achieve the efficiency of the Carnot cycle.

10. The difference between the heating process of the working fluid and the compression process of the working fluid is that the heating process must generate excess temperature, but the compression process is not.

The ten new ways of elaboration on the second law of thermodynamics are equivalent and can also be proved by mathematics. Any of the ways in which the book is described can be used separately. The inventors suggest that: In the process of thermodynamics research, the PT diagram and the above-mentioned new elaboration method for the second law of thermodynamics should be widely applied. The PT diagram and the new elaboration of the second law of thermodynamics are of great significance for the advancement of thermodynamics and the development of high-efficiency heat engines.

The English expression of the new elaboration 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.

If the final pressure of the 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.

It is impossible to make heat injection process not generate excess-temperature. 8. It is impossible to make heat rejection process not generate excess-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.

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, necessary components, units or systems are provided where necessary in accordance with known techniques in the field of thermal energy and power.

The beneficial effects of the present invention are as follows:

The invention replaces the external combustion heating mode of the traditional hot air machine by using the internal combustion heating mode, and applies the direct heating of the internal combustion heating mode to the hot air machine, thereby overcoming the temperature and pressure of the working medium due to the difficulty of the conventional hot air machine. The higher level affects the power and power density, which can effectively save energy and greatly reduce the size, weight and manufacturing cost of the mechanism, and has broad application prospects.

DRAWINGS

1 is a schematic structural view of Embodiment 1 of the present invention;

2 is a schematic structural view of Embodiment 2 of the present invention; Figure 3 is a schematic structural view of Embodiment 3 of the present invention;

Figure 4 is a schematic structural view of Embodiment 4 of the present invention;

Figure 5 is a schematic view showing the structure of Embodiment 5 of the present invention;

Figure 6 is a schematic view showing the structure of Embodiment 6 of the present invention;

Figure 7 is a schematic view showing the structure of Embodiment 7 of the present invention;

Figure 8 is a schematic view showing the structure of Embodiment 8 of the present invention;

Figure 9 is a schematic view showing the structure of Embodiment 9 of the present invention;

Figure 10 is a schematic view showing the structure of an embodiment of the present invention 10;

Figure 11 is a schematic structural view of Embodiment 11 of the present invention;

Figure 12 is a schematic view showing the structure of Embodiment 12 of the present invention;

Figure 13 is a schematic view showing the structure of Embodiment 13 of the present invention;

Figure 14 is a schematic view showing the structure of Embodiment 14 of the present invention;

Figure 15 is a schematic view showing the structure of Embodiment 15 of the present invention;

Figure 16 is a schematic view showing the structure of Embodiment 16 of the present invention;

Book

Figure 17 is a schematic view showing the structure of Embodiment 17 of the present invention;

Figure 18 is a schematic view showing the structure of Embodiment 18 of the present invention;

Figure 19 is a schematic view showing the structure of Embodiment 19 of the present invention;

Figure 20 is a schematic view showing the structure of Embodiment 20 of the present invention;

Figure 21 is a schematic view showing the structure of Embodiment 21 of the present invention;

Figure 22 is a schematic view showing the structure of Embodiment 22 of the present invention;

Figure 23 is a schematic view showing the structure of Embodiment 23 of the present invention;

Figure 24 is a schematic view showing the structure of Embodiment 24 of the present invention;

Figure 25 is a schematic view showing the structure of Embodiment 25 of the present invention;

Figure 26 shows the PT diagram of the Carnot cycle and the Alto cycle, where , ^e i and ^e ₂ are constants of different values, which are adiabatic indices, and cycles 0-2-3-0 are Carnot cycles, cycles 0-1-4-5-0 is the Carnot cycle after the temperature of the high temperature heat source rises, and the cycle 0-6-7-8-0 is the Alto cycle;

Figure 27 shows a PT diagram of a plurality of different adiabatic process curves, where ^C ', ^ ² , 3 , and are constants of different values, are adiabatic indices, and A and B are state points;

Figure 28 shows the P-T diagram of the adiabatic process curve, where C is a constant, is the adiabatic index, and A and B are the state points.

In the picture:

1 communication channel, 3 internal combustion combustion chamber, 4 oxidant source, 5 fuel source, 6 working fluid outlet, 7 reverse valve wide, 9 piston gas compression mechanism, 10 piston gas working mechanism, 13 impeller compressor, 14 turbine power Mechanism, 15 spark plugs, 16 cryogenic liquid working fluid storage tanks, 17 control valves, 18 non-direct mixing condensing coolers, 19 straight mixing condensing coolers, 20 gas-liquid direct mixing coolers, 21 radiators, 21 1 subsidiary coolers 22 adsorption chillers, 23 non-direct mixing chillers, 30 heat exchangers, Instruction manual

31 side internal combustion combustion chamber, 33 regenerator, 51 oxidant sensor, 52 oxidant control unit, 53 oxidant control wide, 60 gas storage tank, 61 cooling liquid discharge port, 62 cryogenic liquid discharge port, 64 liquid carbon dioxide outlet, 66 Auxiliary working fluid outlet, 70 non-condensable storage tank, 71 non-condensable gas storage compressor, 72 non-condensable gas recovery compressor, 77 crankcase, 81 condensing cooling liquid outlet, 82 non-condensing gas outlet, 88 three-way catalysis , 90 piston liquid mechanism, 91 gas cylinder, 92 gas-liquid isolation structure, 96 hydraulic power mechanism, 97 liquid working fluid return system, 98 process control mechanism, 99 four-class door cylinder piston mechanism, 991 air inlet, 992 row Air port, 993 air supply port, 994 refill port, 100 direct connection channel, 102 accessory gas work mechanism.

detailed description

Example 1

The two-channel entropy cycle engine shown in FIG. 1 includes a piston gas compression mechanism 9, a piston gas work mechanism 10, and two communication passages 1, and the working fluid outlet of the piston gas compression mechanism 9 passes through the communication. The passage 1 is in communication with the working fluid inlet of the piston gas working mechanism 10, and the working fluid outlet of the piston gas working mechanism 10 passes through the working fluid inlet of the other communication passage 1 and the piston gas compression mechanism 9. Connected; the piston-type gas compression mechanism 9 communicates with the piston-type gas work mechanism 10 via the two communication passages 1 to form a working fluid closed circuit; the working fluid outlet of the piston-type gas compression mechanism 9 and the An internal combustion combustion chamber 3 is disposed on the communication passage 1 between the working fluid inlets of the piston gas working mechanism 10, and the working fluid outlet of the piston gas working mechanism 10 and the working inlet of the piston gas compression mechanism 9 A working fluid outlet 6 is disposed in the communication passage 1 between the two, and a control valve 17 is disposed on the working fluid outlet 6.

In the specific implementation of the present invention, necessary components, units or systems should be provided where necessary according to known techniques, such as providing an oxidant inlet, a reducing agent inlet and a spark plug 15 on the internal combustion combustion chamber 3, and corresponding oxidant sources. 4 and the fuel source 5 is in communication with the internal combustion combustion chamber 3, and correspondingly, the oxidant in the oxidant source 4 may be air, and the fuel in the fuel source 5 is gasoline.

In order to facilitate the discharge of excess working fluid in the working fluid closed circuit, the working fluid derived from the working fluid outlet 6 may be a gas or a liquid, and the working fluid outlet 6 discharges the working medium while carrying out the working part. Heat.

In a specific implementation, the control valve 17 can be set as a pressure control valve, and the working fluid portion that causes the excessive pressure is led to close the working fluid.

As an alternative embodiment, the internal combustion combustion chamber 3 may be disposed at any other position within the working fluid closed circuit, and is preferably disposed upstream of the working fluid outlet of the piston gas compression mechanism 9. And in the working fluid closed loop which is downstream of the working fluid outlet of the piston gas working mechanism 10; the working fluid outlet 6 may be disposed at any other position in the closed circuit of the working fluid, preferably It is disposed on the working fluid closed circuit upstream of the working fluid outlet of the piston gas working mechanism 10 and downstream of the working fluid inlet of the internal combustion combustion chamber 3; the control valve 17 may not be provided.

The working process of the product of the present embodiment: an oxidant and a fuel respectively supplied from the oxidant source 4 and the fuel source 5, a combustion reaction occurs in the internal combustion combustion chamber 3, and the combustion into the internal combustion combustion chamber 3 The original gaseous working medium in the closed circuit of the working medium is heated, and simultaneously enters the living along the communication channel 1 together with the product produced by the combustion. The plug gas working mechanism 10 outputs external power; the working fluid after the work is discharged through the piston gas work mechanism 10, and then enters the piston gas compression mechanism 9 via another communication passage 1 to be compressed. The compressed gas working medium is returned to the internal combustion combustion chamber 3 via the working fluid outlet of the piston type gas compression mechanism, and is heated according to the cycle; wherein when the working fluid closes the circuit, the pressure is too large, The working fluid outlet 6 leads to a part of the working fluid.

In a specific implementation, the oxidant in the oxidant source 4 may also be set as liquid oxygen, high pressure oxygen, high pressure compressed air, liquid air, hydrogen peroxide, aqueous hydrogen peroxide solution, etc.; the fuel in the fuel source 5 may also be set For diesel, heavy oil, kerosene, aviation kerosene, methanol, ethanol, methyl ether, ether, etc.

Example 2

The two-channel entropy cycle engine shown in FIG. 2 differs from the embodiment 1 in that: the two-channel entropy cycle engine further includes a cooler, the cooler is configured as a radiator 21, and the radiator 21 is disposed at The communication channel between the working fluid outlet of the piston gas working mechanism 10 and the working fluid inlet of the piston gas compression mechanism 9 may be used as liquid oxygen in the oxidant source 4; The working fluid outlet 6 is disposed on the communication passage 1 between the working fluid outlet of the piston type gas compression mechanism 9 and the working inlet of the internal combustion combustion chamber 3, and the working fluid outlet 6 is controlled to be 17 and stored. The gas tank 60 is connected, the gas storage tank 60 is for storing high pressure gas and non-condensable gas, the fuel source 5 and the scattered gas

Book

The degree of cooling of the working medium by the heater 21 determines the type and state of the derived working medium. When the fuel is set to hydrogen, the derived working medium may be gaseous or liquid water, or a mixture thereof with a gas in a closed loop; In the case of a hydrocarbon, the derived working fluid further contains other products such as carbon dioxide, and the circulating gas in the closed circuit of the working fluid is set to helium.

The piston of the piston type gas compression mechanism 9 and the piston of the piston type gas work mechanism 10 are respectively connected via a connecting rod and a different connecting rod journal on the same crankshaft, and the phase difference between the two connecting rod journals is 90 degree.

In a specific implementation, the control valve 17 can be selectively set as a pressure control valve, and the control valve 17 is controlled by a peak pressure control mechanism, and the pressure of the peak pressure control mechanism in the working fluid closed circuit exceeds Setting the value to open the control block 17 and closing the control valve 17 when the pressure in the closed circuit drops back to the set value; or subjecting the control valve 17 to the valley pressure control mechanism Controlling that the control valve 17 is opened when the pressure in the working fluid closed circuit is in a valley pressure state, and the control valve 17 is closed when the pressure in the working fluid closed circuit is to 0.2 MPa; or The control valve 17 is controlled by an opening degree control mechanism, and the opening degree control mechanism controls the opening degree of the control valve 17 according to a pressure setting range in the working fluid closed circuit to make the working fluid outlet 6 In a normally open state at a certain degree of opening; alternatively, the pressure in the closed circuit of the working fluid is set to be greater than 0.3 MPa, 0.5 MPa, 1 MPa, 1.5 MPa, 2 MPa, 2.5 MPa, 3 MPa, 5 MPa, 8 MPa or greater 10 MPa.

As an alternative embodiment, the cooler may be configured as another type of cooler, such as a heat exchanger cooler; the cooler may also be disposed at any other location of the working fluid closed circuit; The cooler and the gas storage tank 60 may be alternatively disposed; the control valve 17 may not be provided.

Alternatively, the phase difference between the two connecting rod journals may be set to any value in a range of more than 0 degrees and less than 180 degrees; or the piston of the piston type gas compression mechanism 9 and the piston gas working mechanism The pistons of 10 can be connected to the same connecting rod journal of the same crankshaft via the connecting rods respectively. At this time, the angle between the cylinder center lines of the two cylinders should be set to be less than 180 degrees. In all embodiments of the present invention, the connection relationship between the piston of the piston type gas compression mechanism 9 and the piston and the crankshaft of the piston gas work mechanism 10 can be set with reference to the embodiment and its transformable embodiment. And of course, in all embodiments of the present invention, including the embodiment, the piston of the piston type gas compression mechanism 9 and the piston of the piston gas work mechanism 10 and the crankshaft may be in other connection relationship; In all of the alternative embodiments of the embodiment in which the control valve 17 is provided, the control valve 17 can be controlled by the peak pressure control mechanism, controlled by the valley pressure control mechanism, or controlled by the opening degree control mechanism with reference to the present embodiment. .

In the embodiment in which all of the working fluid outlets 6 of the present invention are not connected to other devices, the working fluid outlet 6 may be in communication with the gas storage tank 60 with reference to the present embodiment.

Example 3

The two-channel entropy cycle engine shown in FIG. 3 differs from the embodiment 1 in that: the two-channel entropy cycle engine further includes a cooler, the cooler is configured as a radiator 21, and the radiator 21 is disposed at The piston of the piston type gas compression mechanism 9 is on the cylinder.

In a specific implementation, the heat sink 21 may also be disposed on the communication channel 1 at the working fluid outlet of the piston gas compression mechanism 9; the internal combustion combustion chamber 3 may also be disposed in the In the cylinder of the piston gas working mechanism 10, the working fluid flowing out of the internal combustion combustion chamber 3 is a working medium in a high energy state, and the purpose is to directly work by using the working medium in a high energy state.

Example 4

The two-channel entropy cycle engine shown in FIG. 4 differs from Embodiment 1 in that: the two-channel entropy cycle engine further includes a cooler, and the cooler is set as a gas-liquid direct charge cooler 20, the gas The liquid direct mixing cooler 20 is disposed on a communication passage between the working fluid outlet of the piston type gas working mechanism 10 and the working fluid inlet of the piston type gas compression mechanism 9, and the internal combustion combustion chamber 3 is disposed adjacent to The internal combustion combustion chamber 31 is provided with a check width 7 on the communication passage 1 between the working fluid outlet of the piston type gas compression mechanism 9 and the side internal combustion combustion chamber 31, thereby causing the piston gas to be The working fluid flowing out of the compression mechanism 9 is heated by the side internal combustion combustion chamber 31 and flows to the piston gas working mechanism 10.

In the present invention, the so-called gas-liquid direct-mixing cooler 20 means that a cooling liquid introduction port and a discharge port are provided on the closed circuit of the working fluid, and the principle is to absorb the gas in the closed circuit of the working fluid by using the introduced liquid. The heat is cooled and cooled, and the heated liquid is further discharged from the closed loop of the working fluid; a gas-liquid separator can be used for exporting to prevent the gas working fluid from flowing out.

As an alternative embodiment, the gas-liquid direct mixing cooler 20 and the backstop 7 may alternatively be provided; the cooler may be provided as another type of cooler.

In all of the embodiments of the present invention, the internal combustion combustion chamber 3 can be referred to as the side combustion chamber 31 with reference to the present embodiment.

Example 5

The two-channel entropy cycle engine shown in FIG. 5 differs from the third embodiment in that: the radiator 21 is modified in the working fluid outlet of the piston gas working mechanism 10 and the piston gas compression mechanism 9 Between the entrances of the working fluids In the communication passage 1, the internal combustion combustion chamber 3 is disposed in a cylinder of the piston gas working mechanism 10, and the working fluid outlet 6 is disposed in the radiator 21 and the piston type gas compression mechanism The communication channel 1 between the working fluid inlets of the nine, the dual channel entropy cycle engine further includes a non-direct mixing condensing cooler 18, the working fluid outlet 6 and the non-direct mixing condensing cooler 18 Connected to the cooling medium inlet, a cryogenic liquid discharge port 62 is disposed on the non-direct mixed condensing cooler 18, and the cryogenic liquid discharge port 62 communicates with the cryogenic liquid working fluid storage tank 16, the non-direct mixing The condensing cooler 18 further cools the working fluid flowing out of the piston gas working mechanism 10 and cooled by the radiator 21, and the generated gas liquefied material (such as liquid carbon dioxide, etc.) is stored in the cryogenic liquid working fluid storage tank. In the above, at this time, the refrigerant of the non-direct mixed condensing cooler 18 is liquid oxygen liquid nitrogen or the like having a low condensation temperature.

As an alternative embodiment, the cryogenic liquid working fluid storage tank 16 may not be provided; the cryogenic liquid discharge port 62 may not be provided.

In the embodiment in which all of the working fluid outlets 6 of the present invention are not connected to other devices, the non-direct mixed condensing cooler 18 and its related structure may be provided with reference to the present embodiment.

Example 6

The two-channel entropy cycle engine shown in FIG. 6 differs from the embodiment 5 in that the cryogenic liquid working fluid storage tank 16 is eliminated, and the internal combustion combustion chamber 3 is modified in the piston type gas compression mechanism. A non-condensing gas outlet 82 is added to the non-direct mixed condensing cooler 18 on the communication passage 1 between the working fluid outlet of the piston and the working fluid inlet of the piston gas working mechanism 10, the oxidant source 4 via the heated fluid passage of the non-direct mixing condensing cooler 18 in communication with the internal combustion combustion chamber 3, the oxidant acting as a refrigerant for the non-direct mixing condensing cooler 18, thereby effecting the working fluid outlet 6 The working fluid coming out is further cooled. The working medium cooled by the non-direct mixed condensing cooler 18 is partially cooled to flow out of the condensed cooling liquid outlet 81, and the other part is cooled, and is still in the form of gas, which is non-condensable. The non-condensable gas flows out from the non-condensable gas outlet 82.

In a specific implementation, optionally, the cryogenic liquid discharge port 62 is in communication with a cryogenic liquid working fluid storage tank 16 for storing a gas liquefaction; the non-condensing gas outlet 82 is in communication with the non-condensable gas storage tank 70 for storing non-condensable gas, or the non-condensable gas outlet 82 is in communication with the piston type gas compression mechanism 9, and the non-condensable gas is further compressed. Re-entering the working fluid closed circuit, or the non-condensing gas outlet 82 may also be in communication with any other position of the working fluid closed circuit, as long as the non-condensable gas can be returned to the working fluid closed circuit.

Example 7

The two-channel entropy cycle engine shown in FIG. 7 differs from the embodiment 3 in that the cooler is relocated to the working fluid outlet 6 and the working inlet of the piston gas working mechanism 10. Between the communication passages 1, and two, that is, a non-direct mixing cooler 23 as the cooler is added, and the oxidant source 4 passes through the heated fluid passage of the non-direct mixing cooler 23. It is in communication with the internal combustion combustion chamber 3.

As an alternative embodiment, the heated fluid passage of the non-direct mixing cooler 23 may not be in communication with the oxidant source 4; the oxidant source 4 may be in direct communication with the internal combustion chamber 3.

Example 8

The two-channel entropy cycle engine shown in FIG. 8 differs from the embodiment 7 in that: the radiator 21 and the Description The communication passage 1 between the non-direct mixing condensing coolers 18 is provided with a cooling liquid discharge port 61, and the non-direct mixing cooler 23 is provided with a cryogenic liquid discharge port 62.

After the working medium is cooled by the radiator, a substance having a higher condensation temperature (such as water) has been condensed, and can be discharged from the cooling liquid discharge port 61 in a liquid form; the working medium which is not easily condensed is in the non-straight The mixed condensing cooler 18 is further cooled, and the liquefied working medium after being cooled is discharged through the cryogenic liquid discharge port 62. The working fluid outlet 6 corresponds to a discharge port including the cooling liquid discharge port 61 and the cryogenic liquid discharge port 62.

Example 9

The two-channel entropy cycle engine shown in FIG. 9 differs from Embodiment 3 in that: the two-channel entropy cycle engine further includes a direct connection passage 100, and the direct connection passage 100 communicates with the piston gas work mechanism 10 The working fluid outlet is connected to the working fluid inlet of the piston compression mechanism 9, and the direct connecting passage 100 is equivalent to the working fluid outlet of the piston gas working mechanism 10 and the working fluid inlet of the piston compression mechanism 9. The communication passage 1 is divided into two branches, one of which is provided with a cooler (partial communication passage provided with a cooler), and the other branch (directly connected to the passage 100) is not provided. The cooler is provided with a control width 17 for controlling the opening and closing of the two branches.

The function of the direct connection channel 100 is: when the temperature of the working fluid flowing out from the working fluid outlet of the piston gas working mechanism 10 is low, the control width 17 on the direct connection channel 100 is opened. The control valve 17 on the communication passage 1 is closed, and the working fluid can flow through the direct connection passage 100 to the cylinder of the piston type gas compression mechanism 9; when working from the piston gas working mechanism 10 The temperature of the working fluid flowing out of the mass outlet is high, and when the cooling is required to be cooled by the cooler, the control valve 17 on the direct connecting passage 100 is closed, the control valve 17 on the communication passage 1 is opened, and the working medium is connected. The passage 1 flows into the cylinder of the piston type gas compression mechanism 9.

Example 10

The two-channel entropy cycle engine shown in FIG. 10 differs from the third embodiment in that: the heat sink 21 is modified in the working fluid outlet of the piston gas working mechanism 10 and the piston gas compression mechanism 9 The communication passage 1 between the working fluid inlets is provided on the communication passage 1 between the working fluid outlet of the piston gas working mechanism 10 and the working fluid inlet of the piston gas compression mechanism. A piston type gas working mechanism 10; because of the high working energy of the gas working medium after one work, the work can be continued, and the two piston type gas working mechanisms 10 can be arranged in series to improve the efficiency of the engine.

Example 11

The two-channel entropy cycle engine shown in FIG. 11 differs from the third embodiment in that: the radiator 21 is modified in the working fluid outlet of the piston gas working mechanism 10 and the piston gas compression mechanism 9 On the communication passage 1 between the working fluid inlets, the oxidant source 4 communicates with the communication passage 1 between the radiator 21 and the working inlet of the piston gas compression mechanism 9 via an oxidant inlet, a cooling liquid discharge port 61 is provided on the communication passage 1 between the radiator 21 and the oxidant inlet, and a liquid is provided on the communication passage 1 of the oxidant inlet and the piston type gas compression mechanism 9. A carbon dioxide outlet 64 for further cooling the working fluid in the communication passage 1. — 垦L υ ^ if

Description Book Example 12

The two-channel entropy cycle engine shown in FIG. 12 differs from the embodiment 6 in that: in the working fluid closed circuit, the gas participating in the cycle contains argon gas, and the two-channel entropy cycle engine further includes non-condensing. The gas storage tank 70, the non-condensing gas outlet 82 of the non-direct mixing condensing cooler 18 is connected to the non-condensable gas storage tank 70 via a control valve 17, and the non-condensable gas storage tank 70 and the working fluid closed circuit Connected.

As an alternative embodiment, the control valve 17 can be modified to any other suitable control device. Example 13

The two-channel entropy cycle engine shown in FIG. 13 differs from the third embodiment in that: the radiator 21 is modified in the working fluid outlet of the piston gas working mechanism 10 and the piston gas compression mechanism 9 The communication channel 1 between the working fluid inlets further includes a non-condensing gas returning compressor 71, and the air inlet of the non-condensing gas returning compressor 71 passes through the control valve 17 and the The working fluid is in closed loop communication, and the gas outlet of the non-condensable gas returning compressor 71 is in communication with the non-condensable gas storage tank 70, and the non-condensable gas storage tank 70 is in communication with the working fluid closed circuit.

As an alternative embodiment, the control valve 17 can be modified to any other suitable control device; the non-condensable return storage compressor 71 can be omitted.

Example 14

The two-channel entropy cycle engine shown in FIG. 14 differs from the first embodiment in that: a regenerator 33 is provided on the communication passage 1, and the regenerator 33 is a heat exchange regenerator, The communication passage 1 between the working fluid outlet of the piston type gas working mechanism 10 and the working medium inlet of the piston type gas compression mechanism 9 is set as the cooled fluid passage of the regenerator 33, the piston gas The communication passage 1 between the working fluid outlet of the compression mechanism 9 and the working fluid inlet of the piston gas working mechanism 10 is set as the heated fluid passage of the regenerator 33.

Example 15

The dual-channel entropy cycle engine shown in FIG. 15 differs from the embodiment 4 in that the dual-channel entropy cycle engine further includes an auxiliary gas work mechanism 102, and the auxiliary gas work mechanism 102 is set as a piston gas work mechanism. The working fluid outlet 6 communicates with the inlet of the auxiliary gas working mechanism 102. The working fluid derived from the working fluid outlet 6 is also in a high temperature and high pressure state, and the piston gas working mechanism can be pushed to continue work.

Alternatively, the auxiliary gas working mechanism 102 may be a gas working mechanism such as a Roots gas working mechanism, a screw gas working mechanism or a power turbine.

Example 16

The two-channel entropy cycle engine shown in FIG. 16 differs from the third embodiment in that: the radiator 21 is modified in the working fluid outlet of the piston gas working mechanism 10 and the piston gas compression mechanism 9 On the communication passage 1 between the working fluid inlets, the working fluid outlet 6 is modified between the radiator 21 and the working fluid outlet of the piston gas working mechanism 10 The dual-channel entropy cycle engine further includes a direct-mix condensing cooler 19, the cooled fluid inlet of the direct-mix condensing cooler 19 is in communication with the working fluid outlet 6, the oxidant source 4 and the straight The heated condensing cooler 19 is connected to the heated fluid inlet, and the direct mixing condensing cooler 19 is provided with a cryogenic liquid discharge port 62, and the cryogenic liquid discharge port 62 communicates with the cryogenic liquid working fluid storage tank 16 Straight-mixed condensing cooler 19 The description is provided with a non-condensing gas outlet 82, which is in communication with the working fluid closed circuit. An oxidant and non-condensable gas are introduced into the working fluid closed circuit via the non-condensable gas outlet 82, optionally into the internal combustion combustion chamber 3.

In this embodiment, the heated fluid outlet of the direct mixing condensing cooler, 19 is set as the non-condensing gas outlet 82, that is, the oxidant source 4 passes through the heated fluid outlet of the direct mixing condensing cooler 19. It is in communication with the internal combustion combustion chamber 3.

As an alternative embodiment, the heated fluid outlet of the direct mixing condensing cooler 19 may be separated from the non-condensable gas outlet 82, and connected to the working fluid closed circuit via the non-condensing gas outlet 82. .

Example 17

The two-channel entropy cycle engine shown in FIG. 17 differs from the embodiment 3 in that: the cooler is modified in the working fluid outlet of the piston gas working mechanism 10 and the piston gas compression mechanism 9 On the communication channel 1 between the working fluid inlets, and the cooler is changed to an adsorption cooler 22, the working fluid outlet of the piston gas working mechanism 10 and the piston gas compression mechanism 9 The communication passage 1 between the working fluid inlets is set as the cooled fluid passage of the adsorption cooler 22.

Example 18

The two-channel entropy cycle engine shown in FIG. 18 differs from the third embodiment in that: the internal combustion combustion chamber 3 is disposed in the communication passage 1 in the form of a separate cavity to ensure that the working fluid burns more. The stability is smoother, and a three-way catalyst 88 is disposed in the communication passage 1 between the internal combustion combustion chamber 3 and the working fluid inlet of the piston gas working mechanism 10.

In all embodiments of the present invention, the internal combustion combustion chamber 3 may be disposed in the communication passage 1 in the form of a separate cavity with reference to the present embodiment.

Example 19

The two-channel entropy cycle engine shown in Fig. 19 differs from the embodiment 3 in that between the working fluid outlet of the piston gas working mechanism 10 and the working fluid inlet of the piston gas compression mechanism 9. A three-way catalyst 88 is disposed in the communication passage 1 .

Example 20

The two-channel entropy cycle engine shown in FIG. 20 differs from the first embodiment in that: the two-channel entropy cycle engine further includes a low-temperature cold source 50, the low-temperature cold source 50 and the piston-type gas compression mechanism 9 In connection, the cryogenic cold source 50 is for providing a low temperature substance for cooling the working fluid of the piston type gas compression mechanism 9, and the low temperature substance of the low temperature cold source 50 is set to liquid nitrogen.

In a specific implementation, the low temperature cold source 50 may also be connected to a communication channel between the working fluid outlet of the piston gas working mechanism 10 and the working fluid inlet of the piston gas compression mechanism 9 . The cryogenic material is provided for cooling the working fluid that is about to enter the piston gas compression mechanism 9; the cryogenic cold source 50 may also be heat exchanged to the working fluid in the piston gas compression mechanism 9 or The working fluid that is about to enter the piston type gas compression mechanism 9 is cooled.

Example 21

The two-channel entropy cycle engine shown in FIG. 21 differs from Embodiment 1 in that: the two-channel entropy cyclic transmission Description

The motive further includes a radiator 21, a turbine power mechanism 14 and an impeller compressor 13, the radiator 21 being disposed at a working fluid outlet of the piston gas working mechanism 10 and a working fluid inlet of the piston gas compression mechanism 9. The working fluid outlet 6 communicates with the working fluid inlet of the turbine power mechanism 14 , and the working fluid outlet of the turbine power mechanism 14 is compressed by the auxiliary cooler 21 1 and the impeller. The working fluid inlet of the machine 13 is in communication, and the working fluid outlet of the impeller compressor 13 is in communication with the communication passage 1; between the working fluid outlet of the turbine power mechanism 14 and the working fluid inlet of the impeller compressor 13 An auxiliary working fluid outlet 66 is provided on the passage.

The auxiliary working fluid outlet 66 shown in the drawing is provided on the passage between the auxiliary cooler 21 1 and the working inlet of the impeller compressor 13.

In a specific implementation, optionally, the turbine power mechanism 14 may be coaxially disposed with the impeller compressor 13 and output power thereto; the auxiliary working fluid outlet 66 may also be disposed at the turbine power mechanism 14 a working medium outlet and a passage between the auxiliary cooler 21 1; a working fluid outlet of the impeller compressor 13 communicates with a communication port provided on the closed circuit of the working fluid, the communication port and the working The mass outlets 6 are disposed at different locations on the closed circuit of the working fluid.

Example 22

The two-channel entropy cycle engine shown in FIG. 22 differs from the third embodiment in that: the radiator 21 is modified in the working fluid outlet of the piston gas working mechanism 10 and the piston gas compression mechanism 9 On the communication passage 1 between the working fluid inlets, the working fluid outlet 6 is modified on a communication passage between the working fluid outlet of the piston gas working mechanism 10 and the radiator 21, The oxidant source 4 is set as a four-type door cylinder piston mechanism 99, and the four-type door cylinder piston mechanism 99 is caused to perform the power stroke of the four-type door cylinder piston mechanism 99 according to the intake stroke-pressure gas supply stroke-gas back charge- The exhaust stroke operation mode is controlled by four types of door control mechanisms that are cyclically operated. The air supply port 993 is an oxidant outlet of the oxidant source 4, and the refill port 994 is in communication with the working fluid outlet 6.

The oxidant compressed by the four-type door cylinder piston mechanism 99 enters the internal combustion combustion chamber 3 through the air supply port 993, and the fuel source 5 injects fuel into the internal combustion combustion chamber 3, the oxidant And a combustion chemical reaction occurs between the fuel in the internal combustion combustion chamber 3, a large amount of heat generated to heat the working fluid in the closed circuit of the working fluid, and the mixed combustion product pushes the piston gas working mechanism 10 to perform work, The working fluid flowing out of the piston gas working mechanism 10 enters the four-type door cylinder piston mechanism 99 through the working fluid outlet 6 , and the residual heat of the working medium pushes the four types of door cylinder piston mechanism 99 to work, The exhaust port 992 discharges the four types of door cylinder piston mechanisms.

As an alternative embodiment, the oxidant source 4 can be separated from the four type of door cylinder piston mechanism 99. Example 23

The two-channel entropy cycle engine shown in FIG. 23 differs from the fourth embodiment in that: the cooler is a radiator 21, and the bypass internal combustion chamber 31 is set as a four-type door cylinder piston mechanism 99. The oxidant source 4 and the fuel source 5 are in communication with the air inlet 991, and a spark plug 15 is disposed on the four-type door cylinder piston mechanism 99, and the oxidant source 4 and the fuel source 5 are in the four categories. After the combustion chemical reaction is performed in the door cylinder piston mechanism 99, part of the high temperature and high pressure working fluid generated can be used to make the four types of door cylinder piston mechanism 99 work, and another part of the working medium enters the working fluid closed circuit through the air supply port 993. Entering the piston gas working mechanism 10 together with the working medium heated by the working fluid, the refilling port 994 is in communication with the working fluid outlet 6, and the part of the working fluid discharged from the working fluid outlet 6 is from the Refill port 994 import office In the four types of door cylinder piston mechanism 99, the four types of door cylinder piston mechanism 99 discharges part of the working medium through the exhaust port 992.

Example 24

The two-channel entropy cycle engine shown in FIG. 24 differs from Embodiment 3 in that: the two-channel entropy cycle engine further includes an oxidant sensor 51 and an oxidant control device 52, and the oxidant sensor 51 includes an oxidant probe. The oxidant probe is disposed in the communication passage 1, and the oxidant sensor 51 provides a signal to the oxidant control device 52. The oxidant source 4 is in communication with the working fluid closed circuit via an oxidant control valve 53. The oxidant control device 52 The oxidant control valve 5 is controlled to open or close to adjust the amount of oxidant in the closed circuit of the working fluid.

Example 25

The two-channel entropy cycle engine shown in FIG. 25 differs from the embodiment 24 in that: the piston type gas compression mechanism 9 and the piston gas work mechanism 10 are each configured as a piston liquid mechanism 90, the piston liquid The mechanism 90 includes a gas-liquid cylinder 91 and a gas-liquid isolation structure 92, and the gas-liquid insulation structure 92 is disposed in the gas-liquid cylinder 91. The liquid end of the gas-liquid cylinder 91 is in communication with a hydraulic power mechanism 96, and the hydraulic power mechanism 96 outputs power externally. The hydraulic power mechanism 96 is in communication with the liquid working fluid returning system 97. The liquid working fluid returning system 97 and The liquid of the gas cylinder 91

Book

The end is connected; the hydraulic power mechanism 96 and the liquid working fluid return system 97 are controlled by a process control mechanism 98. The gas working medium of the gas-liquid cylinder 91 has a pressure greater than the sum of the inertial forces of the liquid in the gas-liquid cylinder 91 and the gas-liquid isolation structure 92 when the gas-liquid isolation structure 92 is reciprocated. The gas-liquid isolation structure 92 does not hit the cylinder head of the gas-liquid cylinder 91.

Alternatively, one of the piston type gas compression mechanism 9 and the piston type gas work mechanism 10 is set as the piston liquid mechanism 90 and its corresponding auxiliary means.

In all of the embodiments of the present invention, the internal combustion combustion chamber 3 may be a continuous combustion chamber or a intermittent combustion chamber, and when it is a batch combustion chamber, different intermittent combustion timing relationships may be selected as needed.

In all embodiments of the present invention, the mass flow rate of the substance discharged from the internal combustion combustion chamber 3 is greater than the mass flow rate of the substance introduced into the internal combustion combustion chamber 3 from outside the working fluid circuit; and the side internal combustion is included In the structure of the chamber 31, the mass flow rate of the working fluid flowing into the piston type gas working mechanism 10 is made larger than the mass flow rate of the substance discharged from the side internal combustion combustion chamber 31.

In all embodiments of the present invention, the pressure of the working fluid closed circuit may be set to be at least greater than 2 MPa; alternatively, the pressure bearing capacity of the working fluid closed circuit is set to be greater than 2.5 MPa, 3 MPa, 3.5. MPa, 4 MPa, 4.5 MPa, 5 MPa, 5.5 MPa, 6 MPa, 6.5 MPa, 7 MPa, 7.5 MPa, 8 MPa 8.5 MPa, 9 MPa, 9.5 MPa, 10 MPa, 10.5 MPa, l lMPa, 1 1.5 MPa, 12 MPa, 12.5 MPa, 13 MPa, 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 more than 40MPa. Accordingly, the pressure bearing capacity of the oxidant source 4 and the fuel source 5 is also set to the same numerical range as described above. Due to the need to spray the oxidant source 4 or the substance in the fuel source 5 into the closed loop of the working fluid, The specification therefore applies in a practical application that the pressure bearing capacity of the oxidant source 4 or the fuel source 5 is generally set to be greater than the pressure bearing capacity of the working fluid closed circuit.

It is apparent that the present invention is not limited to the above embodiments, and many variations can be derived or conceived according to the well-known art in the art and the technical solutions disclosed in the present invention, and all such modifications are also considered to be the scope of protection of the present invention.

Claims

Claim

A two-channel entropy cycle engine comprising a piston type gas compression mechanism (9), a piston gas work mechanism (10) and two communication passages (1), characterized in that: the piston type gas compression mechanism (9) The working medium outlet is connected to the working medium of the piston gas working mechanism (10) via a communication passage (1), and the working fluid outlet of the piston gas working mechanism (10) passes through another The communication passage (1) is in communication with the working fluid inlet of the piston gas compression mechanism (9); the piston gas compression mechanism (9) performs work with the piston gas via the two communication passages (1) The mechanism (10) is connected to form a working fluid closed circuit; an internal combustion combustion chamber (3) is disposed in the working fluid closed circuit, and a working fluid outlet (6) is disposed on the working fluid closed circuit.

2. The two-channel entropy cycle engine according to claim 1, wherein: said internal combustion combustion chamber (3) is disposed upstream of said working fluid outlet of said piston type gas compression mechanism (9) and said piston The working fluid outlet of the gas working mechanism (10) is in the closed loop of the working fluid downstream.

3. A two-channel entropy cycle engine according to claim 1 or 2, characterized in that the internal combustion combustion chamber (3) is provided as a side-by-side internal combustion chamber (31).

4. The dual channel entropy cycle engine of claim 1 wherein: said dual channel entropy cycle engine further comprises a chiller disposed on said working fluid closed circuit.

5. The dual channel entropy cycle engine of claim 4, wherein: the dual channel entropy cycle engine further comprises a direct connection channel (100), the direct connection channel (100) communicating with the piston gas working mechanism a working fluid outlet of (10) and a working fluid inlet of the piston compression mechanism (9), the cooler being disposed on the direct connection passage (100) or provided with the piston gas working mechanism (10) The communication passage (1) between the working fluid outlet and the working fluid inlet of the piston type gas compression mechanism (9), the direct connection passage (100) and the piston gas working mechanism ( A control valve (17) is disposed on the communication passage (1) between the working fluid outlet of 10) and the working fluid inlet of the piston gas compression mechanism (9).

6. The dual channel entropy cycle engine according to claim 4, wherein: said two-channel entropy cycle engine further comprises an oxidant source (4), said cooler being disposed in said piston gas working mechanism (10) The communication passage (1) between the working fluid outlet and the piston gas compression mechanism (9) working fluid inlet, the oxidant source (4) passing through the oxidant inlet and the cooler and the piston gas The communication passage (1) between the working fluid inlets of the compression mechanism (9) is in communication, and a cooling liquid discharge port (61) is provided on the communication passage (1) between the cooler and the oxidant inlet. A liquid carbon dioxide outlet (64) is disposed on the communication passage (1) between the oxidant inlet and the piston gas compression mechanism (9).

7. The dual channel entropy cycle engine according to claim 4, wherein: said cooler is disposed upstream of said working fluid outlet of said piston gas working mechanism (10) and said internal combustion combustion chamber (3) The working fluid inlet is closed on the downstream working fluid.

8. The dual channel entropy cycle engine according to claim 4, wherein the cooler is configured as a radiator (21), a gas-liquid direct mixing cooler (20), an adsorption refrigerator (22) or a non-straight Mix cooler (23).

9. The dual channel entropy cycle engine of claim 8 wherein: said dual channel entropy cycle engine further comprises an oxidant source (4), said oxidant source (4) being passed through said non-direct mixer cooler (23) Heated fluid channel and The internal combustion combustion chamber (3) of the claims is in communication.

10. A two-channel entropy cycle engine according to claim 8 or 9, characterized in that a cryogenic liquid discharge port (62) is provided on the non-direct mixing cooler (23).

11. The dual channel entropy cycle engine according to claim 4, 5, 7, 8 or 9, wherein: the two-channel entropy cycle engine further comprises a cooling liquid discharge port (61), and the cooling liquid discharge port ( 61) is disposed on the communication passage (1) between the cooler and the working fluid outlet (6).

12. The dual channel entropy cycle engine according to claim 1 or 2, wherein: the two-channel entropy cycle engine further comprises an oxidant source (4), the oxidant source (4) being in communication with the working fluid closed loop .

13. A two-channel entropy cycle engine according to claim 12, characterized in that said oxidant source (4) is in communication with said internal combustion chamber (3).

14. The dual channel entropy cycle engine of claim 12, wherein: said entropy cycle engine further comprises a direct mixing condensing cooler (19), said cooled fluid inlet of said direct mixing condensing cooler (19) The working fluid outlet (6) is in communication, the oxidant source (4) is in communication with the heated fluid inlet of the direct mixing condensing cooler (19), and is passed through the direct mixing condensing cooler (19) A heated fluid outlet is in communication with the working fluid closed circuit.

15. The two-channel entropy cycle engine according to claim 14, wherein: said oxidant source (4) passes through said heated fluid outlet of said direct mixing condensing cooler (19) and said internal combustion chamber (3) Connected.

16. The two-channel entropy cycle engine of claim 12, wherein: said oxidant source (4) has a pressure greater than 2 MPa.

17. The two-channel entropy cycle engine according to claim 2, wherein: said working fluid outlet (6) is disposed upstream of said working fluid outlet of said piston gas working mechanism (10) and said The working fluid inlet of the internal combustion combustion chamber (3) is on the downstream closed circuit of the working fluid.

18. The dual channel entropy cycle engine of claim 1 wherein: said dual channel entropy cycle engine further comprises a non-direct mixed condensing cooler (18), said non-direct mixed condensing cooler (18) being A cooling medium inlet is connected to the working fluid outlet (6).

19. The two-channel entropy cycle engine according to claim 14, wherein: the direct-mix condensing cooler (19) is provided with a cryogenic liquid discharge port (62).

20. A two-channel entropy cycle engine according to claim 18, wherein said non-direct mixing condensing cooler (18) is provided with a cryogenic liquid discharge port (62).

21. The dual channel entropy cycle engine of claim 19 or 20, wherein: the dual channel entropy cycle engine further comprises a cryogenic liquid working fluid storage tank (16), the cryogenic liquid working fluid storage tank ( 16) with the cryogenic liquid discharge port

(62) Connected.

A two-channel entropy cycle engine according to claim 14, wherein: said direct mixing condensing cooler (19) is provided with a non-condensable gas outlet (82).

23. A two-channel entropy cycle engine according to claim 18, wherein said non-direct mixing condensing cooler (18) is provided with a non-condensing gas outlet (82). Claim

24. A two-channel entropy cycle engine according to claim 22 or 23, wherein said non-condensable gas outlet (82) is in communication with said working fluid closed circuit.

25. The entropy cycle engine of claim 18, wherein: said entropy cycle engine further comprises an oxidant source (4), said oxidant source (4) being passed through said non-direct mixing condensing cooler (18) A heating fluid passage is in communication with the internal combustion chamber (3).

26. The dual channel entropy cycle engine of claim 1 wherein: a control valve (17) is provided on said working fluid outlet (6).

27. The two-channel entropy cycle engine according to claim 26, wherein: said control valve (17) is set as a pressure control valve, and said pressure control valve controls said working fluid outlet (6) at said work The working fluid is derived when the pressure in the closed loop exceeds the set limit.

28. The dual channel entropy cycle engine of claim 26 wherein: said pressure control is controlled by a control mechanism that causes a minimum pressure in said working fluid closed circuit to be greater than 0.2 MPa.

29. The dual channel entropy cycle engine according to claim 26, wherein: said control valve (17) is controlled by a threshold control mechanism, and said opening degree control mechanism is configured according to a pressure in said working fluid closed circuit The range is controlled to control the degree of opening of the control port (17) such that the working fluid outlet (6) is in a normally open state at a certain degree of opening.

30. The dual channel entropy cycle engine according to claim 1 or 17, wherein: the dual channel entropy cycle engine further comprises an auxiliary gas work mechanism (102), and the working fluid outlet (6) and the subsidiary The working inlet of the gas working mechanism (102) is connected.

31. The dual channel entropy cycle engine of claim 1 or 17, wherein: the dual channel entropy cycle engine further comprises a gas storage tank (60), the gas storage tank (60) and the working medium guide The exit (6) is connected.

32. The two-channel entropy cycle engine according to claim 1, characterized in that: a check valve (7) is provided on the communication passage (1).

33. The two-channel entropy cycle engine according to claim 1, wherein: the working fluid outlet of the piston gas working mechanism (10) is upstream, and the piston gas compression mechanism (9) is The mass inlet is provided with another piston gas working mechanism (10) on the closed circuit of the working fluid downstream.

The entropy cycle engine according to claim 1 or 33, characterized in that the piston type gas working mechanism (10) outputs power to the piston type gas compression mechanism (9).

35. The two-channel entropy cycle engine according to claim 1, wherein: in the closed circuit of the working fluid, a part of the gas participating in the circulation is non-condensable.

36. The dual channel entropy cycle engine of claim 35, wherein: the dual channel entropy cycle engine further comprises a non-condensable gas storage tank (70), and the non-condensable gas storage tank (70) is controlled by the control device The working fluid is in closed loop communication.

37. The dual channel entropy cycle engine of claim 36, wherein: said dual channel entropy cycle engine further comprises a non-condensable gas return compressor (71), said non-condensable gas returning compressor (71) The air inlet is in communication with the working fluid closed circuit, and the gas outlet of the non-condensable gas returning compressor (71) is in communication with the non-condensable gas storage tank (70).

38. The dual channel entropy cycle engine of claim 1 wherein: three in the closed loop of the working fluid The claim metacatalyst (88).

39. The two-channel entropy cycle engine according to claim 1, wherein: between a cylinder center line of said piston type gas compression mechanism (9) and a cylinder center line of said piston type gas work mechanism (10) The angle of the piston is less than 180 degrees, and the piston of the piston type gas compression mechanism (9) and the piston of the piston type gas work mechanism (10) are respectively connected to the same connecting rod journal of the same crankshaft via a connecting rod.

40. The two-channel entropy cycle engine according to claim 39, wherein: between the cylinder center line of the piston type gas compression mechanism (9) and the cylinder center line of the piston gas work mechanism (10) The angle is 90 degrees.

The dual-channel entropy cycle engine according to claim 1, wherein the piston of the piston type gas compression mechanism (9) and the piston of the piston type gas work mechanism (10) pass through a connecting rod and a same crankshaft, respectively. The different connecting rod journals are connected, and the phase difference between the two connecting rod journals is greater than 0 degrees and less than 180 degrees.

42. The dual channel entropy cycle engine of claim 1 wherein: said dual channel entropy cycle engine further comprises a cryogenic cold source (50), said cryogenic cold source (50) for providing a cryogenic material, said The cryogenic material is used to cool the working fluid in the piston gas compression mechanism (9) or about to enter the piston gas compression mechanism (9).

43. The dual channel entropy cycle engine of claim 1 wherein: said dual channel entropy cycle engine further comprises a turbine power mechanism (14) and an impeller compressor (13), said working fluid outlet (6) And the turbine power mechanism

The working fluid inlet of (14) is connected, and the working fluid outlet of the turbine power mechanism (14) is connected to the working fluid inlet of the impeller compressor (13) via an auxiliary cooler (211), the impeller compressor (13) The working medium outlet is in communication with the working fluid closed circuit; the working fluid outlet of the turbine power mechanism (14) and the working fluid inlet of the impeller compressor (13) are provided with an auxiliary working fluid outlet (66).

44. The dual channel entropy cycle engine of claim 1 wherein: said dual channel entropy cycle engine further comprises a four type of door cylinder piston mechanism (99), said four types of door cylinder piston mechanism (99) The gas LJ (993) is in communication with the working fluid closed circuit, and the refill port (994) of the four-type door cylinder piston mechanism (99) is in communication with the working fluid outlet (6).

45. The dual channel entropy cycle engine of claim 44, wherein: said dual channel entropy cycle engine further comprises an oxidant source (4), said oxidant source (4) being set to said four type of door cylinder piston mechanism (99).

46. The two-channel entropy cycle engine according to claim 3, wherein: said side internal combustion chamber (31) is set as a four-type door cylinder piston mechanism (99), said four-type door cylinder piston mechanism (99) The gas supply port (993) communicates with the cylinder of the piston gas working mechanism (10), and the refill port (994) of the four types of door cylinder piston mechanism (99) and the working fluid outlet (6) ) Connected.

47. The dual channel entropy cycle engine of claim 12, wherein: said dual channel entropy cycle engine further comprises an oxidant sensor (51) and an oxidant control device (52), said oxidant sensor (51) being located at In the closed circuit of the working fluid, the oxidant sensor (51) provides a signal to the oxidant control device (52), and the oxidant source (4) is connected to the working fluid closed circuit via an oxidant control valve (53). The oxidant control device (52) controls the oxidant control valve (53).

48. The dual channel entropy cycle engine of claim 1 wherein said piston gas compression mechanism (9) The claim is set as a piston liquid mechanism (90), the piston liquid mechanism includes a gas-liquid cylinder (91) and a gas-liquid isolation structure (92), and the gas-liquid isolation structure (92) is disposed in the gas-liquid cylinder (91) ) Inside.

49. The two-channel entropy cycle engine according to claim 1, wherein: the piston gas work mechanism (10) is a piston liquid mechanism (90), and the piston liquid mechanism comprises a gas liquid cylinder (91) and gas. a liquid isolation structure (92), the gas-liquid isolation structure (92) is disposed in the gas-liquid cylinder (91).

50. The dual channel entropy cycle engine according to claim 48 or 49, wherein: the gas working fluid of the gas cylinder (91) has a pressure greater than the gas cylinder of the gas-liquid isolation structure (92) (91) The sum of the inertial forces in the liquid and the gas-liquid isolation structure (92) when reciprocating.

51. The two-channel entropy cycle engine according to claim 1, wherein: the mass flow rate of the substance discharged from the internal combustion combustion chamber (3) is greater than the introduction into the internal combustion combustion chamber from the closed circuit of the working fluid (3) The mass flow of the substance.

52. The two-channel entropy cycle engine according to claim 3, wherein: a mass flow rate of the working fluid flowing into the piston gas working mechanism (10) is greater than a mass flow rate of the side internal combustion combustion chamber (31) Mass Flow.

53. The dual channel entropy cycle engine of claim 1 wherein: said working fluid closed circuit has a pressure bearing capacity greater than 2 MPa.

54. The two-channel entropy cycle engine according to claim 1, wherein: a regenerator (33) is disposed on the communication passage (1), and a working fluid outlet of the piston gas working mechanism (10) The communication passage (1) between the working fluid inlets of the piston type gas compression mechanism (9) is set as a cooled fluid passage of the regenerator (33), and the piston type gas compression mechanism (9) The communication passage (1) between the working fluid outlet and the working fluid inlet of the piston gas working mechanism (10) is set as the heated fluid passage of the regenerator (33).

A two-channel entropy cycle engine according to claim 1, characterized in that said internal combustion chamber (3) is disposed in said communication passage (1) in the form of a separate cavity.