JP2009115065A - Energy conversion system - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an energy conversion system having simple structure and high exhaust heat recovery efficiency and capable of obtaining high energy conversion efficiency. <P>SOLUTION: The energy conversion system 1A has a Rankine cycle circuit 11 and a Stirling engine 12, and a working medium of the Rankine cycle circuit 11 and a high temperature side piston of the Stirling engine 12 are heated by a heater 13. Generators 20, 22 are connected to an expansion device 15 of the Rankine cycle circuit 11 and the Stirling engine 12, respectively. A cooling medium of the Stirling engine 12 flowing out of a cooling medium storage tank 34 performs heat exchange with the working medium of the Rankine cycle circuit 11 by a heat exchanger 16 and absorbs the heat of the working medium. In addition, the cooling medium absorbs the heat of a low temperature part of the Stirling engine by a water jacket 33 and exhaust the heat of the heater 13 by an exhaust heat recovery part 37h of an exhaust heat recovery device 14, and then is stored in the cooling medium storage tank 34. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to an energy conversion system that combines a Rankine cycle circuit and a Stirling engine.

  In recent years, resource issues and environmental issues have been emphasized, and improvement of energy conversion efficiency of heat engines and the like and effective utilization of waste energy have become important issues. For this reason, conventionally, an energy conversion system in which a Rankine cycle circuit and a Stirling engine are combined has been proposed. For example, Patent Document 1 describes an energy conversion system (composite cooling power generation apparatus) 300 that generates power by combining a Rankine cycle circuit 100 and a Stirling engine 200 as shown in a schematic diagram of FIG.

  The energy conversion system 300 includes an expander (expansion turbine) 102 driven by a working medium evaporated by an evaporator (evaporator) 101 in the Rankine cycle circuit 100 and a condenser (condenser) that condenses the expanded working medium. 103, and a generator (generator) 104 that generates power by driving the expander 102 is attached to the expander 102.

On the other hand, the Stirling engine 200 reciprocates the working gas between a high temperature part 202 provided with a high temperature side cylinder (not shown) and a low temperature part 204 provided with a low temperature side cylinder (not shown), and the working gas expands. It is driven by repeating and contracting. A generator (generator) 201 is also attached to the Stirling engine 200. Waste heat generated when the high temperature section 202 of the Stirling engine 200 is heated is recovered and supplied to the evaporator 101 in the Rankine cycle circuit 100. The working medium of the Rankine cycle circuit 100 is expanded by the expander 102 and then condensed in the condenser 103 through heat exchange with the liquefied natural gas as the second cooling medium, while the cooling medium (cooling heat) of the Stirling engine 200 is condensed. The medium) circulates between the Stirling engine 200 and the vaporizer 203, heat-exchanges in the low-temperature part 204 of the Stirling engine 200, rises in temperature, and then passes through the condenser 103 in the vaporizer 203. And heat exchange is performed and cooled.
JP 2006-329059 A

  However, the invention described in Patent Document 1 condenses and cools the working medium of the Rankine cycle circuit and the cooling medium of the Stirling engine by the second cooling medium for absorbing and discarding the exhaust heat. And a vaporizer must be provided separately, and in addition to the working medium conduction pipe and the cooling medium conduction pipe, a second cooling medium conduction pipe must be provided, which complicates the structure. There's a problem. In the invention described in Patent Document 1, since the working medium is separately exchanged with the condenser and the cooling medium is separately exchanged with the vaporizer, the overall heat exchange efficiency is lowered, and the exhaust heat after the heat exchange is restored. There is a problem that the energy utilization efficiency in the case of using it decreases.

  The present invention has been made in view of the above problems, and an object of the present invention is to provide an energy conversion system that has a simple structure, high exhaust heat recovery efficiency, and high energy conversion efficiency.

  In order to solve this problem, the invention described in claim 1 includes a Rankine cycle circuit including an expander that converts expansion energy of a working medium into kinetic energy, a high-temperature unit that heats and expands the working gas in the expansion chamber, and An energy conversion system comprising a low temperature part for cooling and shrinking the working gas and a Stirling engine for converting thermal energy into kinetic energy, between the cooling medium for cooling the low temperature part of the Stirling engine and the working medium A heat exchanger for performing heat exchange is provided.

  According to a second aspect of the present invention, in addition to the configuration of the first aspect, the heat exchanger includes the working medium in which expansion energy is converted into kinetic energy through the expander and the Stirling engine. The cooling medium before being supplied to the low temperature part is supplied.

  According to a third aspect of the present invention, in addition to the configuration of the first or second aspect, a heating unit that absorbs heat to give expansion energy to the working medium provided in the Rankine cycle circuit and the Stirling engine A heater for heating at least one of the high-temperature parts and an exhaust heat recovery unit for passing the heat generated from the heater are provided, and the cooling medium is passed through the exhaust heat recovery unit. And an exhaust heat recovery section for exchanging heat with the air inside the exhaust heat recovery unit.

  The invention according to claim 4 is provided with a rotating machine such as a generator or a motor in addition to the configuration according to any one of claims 1 to 3, and the rotating machine includes the output shaft of the Stirling engine and the Rankine cycle. It is connected to each of the output shafts of the expander of the circuit, or only one of them, and rotational kinetic energy is supplied to the rotating machine so as to be driven.

  The invention according to claim 5 is characterized in that, in addition to the structure according to any one of claims 1 to 4, an output shaft of the Stirling engine and an output shaft of the expander are connected.

  In addition to the structure of Claim 5, the invention of Claim 6 is a mechanism for controlling the rotational speed of each of the output shafts at a connection portion between the output shaft of the Stirling engine and the output shaft of the expander, The present invention is characterized in that a rotation adjusting unit is provided that rotates each output shaft at a predetermined rotation ratio by adjusting with a fluid or the like.

  According to a seventh aspect of the invention, in addition to the configuration of the sixth aspect, the rotation adjusting portion is formed by a speed change means such as a gear mechanism such as a planetary gear mechanism, a torque converter, or a continuously variable transmission. And

  The invention according to claim 8 is characterized in that, in addition to the configuration according to any one of claims 1 to 7, a cooling medium storage tank for storing the cooling medium that has passed through the low temperature part is provided. .

  According to a ninth aspect of the present invention, in addition to the configuration of the eighth aspect, the cooling medium stored in the cooling medium storage tank is supplied to the low temperature part, and the cooling medium storage tank and the low temperature part are provided. And a cooling medium conducting tube for circulating the cooling medium is provided.

  According to a tenth aspect of the present invention, in addition to the configuration according to the eighth or ninth aspect, the cooling medium flowing out from the cooling medium storage tank is allowed to flow into the heat exchanger as a flow path for the cooling medium. Cooling medium flow path and a second cooling medium flow path for allowing the cooling medium flowing out from the cooling medium storage tank to flow into the low temperature portion, the first cooling medium flow path and the second cooling medium flow path are provided. A cooling medium flow rate adjustment valve is provided for adjusting the flow rate of the cooling medium with respect to the cooling medium flow path.

  The invention according to claim 11 is the configuration according to any one of claims 8 to 10, in addition to the cooling medium conducting pipe or the cooling medium storage tank through which the cooling medium that has passed through the low temperature portion is conducted. An external channel connected to at least one of the cooling medium and the cooling medium and the cooling medium stored in the cooling medium storage layer to flow out to the outside, and the cooling medium of the external channel And an outflow amount adjusting valve for adjusting the flow rate of the gas.

  According to a twelfth aspect of the present invention, in addition to the structure according to any one of the first to eleventh aspects, a compressor that compresses the second working medium, heat between indoor air and the second working medium. A refrigerating and air-conditioning cycle circuit provided with a second heat exchanger for performing exchange,

  The compressor is connected to at least one of an output shaft of the Stirling engine and an output shaft of the expander.

  According to a thirteenth aspect of the present invention, in addition to the configuration of the twelfth aspect, a third heat exchanger that exchanges heat between the second working medium of the refrigeration air-conditioning cycle circuit and the cooling medium of the Stirling engine. It is provided with.

  According to a fourteenth aspect of the present invention, in addition to the configuration according to the thirteenth aspect, the third heat exchanger, the working medium of the Rankine cycle circuit, and the cooling medium of the Stirling engine perform heat exchange. A heat exchanger and a third cooling medium flow path for allowing the cooling medium flowing out from the cooling medium storage tank to flow into the heat exchanger as the cooling medium flow path; and the cooling medium storage tank A fourth cooling medium flow path for allowing the cooling medium flowing out from the third heat exchanger to flow into the third heat exchanger, and the cooling medium flow path with respect to the third cooling medium flow path and the fourth cooling medium flow path. A second coolant flow rate adjustment valve for adjusting the flow rate is provided.

  According to a fifteenth aspect of the present invention, in addition to the configuration according to any one of the twelfth to fourteenth aspects, the refrigeration air conditioning cycle circuit forcibly exchanges heat between the second working medium and outdoor air. A fourth heat exchanger is provided.

  According to a sixteenth aspect of the present invention, in addition to the configuration according to any one of the twelfth to fifteenth aspects, at least one of the output shaft of the Stirling engine and the output shaft of the expander includes the compressor. The rotating machine is connected, and a connecting portion between the output shaft, the compressor, and the rotating machine has a driving force output from at least one of the Stirling engine and the expander, and the compressor and the A rotation adjusting unit for adjusting a transmission state to one or both of the rotating machines is provided.

  According to a seventeenth aspect of the present invention, in addition to the configuration according to any one of the twelfth to sixteenth aspects, in the refrigeration air-conditioning cycle circuit, the flow path of the second working medium is switched, and the second heat exchange And a four-way valve forming either a first circuit for using the condenser as an evaporator or a second circuit for using the second heat exchanger as a condenser.

  According to an eighteenth aspect of the present invention, in addition to the configuration according to any one of the first to seventeenth aspects, the working medium of the Rankine cycle circuit and the surrounding air are forcibly exchanged with heat to cause the working medium to be exchanged. A fifth heat exchanger for cooling is provided, and as the working medium flow path, a first working medium flow path for allowing the working medium flowing out from the expander to pass through the heat exchanger, and an outflow from the expander A second working medium flow path for passing the working medium through the fifth heat exchanger is provided, and the flow rate of the working medium with respect to the first working medium flow path and the second working medium flow path is set. A working medium flow control valve for adjusting is provided.

  According to the first aspect of the present invention, in the energy conversion system including the Rankine cycle circuit and the Stirling engine, heat exchange is performed between the cooling medium that cools the low temperature portion of the Stirling engine and the working medium of the Stirling engine. By including the heat exchanger, it is possible to directly exchange heat between the cooling medium and the working medium. As a result, the exhaust heat of the Rankine cycle circuit can be recovered only by the cooling medium without interposing the second cooling medium for recovering the exhaust heat, and the energy when the exhaust heat is reused. Conversion efficiency can be improved.

  According to the first aspect of the present invention, there is provided a conducting pipe for conducting the second cooling medium, a capacitor for exchanging heat between the second cooling medium and the working medium, and the second working medium; It is not necessary to separately provide a vaporizer that exchanges heat with the cooling medium, and the configuration of the entire system can be simplified. Thereby, it is possible to construct an energy conversion system that has a simple structure, high exhaust heat recovery efficiency, and high energy conversion efficiency.

  According to the second aspect of the present invention, the heat exchanger includes the working medium in which the expansion energy is converted into kinetic energy through the expander and the cooling medium before being supplied to the low temperature portion of the Stirling engine. After being passed through the expander, the heat exchange between the relatively low temperature working medium and the cooling medium cooler than the working medium is performed to cool the working medium with the cooling medium, and then the cooling medium is compared. It can be supplied to the low temperature part of the Stirling engine, which is a high temperature. This makes it possible to recover the exhaust heat remaining after expansion of the working medium without reducing the efficiency of heat exchange, and to cool the working medium and the low-temperature part with the cooling medium, thereby further increasing energy conversion. Efficiency can be obtained.

  According to the third aspect of the present invention, a heater that heats at least one of a heating unit that absorbs heat to give expansion energy to a working medium provided in the Rankine cycle circuit and a high-temperature unit of a Stirling engine. And an exhaust heat recovery unit that passes heat generated from the heater, and passes the cooling medium through the exhaust heat recovery unit to exchange heat between the cooling medium and the air inside the exhaust heat recovery unit Since the exhaust heat generated by the heater can be recovered by the cooling medium that passes through the exhaust heat recovery unit, the exhaust heat that is not used when heating the working medium and the high temperature part of the Stirling engine can be recovered. The amount of waste can be reduced.

  According to the fourth aspect of the present invention, a rotating machine such as a generator or a motor is provided, and the rotating machine is provided on each of the output shaft of the Stirling engine and the output shaft of the expander of the Rankine cycle circuit, or on only one of them. By being connected and driven by supplying rotational kinetic energy to the rotating machine, the rotating machine can be driven by the energy output from at least one of the Stirling engine and the Rankine cycle circuit. . Thereby, various kinetic energy and electric power energy can be efficiently acquired from the energy of the rotational motion of an output shaft.

  According to the fifth aspect of the present invention, the output shaft of the Stirling engine and the output shaft of the expander are connected to each other, so that the connected output shaft is output from the Stirling engine and the Rankine cycle circuit. It is possible to obtain a large output from a single rotating machine connected to an output shaft connected to the output shaft.

  According to the sixth aspect of the present invention, the output shaft of the connecting portion between the output shaft of the Stirling engine and the output shaft of the expander is adjusted by adjusting the rotational speed of each output shaft by a mechanism, fluid, or the like. Is provided with a rotation adjustment unit that rotates the engine at a predetermined rotation ratio, so that even if the rotation speed of each output shaft is different due to a difference in driving state between the Stirling engine and the Rankine cycle circuit, the rotation adjustment unit rotates the rotation speed. By adjusting the difference between them, the rotational speed can be synchronized to obtain the resultant force of the Stirling engine and the expander, and the transmission loss of energy to the rotary machine can be suppressed.

  According to the seventh aspect of the present invention, the rotation adjusting portion is formed by a gear mechanism such as a planetary gear mechanism, a speed change means such as a torque converter, a continuously variable transmission, etc. The number can be adjusted by a specific device using a mechanism or a fluid.

  According to the eighth aspect of the invention, since the cooling medium storage tank that stores the cooling medium that has passed through the low temperature portion is provided, the exhaust heat recovered by the cooling medium can be stored in the medium storage tank. Further, the stored cooling medium can be taken out, and the exhaust heat recovered by the cooling medium and the cooling medium can be used for multiple purposes. Thereby, the energy amount which can be used by the user of the system can be increased.

  According to the ninth aspect of the present invention, the cooling medium conducting pipe that supplies the cooling medium stored in the cooling medium storage tank to the low temperature part and circulates the cooling medium between the cooling medium storage tank and the low temperature part. The Stirling engine can be cooled with the cooling medium stored in the cooling medium storage tank, and the cooling medium can be circulated between the Stirling engine and the cooling medium storage tank. Can be increased. Further, by storing the continuously circulating cooling medium in the cooling medium storage tank, a large amount of heat can be stored in the cooling medium storage tank, and convenience when taking out the cooling medium and using the heat is enhanced. Thereby, the increase in the usage-amount of a cooling medium can be suppressed and the convenience of heat utilization can be improved.

  According to the invention described in claim 10, as the cooling medium flow path, the cooling medium flowing out from the cooling medium storage tank flows into the heat exchanger, and the first cooling medium flow path flows out from the cooling medium storage tank. By providing the second cooling medium flow path for allowing the cooling medium to flow into the low temperature part, the cooling medium flowing out from the cooling medium storage tank can be directly supplied to the low temperature part, and the thermal efficiency of the Stirling engine is improved. be able to. Further, a cooling medium flow rate adjusting valve for adjusting the flow rate of the cooling medium with respect to the first cooling medium flow path and the second cooling medium flow path is provided. The flow rate of the cooling medium used for cooling the working medium of the cycle circuit and the flow rate of the cooling medium used for increasing the cooling efficiency of the Stirling engine can be controlled.

  According to the eleventh aspect of the present invention, the cooling medium that has passed through the low temperature portion is connected to at least one of the cooling medium conduction pipe and the cooling medium storage tank, and is stored in the cooling medium and the cooling medium storage layer. By providing the external flow path for allowing at least one of the cooled cooling medium to flow out, the cooling medium from which the exhaust heat has been recovered can be easily taken out. In addition, since the outflow amount adjusting valve for adjusting the flow rate of the cooling medium in the external flow path is provided, the amount of water discharged from the external flow path can be controlled when the cooling medium is taken out. Thereby, the convenience at the time of utilizing the cooling medium and the exhaust heat recovered by the cooling medium can be improved.

  According to invention of Claim 12, the refrigerating air-conditioning cycle circuit provided with the compressor which compresses a 2nd working medium, and the 2nd heat exchanger which performs heat exchange between indoor air and a 2nd working medium The compressor is connected to at least one of the output shaft of the Stirling engine and the output shaft of the expander, so that the refrigeration and air conditioning cycle circuit is driven by the output of at least one of the Stirling engine and the expander. An air conditioner that supplies power and heats or cools indoor air by the second heat exchanger can be realized. As a result, the system can be used more versatilely.

  According to the invention described in claim 13, by providing the third heat exchanger that performs heat exchange between the second working medium of the refrigeration air-conditioning cycle circuit and the cooling medium of the Stirling engine, the second working medium is obtained. Allows cooling with a cooling medium. Thereby, heat exchange can be performed between the system components including the refrigeration air conditioning cycle circuit, and higher energy conversion efficiency can be obtained.

  According to the fourteenth aspect of the present invention, the third heat exchanger and the heat exchanger are provided, respectively, and the cooling medium flowing out from the cooling medium storage tank flows into the heat exchanger as the cooling medium flow path. The third cooling medium flow path and the fourth cooling medium flow path for allowing the cooling medium flowing out from the cooling medium storage tank to flow into the third heat exchanger are provided, so that the cooling medium is cooled by the second working medium. And cooling of the working medium. In addition, the operation of the refrigeration air-conditioning cycle circuit and the Rankine cycle circuit is provided by the provision of the second cooling medium flow rate adjustment valve for adjusting the flow rate of the cooling medium with respect to the third cooling medium flow channel and the fourth cooling medium flow channel. The flow rate of the cooling medium used for cooling the refrigeration air conditioning cycle circuit and the flow rate of the cooling medium used for cooling the Rankine cycle circuit can be controlled based on the state.

  According to the invention described in claim 15, the refrigeration air conditioning cycle circuit includes the fourth heat exchanger that forcibly exchanges heat between the second working medium and outdoor air, so that the The two working media can be cooled or heated without heat exchange with the cooling medium or the working medium.

  According to the invention described in claim 16, the compressor and the rotating machine are connected to at least one of the output shaft of the Stirling engine and the output shaft of the expander, and the connecting portion between the output shaft and the compressor and the rotating machine. Is provided with a rotation adjusting unit that adjusts the transmission state of the driving force output from at least one of the Stirling engine and the expander to one or both of the compressor and the rotating machine. With respect to the compressor and the rotating machine connected to the output shaft, it is possible to select a driving target and control a driving state.

  According to the invention described in claim 17, in the refrigeration air-conditioning cycle circuit, the first circulation path or the second heat exchanger for switching the flow path of the second working medium and using the second heat exchanger as an evaporator. By providing a four-way valve that forms any of the second circulation path for use as a condenser, the second heat exchanger can be used for both indoor units for cooling and indoor units, The system can be operated more diversely.

  According to the invention described in claim 18, the Rankine cycle circuit is provided with the fifth heat exchanger for forcibly exchanging heat between the working medium of the Rankine cycle circuit and the surrounding air to cool the working medium. The working medium can be cooled without heat exchange with the cooling medium. In addition, as the working medium flow path, a first working medium flow path that allows the working medium flowing out from the expander to pass through the heat exchanger, and a second that allows the working medium flowing out from the expander to pass through the fifth heat exchanger. And a working medium flow rate adjusting valve for adjusting the flow rate of the working medium with respect to the first working medium flow path and the second working medium flow path is provided. Heat energy can be recovered by the cooling medium, or heat can be forcibly exchanged with the surrounding air to dissipate heat, and the heat exchanger and the fifth heat exchange can be performed based on the operating state of the Stirling engine, the temperature, etc. It is possible to drive the Rankine cycle circuit in a good state at all times by adjusting the flow rate of the working medium with respect to the vessel, and to improve the convenience of system operation.

Embodiments of the present invention will be described below.
Embodiment 1 of the Invention
1 to 4 show an embodiment of the present invention.

  First, the configuration will be described. An energy conversion system 1A of this embodiment is a household cogeneration system, and has a Rankine cycle circuit 11 having an output of about several hundred W (more specifically, about 300 W to 700 W). , A Stirling engine 12 having an output of several kW (more specifically, about 1 kW to 3 kW), and a cooling medium circulation circuit 35 that circulates a cooling medium for cooling the Stirling engine 12.

  The Rankine cycle circuit 11 includes a heating unit 18d, an expander 15, a heat exchanger 16, and a first pump 17. The heating unit 18d, the expander 15, the heat exchanger 16, and the first pump 17 are respectively connected by working medium conduction pipes 18a, 18b, and 18c that are working medium conduction paths to form a working medium circulation path.

  As the working medium, for example, chlorofluorocarbons such as R245fa and R245ca are used, but other substances such as butane, pentane, and carbon dioxide that are easily liquefied by compression and have large heat of vaporization may be used as the working medium.

  The heater 13 is a burner that dissipates heat by gas combustion, and is provided inside the exhaust heat recovery device 14 so as to face the high temperature portion of the Stirling engine 12. The heater 13 may be anything as long as it can be used as a heat source for the Stirling engine 12 (external combustion engine), such as one that directly burns fossil fuel, factory exhaust heat, automobile exhaust heat, or incinerator. It is also possible to use the exhaust heat of the.

  The exhaust heat recovery unit 14 is formed in a substantially cylindrical shape by a member having high heat resistance and heat insulation, and one side (the right side in FIG. 2) sucks air and the other side (the left side in FIG. 2) discharges air. It is formed on the exhaust side. As shown in FIG. 2, the heater 13 is provided on the intake side of the exhaust heat recovery unit 14, and the heat generated from the heater 13 passes through the exhaust heat recovery unit 14 and is released to the exhaust side.

  The expander 15 is a scroll type expander, and converts the expansion energy of the working medium into rotational kinetic energy. The expander 15 is provided with an output shaft 19, and a generator 20 as a “rotator” is connected to the output shaft 19, and the generator 20 is driven by the rotational kinetic energy of the expander 15.

  The first pump 17 is a low-temperature and high-pressure pump, and is configured to send the working medium that has passed through the heat exchanger 16 to the exhaust heat recovery unit 14 and circulate the working medium in the Rankine cycle circuit 11.

  A heating unit 18d is provided in the middle of the working medium conducting tube 18a. The heating portion 18d is formed in a spiral shape by a tubular member capable of conducting the working medium, and is disposed closer to the exhaust side than the heater 13 inside the exhaust heat recovery device 14. Although the heating part 18d in this embodiment is disposed along the inner peripheral surface of the exhaust heat recovery unit 14, the inside of the heating unit 18d is conducted, for example, disposed around the exhaust heat recovery unit 14. Any arrangement may be employed as long as heat exchange between the working medium and the air inside the exhaust heat recovery device 14 (that is, combustion exhaust of the heater 13) can be performed efficiently.

  On the other hand, the Stirling engine 12 is a two-piston type Stirling engine as shown in FIG. 2, and a crank chamber 12a and a generator chamber 23 are provided in communication with a housing 21 formed by casting or the like, and above the crank chamber 12a. A high temperature side cylinder 24 of “high temperature part” and a low temperature side cylinder 25 as “low temperature part” are provided.

  A high temperature side piston 27 is provided inside the high temperature side cylinder 24, and a low temperature side piston 28 is provided inside the low temperature side cylinder 25, and is formed between the inside of the high temperature side cylinder 24 and the high temperature side piston 27. The space is formed in the expansion chamber 31, and the space formed between the low temperature side cylinder 25 and the low temperature side piston 28 is formed in the contraction chamber 32, and the expansion chamber 31 and the contraction chamber 32 are communicated with each other by the communication pipe 26. A working gas is enclosed in the expansion chamber 31 and the contraction chamber 32. The working gas moves through the expansion chamber 31 and the contraction chamber 32 via the communication pipe 26, is heated and expanded in the expansion chamber 31, and is cooled and contracted in the contraction chamber 32. As the working gas, non-condensable gas such as helium, hydrogen, carbon dioxide, nitrogen and air is used.

  The high temperature side piston 27 and the low temperature side piston 28 are coupled to one output shaft 29 disposed in the crank chamber 12a. The output shaft 29 is a crankshaft, and converts the vertical motion of the pistons 27 and 28 into rotational motion. The first crank portion 29a to which the high temperature side piston 27 is connected and the second crank portion 29b to which the low temperature side piston 28 are connected have a phase difference of a predetermined angle (for example, about 90 degrees). One end side of the output shaft 29 extends inside the generator chamber 23 and is connected to a generator 22 as a “rotating machine”. The other end portion of the output shaft 29 protrudes from the other side portion of the housing 21 to the outside. A flywheel 30 is connected. The generator 22 receives power from the Stirling engine 12 to generate electric power, but also functions as a starter motor when starting the Stirling engine 12. However, a starter motor may be provided separately from the generator 22 so that the generator 22 only generates power.

  The high temperature side cylinder 24 is accommodated on the exhaust side of the heater 13 inside the exhaust heat recovery device 14 and is heated by the heat generated by the heater 13.

  A water jacket 33 forming a cooling medium circulation circuit 35 is provided around the low temperature side cylinder 25, and the low temperature side cylinder 25 is cooled by a cooling medium flowing through the water jacket 33. The cooling medium in this embodiment is water.

  The cooling medium circulation circuit 35 includes a second pump 36 that sends the cooling medium supplied from the cooling medium storage tank 34 to the heat exchanger 16, the heat exchanger 16, a water jacket 33, and an exhaust heat recovery unit 37h. ing. The cooling medium storage tank 34, the second pump 36, the heat exchanger 16, and the water jacket 33 are respectively connected by cooling medium conduction pipes 37 a, 37 b, 37 c, and 37 d provided as a cooling medium conduction path, and exhaust heat recovery is performed. The part 37h is provided in the middle of the cooling medium conducting pipe 37d to form a cooling medium circulation path.

  The second pump 36 is a low-temperature and low-pressure pump, and sends the cooling medium supplied from the cooling medium storage tank 34 to the heat exchanger 16. The cooling medium storage tank 34 is a hot water storage tank having a hot water storage capacity of several tens to several hundreds of liters.

  The cooling medium storage tank 34 is provided with an outflow pipe 34a and an inflow pipe 34b. The outflow pipe 34a is provided on the upper side of the cooling medium storage tank 34, and is configured to allow the cooling medium stored in the cooling medium storage tank 34 to flow out to the outside. A valve 34c for adjusting the amount is provided. The inflow pipe 34b is provided below the cooling medium storage tank 34, and is configured so that the cooling medium can be injected into the cooling medium storage tank 34 from the outside.

  The heat exchanger 16 is supplied with the working medium in which the expansion energy is converted into kinetic energy through the expander 15 and the cooling medium before being supplied to the water jacket 33 of the Stirling engine 12. The heat exchanger 16 is provided with a working medium flow path and a cooling medium flow path, respectively, so that heat exchange between the working medium and the cooling medium is performed.

  The exhaust heat recovery part 37h is formed in a spiral shape by a tubular member through which a cooling medium can be conducted, and is disposed on the exhaust side of the heater 13 inside the exhaust heat recovery unit 14 as shown in FIG. Yes. The exhaust heat recovery unit 37h in this embodiment is disposed along the inner peripheral surface of the exhaust heat recovery unit 14, but the exhaust heat recovery unit 37h is disposed around the exhaust heat recovery unit 14, for example. Any arrangement may be employed as long as heat exchange between the cooling medium that is conducted through the inside and the air inside the exhaust heat recovery device 14 (that is, combustion exhaust of the heater 13) can be performed efficiently.

  Next, the operation of this embodiment will be described.

  When the first pump 17 is operated in the Rankine cycle circuit 11, the working medium is pressurized, the pressurized working medium is sent to the working medium conducting pipe 18a, and is heated by the heat generated by the heater 13 in the heating unit 18d. The working medium heated by the heating unit 18d is supplied to the expander 15 through the working medium conducting pipe 18a and is expanded by the expander 15. The expansion energy due to the expansion of the working medium is converted into kinetic energy for rotationally driving the expander 15, and the output shaft 19 is rotated by this kinetic energy to drive the generator 20. The expanded working medium is supplied from the expander 15 to the heat exchanger 16 through the working medium conducting pipe 18b, and is cooled by heat exchange with the cooling medium. The cooled working medium is supplied again to the first pump 17 through the working medium conducting pipe 18c from the heat exchanger 16 and pressurized, and thereafter the circulation of the working medium is repeated.

  On the other hand, in the Stirling engine 12, when the high temperature side cylinder 24 is heated by the heat generated by the heater 13, the working gas in the expansion chamber 31 is heated and expands, and is sent to the contraction chamber 32 through the communication pipe 26. . In the contraction chamber 32, the heat exchange between the working gas and the cooling medium in the water jacket 33 is performed via the wall surface of the low temperature side cylinder 25, the working gas is cooled and contracted, and the expansion gas passes through the communication pipe 26 to the expansion chamber 31. The same process is repeated thereafter. The expansion and contraction of the working gas generates kinetic energy for reciprocating the high temperature side piston 27 and the low temperature side piston 28 in the high temperature side cylinder 24 and the low temperature side cylinder 25, respectively. The output shaft 29 rotates and the generator 22 is driven.

  Here, the cooling medium is supplied to the water jacket 33 by circulation in the cooling medium circulation circuit 35. Specifically, the cooling medium stored in the cooling medium storage tank 34 is led out to the cooling medium conduction pipe 37 a by the second pump 36, and the heat exchanger 16 passes through the cooling medium conduction pipe 37 b by pressurization of the second pump 36. To be supplied. In the heat exchanger 16, heat exchange between the cooling medium and the working medium is performed. The cooling medium that has exchanged heat with the working medium is sent out to the cooling medium conducting pipe 37c and supplied to the water jacket 33, and heat exchange between the cooling medium and the working gas is performed.

  The cooling medium subjected to heat exchange with the working gas is sent from the water jacket 33 to the cooling medium conducting pipe 37d and supplied to the exhaust heat recovery unit 37h. When passing through the exhaust heat recovery section 37h, heat exchange between the cooling medium and the combustion exhaust (generated by the heater 13) inside the exhaust heat recovery device 14 is performed. The cooling medium that has exchanged heat with the combustion exhaust (generated by the heater 13) inside the exhaust heat recovery unit 14 is sent from the exhaust heat recovery unit 37h to the cooling medium storage tank 34, and is sent to the cooling medium storage tank 34. Stored again. When the circulation of the cooling medium is continued, the temperature of the cooling medium in the cooling medium storage tank 34 gradually increases, and thermal energy is accumulated in the cooling medium storage tank 34.

  When the user of the energy conversion system 1A uses the thermal energy in the cooling medium storage tank 34, the valve 34c of the outflow pipe 34a is opened to allow the cooling medium in the cooling medium storage tank 34 to flow out. On the other hand, when replenishing the cooling medium in the cooling medium storage tank 34, the cooling medium is injected into the cooling medium storage tank 34 from the inflow pipe 34b. In addition, the cooling medium storage tank 34 is replenished (injected) with a cooling medium so as to be always full.

  As described above, according to this embodiment, in the energy conversion system 1A including the Rankine cycle circuit 11 and the Stirling engine 12, the cooling medium for cooling the low temperature side cylinder 25 of the Stirling engine 12 and the Rankine cycle circuit 11 By including the heat exchanger 16 that exchanges heat with the working medium, it is possible to directly exchange heat between the cooling medium and the working medium. As a result, the exhaust heat of the Rankine cycle circuit 11 and the exhaust heat of the Stirling engine 12 can be recovered only by the cooling medium without interposing a second cooling medium for recovering the exhaust heat. Also, a conduction pipe for conducting the second cooling medium is provided, a condenser for exchanging heat between the second cooling medium and the working medium, and a vaporizer for exchanging heat between the second working medium and the cooling medium are separately provided. The configuration of the entire system can be simplified.

  In this embodiment, the cooling medium led out from the cooling medium storage tank 34 is subjected to heat exchange with the working medium in the heat exchanger 16 and then through the wall surface of the low temperature side cylinder 25 in the water jacket 33. Heat exchange with the working gas takes place. Here, the temperature of the working medium after being expanded in the expander 15 is heated in the expansion chamber 31 of the Stirling engine 12 and expanded, and then the temperature of the working gas sent to the contraction chamber 32 and the wall surface of the low temperature side cylinder 25 is increased. It is lower than the temperature. On the other hand, during normal use, the temperature of the cooling medium passing through the heat exchanger 16 is lower than the temperature of the working medium after being expanded in the expander 15.

  That is, in this embodiment, the heat exchanger 16 is supplied with the working medium that has passed through the expander 15 and converted into kinetic energy and the cooling medium before being supplied to the water jacket 33. Thus, after the heat exchange between the relatively low temperature working medium after passing through the expander 15 and the cooling medium lower in temperature than the working medium is performed to cool the working medium with the cooling medium, the cooling medium is heated to a relatively high temperature. Can be supplied to the water jacket 33 around the low temperature side cylinder 25. As a result, exhaust heat remaining after expansion of the working medium can be recovered without reducing the efficiency of heat exchange, and the working medium, the low temperature side cylinder 25 and the working gas can be cooled by the cooling medium.

  According to this embodiment, the heater 13 that heats the heating unit 18 d of the Rankine cycle circuit 11 and the high temperature side cylinder 24 of the Stirling engine 12, and the exhaust heat recovery device 14 that passes the heat generated from the heater 13, Is provided, and the exhaust heat recovery part 37h for allowing the coolant to pass through is disposed in the exhaust heat recovery unit 14, so that it is not used when heating the working medium or the high temperature side cylinder 24 out of the heat generated by the heater 13. Since the exhausted heat can be recovered by the cooling medium passing through the exhaust heat recovery unit 37h, the amount of heat discarded can be reduced.

  In this embodiment, after the heat exchange is performed in the water jacket 33, the cooling medium is supplied to the exhaust heat recovery unit 37h and is combusted and exhausted inside the exhaust heat recovery unit 14 (of the heater 13). The heat exchange with is performed. Here, the temperature of the combustion exhaust inside the exhaust heat recovery device 14 is higher than the temperature of the working gas sent from the expansion chamber 31 to the contraction chamber 32 and the temperature of the wall surface of the low temperature side cylinder 25.

  That is, in this embodiment, the exhaust heat recovery part 37h is provided in the middle of the cooling medium conducting pipe 37d connected to the water jacket 33, and the cooling medium exchanges heat with the wall surface of the contraction chamber 32 and the working gas. After that, by performing heat exchange with the combustion exhaust (of the heater 13) of the exhaust heat recovery device 14, the exhaust heat of the heater 13 can be recovered by the cooling medium without reducing the efficiency of heat exchange.

  In this embodiment, by providing the cooling medium storage tank 34 that stores the cooling medium that has passed through the water jacket 33, the exhaust heat recovered by the cooling medium can be stored in the cooling medium storage tank 34. Further, the stored cooling medium can be taken out, and the exhaust heat recovered by the cooling medium and the cooling medium can be used for multiple purposes.

  In this embodiment, the coolant stored in the coolant storage tank 34 is supplied to the water jacket 33, and the coolant is circulated between the coolant storage tank 34 and the water jacket 33. 37c, the Stirling engine 12 can be cooled with the cooling medium stored in the cooling medium storage tank 34, and the cooling medium can be circulated between the Stirling engine 12 and the cooling medium storage tank 34. Further, the utilization efficiency of the cooling medium can be increased. Further, by storing the continuously circulating cooling medium in the cooling medium storage tank 34, a large amount of heat can be stored in the cooling medium storage tank 34, and convenience when taking out the cooling medium and using the heat is enhanced.

  According to this embodiment, the generators 20 and 22 are provided, and the generators 20 and 22 are connected to the output shaft 29 of the Stirling engine 12 and the output shaft 19 of the expander 15 of the Rankine cycle circuit 11, respectively. Since the rotational kinetic energy is supplied to and driven by the generator 22, the generators 20 and 22 can be driven by the energy output from the Stirling engine 12 and the Rankine cycle circuit 11.

  Here, the energy efficiency in this embodiment shown as an example of the calculation of the present invention will be considered. FIG. 3 is an energy flow diagram during power generation in the energy conversion system 1A according to this embodiment, and FIG. 4 is a Mollier diagram when the Rankine cycle circuit 11 is driven in the energy conversion system 1A of this embodiment. is there.

  For example, in the energy conversion system 1A, the working medium flowing through the heating unit 18d is heated to about 175 ° C. by the heating of the heater 13 (h1 in FIGS. 4 and 1), and the working gas inside the expansion chamber 31 is heated to about 800 ° C. Consider the case. When this working medium expands in the expander 15, the temperature of the working medium when it is sent out from the expander 15 becomes about 60 ° C. (h2 in FIGS. 4 and 1) and is supplied to the heat exchanger 16. If the temperature of the cooling medium supplied to the heat exchanger 16 is about 15 ° C., the temperature of the working medium when being sent out from the heat exchanger 16 is about 30 ° C. (h3 in FIGS. 4 and 1), and the first pump 17 (h4 in FIGS. 4 and 1). As a result, as shown in FIG. 4, when the theoretical shaft output of the expander is 22.5% and the Rankine efficiency is 70%, the shaft output of the expander 15 (that is, the output of the Rankine cycle circuit 11) is 16%. Become.

On the other hand, when the temperature of the cooling medium supplied to the water jacket 33 is about 30 ° C., when the working gas expanded in the expansion chamber 31 of the Stirling engine 12 is sent to the contraction chamber 32, the working gas is cooled to about 70 ° C. Is done. Here, if the Stirling engine 12 is driven as a Carnot cycle, from the output shaft 29 of Stirling engine _{12 η TH = 1-T C} / T H ··· ( wherein A)
However, η _TH : Carnot efficiency, T _C : low temperature side gas temperature, T _H : high temperature side gas temperature.
In the above (Formula A), if T _C = 70 + 273.15 (K) and T _H = 800 + 273.15 (K), η _TH ≈68%. Further, assuming that the regenerator efficiency is 61% and the heat transfer efficiency is 72%, the efficiency of the Stirling engine 12 is about 30% (0.68 × 0.61 × 0.72≈0.30).

  Then, as shown in FIG. 3, considering the case where the heater 13 of the energy conversion system 1A of this embodiment is heated at a calorific value of 4 kW, the output shaft 29 of the Stirling engine 12 is 0.73 kW (ie, The output shaft 19 of the expander 15 of the Rankine cycle circuit 11 is driven by 0.15 kW (30% of the thermal energy (2.42 kW) input to the high temperature side cylinder 24 of the Stirling engine 12). That is, from 16% (0.22 kW) of the heat energy (1.38 kW) input to the heating unit 18d of the Rankine cycle circuit 11, the output loss of the Rankine cycle circuit 11 is 32% (0.22 kW × 0.32 = 0). .0 (kW)) minus the output). Here, if the power generation efficiency of the generators 22 and 20 is 80%, the power generation end output of the generator 22 is 0.58 kW (0.73 (kW) × 0.8≈0.66 (kW)). The end output is 0.12 kW (0.15 (kW) × 0.8 = 0.12 (kW)), and a total of about 0.7 kW is generated. Furthermore, in this energy conversion system 1A, if 90% of the energy not used to drive the Stirling engine 12 and the expander 15 is recovered by the cooling medium and accumulated in the cooling medium storage tank 34, 2.1 kW. Is stored in the cooling medium storage tank 34. Therefore, the total energy amount acquired by the energy conversion system 1A is 2.8 kW (0.7 (kW) +2.1 (kW) = 2.8 (kW)), and the total efficiency ( The ratio of the acquired energy to the fuel (or “energy”) used in the heater 13 (same in this specification) is 70.0%.

  That is, in this embodiment, the Rankine cycle circuit 11 and the Stirling engine 12 are driven by one heater 13 so that the generators 22 and 20 are driven, and the working medium of the Rankine cycle circuit 11 and the Stirling engine 12 are driven. By cooling the working gas and recovering the exhaust heat inside the exhaust heat recovery unit 14 with the cooling medium of the Stirling engine 12 and accumulating it in the cooling medium storage tank 34, high energy conversion efficiency can be obtained. Furthermore, in this embodiment, the heat loss (a) in the Stirling engine 12 shown in FIG. 3 and the Rankine cycle circuit 11 are performed by directly exchanging heat between the cooling medium and the working medium in the heat exchanger 16. Energy loss (b) can be further reduced, and higher energy conversion efficiency can be obtained.

[Embodiment 2 of the Invention]
5 and 6 show a second embodiment.

  In the energy conversion system 1B of this embodiment, the output shaft 29 of the Stirling engine 12 and the output shaft 19 of the expander 15 are connected, and the generator 22 is connected only to the output shaft 29 of the Stirling engine 12, and the generator 22 is connected. It has a configuration in which rotational kinetic energy is supplied.

  As shown in FIG. 6, the Stirling engine 12 includes a generator 22 and an expander 15 that are integrally formed. Specifically, the generator chamber 23 is formed on one side (right side in FIG. 6) of the crank chamber 12a of the housing 38, and the expander 15 is provided on the other side. A partition wall 39 separates the crank chamber 12a and the expander 15 from each other.

  The other end of the output shaft 29 of the Stirling engine 12 is connected to the output shaft 19 of the expander 15. As shown in FIG. 6, a rotation adjusting unit 40 that mechanically adjusts the rotation speed of each of the output shafts 29 and 19 is provided at a connecting portion between the output shaft 29 of the Stirling engine 12 and the output shaft 19 of the expander 15. It has been. The rotation adjusting unit 40 is formed by a speed change mechanism such as a planetary gear mechanism, and is provided in the partition wall 39. Other configurations are the same as those of the first embodiment.

  Next, the operation of this embodiment will be described.

  When the Stirling engine 12 operates, the output shaft 29 rotates. When the working medium circulates through the Rankine cycle circuit 11 and the expander 15 is driven, the output shaft 19 rotates. Since the output shafts 29 and 19 are connected, the kinetic energy of one or both of the output shaft 29 and the output shaft 19 is transmitted to the generator 22, and rotational kinetic energy is supplied to the generator 22 to be driven.

  When both the Stirling engine 12 and the expander 15 are driven, the rotational kinetic energy of the output shafts 29 and 19 is supplied to the generator 22, and the generator 22 is driven by this kinetic energy. Since the rotation adjusting portion 40 is provided at the connecting portion of the output shafts 29 and 19, when the output shafts 29 and 19 are rotating at different rotational speeds, the rotation adjusting portion 40 is connected to the output shafts 29 and 19 respectively. Is adjusted so that both output shafts 29 and 19 are rotated at a predetermined rotation ratio. Then, kinetic energy as a resultant force of the output shafts 29 and 19 is transmitted to the generator 22 in a state where the rotation speeds of the output shafts 29 and 19 are synchronized.

  That is, according to this embodiment, the output shaft 29 of the Stirling engine 12 and the output shaft 19 of the expander 15 are connected, and the rotational kinetic energy of the Stirling engine 12 and the expander 15 is supplied to the generator 22. By being driven, the coupled output shafts 29 and 19 are operated by the driving force of the Stirling engine 12 and the driving force of the expander 15 of the Rankine cycle circuit 11 to increase the torque, and the coupled output. A large output can be obtained from one generator 22 connected to the shafts 29 and 19.

  Further, according to this embodiment, the connecting portion between the output shaft 29 of the Stirling engine 12 and the output shaft 19 of the expander 15 is adjusted by adjusting the rotational speeds of the output shafts 29 and 19 by a mechanism. The rotation adjusting unit 40 that rotates the output shafts 29 and 19 at a predetermined rotation ratio is provided, so that the rotation of the output shafts 29 and 19 depends on the drive state of the Stirling engine 12 and the Rankine cycle circuit 11. Even if the numbers are different, the rotation adjusting unit 40 adjusts the difference in the rotation number to synchronize the rotation number, and the resultant force of the Stirling engine 12 and the expander 15 can be obtained, and the transmission loss of energy to the generator 22 occurs. Can be suppressed.

  According to this embodiment, since the rotation adjusting unit 40 is formed by a gear mechanism such as a planetary gear mechanism, the rotation speed of each of the coupled output shafts 29 and 19 is adjusted using a mechanism. It can be realized by a simple device.

  In this embodiment, the generator 22 is connected to the output shaft 29 of the Stirling engine 12. However, the generator 22 may be connected to the output shaft 19 of the expander 15 instead. .

  In this embodiment, the rotation adjusting unit 40 is formed as a planetary gear mechanism, but is not limited thereto, and may be formed by a gear mechanism other than the planetary gear mechanism, a torque converter, a continuously variable transmission, or the like. Moreover, you may form combining some or all, such as a gear mechanism, a torque converter, a continuously variable transmission.

Embodiment 3 of the Invention
FIG. 7 shows an embodiment of the present invention.

  In the energy conversion system 1C of this embodiment, the generator chamber 23 is provided on one side (right side in FIG. 7) of the crank chamber 12a of the housing 49, and the expander 15 is provided on one side of the generator chamber 23. The generator chamber 23 and the expander 15 are penetrated, and the Stirling engine 12 and the generator chamber 23 are partitioned by a partition wall 41.

  One end of the output shaft 29 of the Stirling engine 12 is connected to the output shaft 19 of the expander 15. A rotation adjusting unit 40 is provided at a connecting portion between the output shaft 29 of the Stirling engine 12 and the output shaft 19 of the expander 15, and the rotation adjusting unit 40 is connected to one side of the generator chamber 23.

  Further, one end of the working medium conducting pipe 18 b through which the working medium after expansion is connected is connected to the generator chamber 23 and the other end is connected to the heat exchanger 16. Other configurations are the same as those of the second embodiment.

  In this embodiment, the working medium expanded in the expander 15 is discharged into the generator chamber 23 and then supplied to the heat exchanger 16 through the working medium conducting pipe 18b. The temperature of the working medium supplied to the generator chamber 23 is sufficiently lower than that of the generator 22. Therefore, the generator 22 is cooled when the working medium passes through the generator chamber 23, so that overheating of the generator 22 can be suppressed. .

[Embodiment 4 of the Invention]
FIG. 8 shows an embodiment of the present invention.

  In the energy conversion system 1D of this embodiment, the cooling medium flowing out from the cooling medium storage tank 34 as the cooling medium flow path and flowing into the heat exchanger 16 flows from the second pump 36 to the cooling medium conducting pipe 37b. The cooling medium conducting pipe 42 as the “first cooling medium flow path” and the “second cooling medium flow for allowing the cooling medium sent from the second pump 36 to the cooling medium conducting pipe 37 b to flow into the water jacket 33. A cooling medium conducting tube 43 as a “path” is provided.

  One end of the coolant supply pipes 37 b, 42, 43 is connected to the coolant flow rate adjustment valve 44, the other end of the coolant supply pipe 42 is connected to the heat exchanger 16, and the other end of the coolant supply pipe 43. The part is connected to the water jacket 33. The other end of the cooling medium conducting pipe 37c whose one end is connected to the cooling medium outflow side of the heat exchanger 16 is the cooling medium conducting pipe whose one end is connected to the cooling medium outflow side of the water jacket 33. The cooling medium flow path is joined in the middle of 37d.

  The cooling medium flow rate adjustment valve 44 is a three-way valve, and adjusts the amount of the cooling medium sent to the cooling medium conducting pipes 42 and 43, respectively. Other configurations are the same as those of the second embodiment.

  Next, the operation of this embodiment will be described.

  The cooling medium flowing out from the cooling medium storage tank 34 is sent out from the second pump 36 to the cooling medium conducting pipe 37b and supplied to the cooling medium flow rate adjustment valve 44. It flows out to the cooling medium conducting pipes 42 and 43. The cooling medium flowing out to the cooling medium conducting pipe 42 is supplied to the heat exchanger 16 and performs heat exchange with the working medium. The cooling medium flowing out to the cooling medium conducting pipe 43 is supplied to the water jacket 33 and performs heat exchange with the low temperature side cylinder 25 and the working gas. The cooling medium flowing out from the heat exchanger 16 to the cooling medium conduction pipe 37c and the cooling medium flowing out from the water jacket 33 to the cooling medium conduction pipe 37d merge, and then in the exhaust heat recovery section 37h, the (heater 13) is exchanged with the combustion exhaust gas, and is stored again in the cooling medium storage tank 34.

  As described above, in this embodiment, the cooling medium flow pipe 42 that allows the cooling medium flowing out from the cooling medium storage tank 34 to flow into the heat exchanger 16 and the cooling medium that flows out from the cooling medium storage tank 34 are used as the cooling medium flow path. By providing the cooling medium conducting pipe 43 for allowing the medium to flow into the water jacket 33, the cooling medium flowing out from the cooling medium storage tank 34 can be directly supplied to the water jacket 33, and the thermal efficiency of the Stirling engine 12 is improved. Can be made. Further, by providing the cooling medium flow rate adjusting valve 44 for adjusting the flow rate of the cooling medium to each of the cooling medium conducting pipes 42 and 43, the Rankine cycle circuit 11 is based on the operating state of the Rankine cycle circuit 11 or the Stirling engine 12. The flow rate of the cooling medium used for cooling the working medium and the flow rate of the cooling medium used to increase the cooling efficiency of the Stirling engine 12 can be controlled.

[Embodiment 5 of the Invention]
FIG. 9 shows an embodiment of the present invention.

  In the energy conversion system 1E of this embodiment, the cooling medium conducting tube 45 for allowing the cooling medium to flow into the cooling medium circulation circuit 35 from the outside, and the “for cooling medium flowing out from the cooling medium circulation circuit 35” to the outside. Cooling medium conducting pipes 46a, 46b, 46c as "external flow paths" are provided.

  One end of the cooling medium conduction pipe 37c is connected to the cooling medium conduction pipe 37d connected to the cooling medium outflow side of the water jacket 33, and the connected portion and the exhaust heat recovery section 37h are connected to each other. In the middle of the cooling medium conducting pipe 37d, an inflow amount adjusting valve 47 is provided. One end of the cooling medium conduction pipe 46a is connected to the middle of the cooling medium conduction pipe 37d through which the cooling medium that has passed through the exhaust heat recovery section 37h (and the water jacket 33) conducts, and one end of the cooling medium conduction pipe 46b is cooled. The medium storage layer 34 is connected. The other end portions of the coolant supply pipes 46 a and 46 b and the one end portion of the coolant supply pipe 46 c are connected to the outflow amount adjusting valve 48.

  The inflow amount adjusting valve 47 and the outflow amount adjusting valve 48 are three-way valves, and the amount of the cooling medium flowing into the cooling medium conduction pipe 37d from the outside and the cooling medium flowing out from the cooling medium conduction pipe 37d and the cooling medium storage tank 34. Adjust the amount. Other configurations are the same as those of the fourth embodiment.

  Next, the operation of this embodiment will be described.

  When taking out the cooling medium circulating through the cooling medium circulation circuit 35 to the outside, the outflow amount adjusting valve 48 is opened, and the cooling medium flowing out from the cooling medium conduction pipe 46a or the cooling medium conduction pipe 46b is discharged from the cooling medium conduction pipe 46c to the outside. Spill. On the other hand, when adding the cooling medium from the outside to the cooling medium circulation circuit 35, the inflow amount adjusting valve 47 is opened, and the cooling medium flowing in from the cooling medium conduction pipe 45 is caused to flow into the cooling medium conduction pipe 37d.

  As described above, in this embodiment, the cooling medium conducting pipes 46a and 46c for letting out the cooling medium that has passed through the water jacket 33 and the exhaust heat recovery unit 37h to the outside, and the cooling medium stored in the cooling medium storage layer 34 are externally supplied. By providing the cooling medium conducting pipes 46b and 46c that flow out into the cooling medium, the cooling medium from which the exhaust heat has been recovered can be easily taken out. Further, the flow rate of the cooling medium, that is, the outflow amount adjustment for adjusting the outflow amount of the cooling medium from the cooling medium conduction pipe 46a and / or the cooling medium conduction pipe 46b to the cooling medium conduction pipe 46c and the discharge amount from the cooling medium conduction pipe 46c. By providing the valve 48, it is possible to control the amount of outflow from the cooling medium conducting pipes 46a and 46b and the amount of water discharged from the cooling medium conducting pipe 46c when the cooling medium is taken out.

  Further, in this embodiment, even if the Rankine cycle circuit 11 and the Stirling engine 12 are not in operation due to the provision of the cooling medium conduction pipes 46a, 46b, 46c and the inflow amount adjusting valve 47. The cooling medium can be used by heating. For example, when the circulation of the cooling medium in the cooling medium circulation circuit 35 is stopped for some reason (for example, the second pump 36 is stopped, the cooling medium flow rate adjustment valve 44 is malfunctioning, the cooling medium conduction pipes 37a, 37b, 37c). If the circulation of the cooling medium in the cooling medium circulation circuit 35 is stopped for an intentional reason (for example, it is stored in the cooling medium storage layer 34 in a full state). When the cooling medium has just been stored and cannot be used as a heat source (that is, when the cooling medium is in the state of cold water and cannot be used as hot water, etc.), the cooling medium is adjusted by adjusting the inflow rate adjusting valve 47. The flow path of the cooling medium flowing out from the conduction pipe 37a is closed and the cooling medium conduction pipes 45 and 37d, the exhaust heat recovery part 37h, and the cooling medium conduction pipes 37d and 46a. By forming a flow path for conducting the cooling medium in the order of 46c, the low-temperature cooling medium (cold water) introduced from the cooling medium conduction pipe 45 is heated in the exhaust heat recovery unit 37h, and the high-temperature cooling medium (hot water) is supplied. It becomes possible to take out from the cooling medium conducting tube 46c.

Embodiment 6 of the Invention
10 and 11 show an embodiment of the present invention.

  In the energy conversion system 1F of this embodiment, in addition to the Rankine cycle circuit 11 and the Stirling engine 12, a refrigeration air conditioning cycle circuit 50 that circulates the second working medium is provided. This refrigerating and air-conditioning cycle circuit 50 includes a compressor 51, a third heat exchanger 52, an expansion valve 53, and an indoor heat exchanger 54 as a “second heat exchanger”, and these include a second working medium conduction pipe 55a, The second working medium circulation path is formed by being connected by 55b, 55c, and 55d. For example, R134a, R407C, R410A, or carbon dioxide is used as the second working medium, but other substances that are easily liquefied by compression and have large heat of vaporization may be used as the working medium.

  The compressor 51 is, for example, a scroll compressor, and compresses the second working medium based on rotational kinetic energy.

  The third heat exchanger 52 is a condenser, and performs heat exchange between the second working medium and the cooling medium of the Stirling engine 12. The third heat exchanger 52 has a cooling medium conduction pipe 37b connected to the cooling medium inflow side, and one end of the cooling medium conduction pipe 37e connected to the inflow side of the heat exchanger 16 on the cooling medium outflow side. The other end is connected.

  The expansion valve 53 expands the second working medium in the liquid state and releases the second working medium in the gas-liquid mixed state. However, a capillary (capillary tube) or the like may be used instead of the expansion valve 53 as long as it has the same function.

  The indoor heat exchanger 54 is an evaporator, and includes an air blowing fan, forcibly exchanging heat between the second working medium passing through and the indoor air.

  In this embodiment, a compressor 51 is connected to the output shaft 29 of the Stirling engine 12 instead of the generator 22 in the second embodiment.

  Other configurations are the same as those of the second embodiment.

  Next, the operation of this embodiment will be described.

  When the Stirling engine 12 or the expander 15 is operated, the compressor 51 is driven by the kinetic energy of the output shaft 29 to compress the second working medium. The high-temperature and high-pressure second working medium compressed by the compressor 51 is supplied to the third heat exchanger 52 through the second working medium conducting pipe 55b and condensed by heat exchange with the cooling medium. The liquid second working medium condensed by heat exchange is supplied to the expansion valve 53 via the second working medium conducting pipe 55c and expands. The expanded low-temperature and low-pressure second working medium is supplied to the indoor heat exchanger 54 via the second working medium conducting pipe 55d in a gas-liquid mixed state, and evaporated to exchange heat with indoor air by the latent heat of vaporization. As a result, cold air is supplied indoors, and the second working medium is vaporized and the temperature rises. The second working medium that has exchanged heat with the indoor air is supplied from the indoor heat exchanger 54 through the second working medium conducting pipe 55a to the compressor 51 and compressed again, and the same circulation of the second working medium is performed thereafter. Done.

  In this embodiment, a refrigerating and air-conditioning cycle circuit 50 including a compressor 51 that compresses a second working medium and an indoor heat exchanger 54 that performs heat exchange between indoor air and the second working medium is provided. Provided, the compressor 51 is connected to the output shaft 29 of the Stirling engine 12 to supply a driving force to the refrigerating and air-conditioning cycle circuit 50 with at least one of the outputs of the Stirling engine 12 and the expander 15. An air conditioner that heats or cools indoor air by the heat exchanger 54 can be realized.

  In this embodiment, the second working medium is provided with the third heat exchanger 52 that exchanges heat between the second working medium of the refrigeration air-conditioning cycle circuit 50 and the cooling medium of the Stirling engine 12. Can be cooled with a cooling medium. Thereby, heat exchange can be performed between system components including the refrigeration air conditioning cycle circuit 50, and high energy conversion efficiency can be obtained.

  In this embodiment, the compressor 51 is connected to the output shaft 29 of the Stirling engine 12, but the compressor 51 may be connected to the output shaft 19 of the expander 15 instead. Further, the circulation of the second working medium in this embodiment can be reversed, and the third heat exchanger 52 can be used as an evaporator and the indoor heat exchanger 54 can be used as a condenser to heat the room indoors. .

  Here, the energy efficiency at the time of cooling in this embodiment shown as an example of the calculation of the present invention will be considered. FIG. 11 is an energy flow diagram during cooling in the energy conversion system 1F according to this embodiment. As in the case of FIG. 3, the heater 13 is heated with a heating value of 4 kW in the heater 13, the output shaft 29 of the Stirling engine 12 is 0.73 kW, the output shaft 19 of the expander 15 of the Rankine cycle circuit 11 is 0. A case where the compressor 51 is driven by driving with an output of 15 kW is shown. In this case, if the transmission efficiency of the generators 22 and 20 is 90%, the shaft output on the generator 22 side is 0.66 kW (0.73 (kW) × 0.9≈0.66 (kW)), and the generator 20 side The output of the shaft is 0.13 kW (0.15 (kW) × 0.9 = 0.13 (kW)). When COP (Coefficient of Performance) = 3, the total output is about 2.37 kW ({0.66 (KW) +0.13 (kW)} × 3.0≈2.37 (kW) Further, 2.1 kW of thermal energy is accumulated in the cooling medium storage tank 34 as in the case of FIG. Therefore, the total energy amount acquired by this energy conversion system 1F is 4.47 kW (2.37 (kW) +2.1 (kW) = 4.47 (kW)), and the total efficiency of this energy conversion system 1F Is 112%.

  That is, also in this embodiment, high energy conversion efficiency can be obtained as in the case of the first embodiment. Furthermore, also in this embodiment, the heat loss in the Stirling engine 12 shown in FIG. 10 and the Rankine cycle circuit 11 are performed by directly exchanging heat between the cooling medium and the working medium in the heat exchanger 16. Energy loss (d) can be further reduced, and higher energy conversion efficiency can be obtained.

Embodiment 7 of the Invention
FIG. 12 shows an embodiment of the present invention.

  In the energy conversion system 1G of this embodiment, as the cooling medium flow path, the cooling medium as the “third cooling medium flow path” for flowing the cooling medium flowing out from the cooling medium storage tank 34 into the heat exchanger 16. A conduction pipe 56 a and a cooling medium conduction pipe 56 b as a “fourth cooling medium flow path” through which the cooling medium flowing out from the cooling medium storage tank 34 flows into the third heat exchanger 52 are provided. One end of the cooling medium conduction pipe 56 a is connected to the inflow side of the heat exchanger 16, and one end of the cooling medium conduction pipe 56 b is connected to the inflow side of the third heat exchanger 52. The other ends of the cooling medium conduction pipes 56a and 56b are connected to a cooling medium flow rate adjustment valve 57 as a “second cooling medium flow rate adjustment valve” connected to the cooling medium conduction pipe 37b. The cooling medium flow rate adjustment valve 57 is a three-way valve, and adjusts the flow rate of the cooling medium with respect to the cooling medium conduction pipes 56a and 56b. The cooling medium conduction pipe 37 c connected to the heat exchanger 16 and the water jacket 33 branches in the middle, and the branched cooling medium conduction pipe 37 f is connected to the outflow side of the third heat exchanger 52. Other configurations are the same as those of the sixth embodiment.

  Next, the operation of this embodiment will be described.

  The cooling medium that has flowed out of the cooling medium storage tank 34 is sent out from the second pump 36 and supplied to the cooling medium flow rate adjustment valve 57, and the respective cooling medium conduction pipes 56 a, 56 a, It flows out to 56b. The cooling medium flowing out to the cooling medium conducting pipe 56a is supplied to the heat exchanger 16 and performs heat exchange with the working medium. The cooling medium flowing out to the cooling medium conducting pipe 56b is supplied to the third heat exchanger 52 and performs heat exchange with the second working medium. The cooling medium flowing out from the heat exchanger 16 to the cooling medium conduction pipe 37 c and the cooling medium flowing out from the third heat exchanger 52 to the cooling medium conduction pipe 37 f merge and are supplied to the water jacket 33.

  In this embodiment, the third heat exchanger 52 and the heat exchanger 16 are provided, respectively, and the cooling medium flowing out from the cooling medium storage tank 34 is flown into the heat exchanger 16 as a cooling medium flow path. By providing the medium conduction pipe 56a and the cooling medium conduction pipe 56b for allowing the cooling medium flowing out from the cooling medium storage tank 34 to flow into the third heat exchanger 52, the cooling medium is cooled and operated. It can be used together with the cooling of the medium. Further, by providing a cooling medium flow rate adjusting valve 57 for adjusting the flow rate of the cooling medium to the respective cooling medium conducting pipes 56a and 56b, the refrigerating and air conditioning based on the operating states of the refrigerating and air conditioning cycle circuit 50 and Rankine cycle circuit 11 is provided. The flow rate of the cooling medium used for cooling the cycle circuit 50 and the flow rate of the cooling medium used for cooling the Rankine cycle circuit 11 can be controlled.

[Embodiment 8 of the Invention]
FIG. 13 shows an embodiment of the present invention.

  In the energy conversion system 1H of this embodiment, the refrigeration air conditioning cycle circuit 50 includes a fourth heat exchanger 58 instead of the third heat exchanger 52 in the sixth embodiment. The fourth heat exchanger 58 is a condenser having a blower fan, and forcibly exchanges heat between the second working medium passing therethrough and outdoor air. The heat exchanger 16 and the water jacket 33 are connected by a cooling medium conducting tube 37c. Other configurations are the same as those of the sixth embodiment.

  Next, the operation of this embodiment will be described.

  In the refrigeration air conditioning cycle circuit 50, the second working medium compressed by the compressor 51 is supplied to the fourth heat exchanger 58 via the second working medium conducting pipe 55b. The fourth heat exchanger 58 forcibly exchanges heat between the second working medium and the surrounding air, thereby cooling the second working medium. The cooled second working medium is supplied to the expansion valve 53 via the second working medium conducting pipe 55c.

  In this embodiment, the refrigeration air-conditioning cycle circuit 50 includes the fourth heat exchanger 58 that forcibly exchanges heat between the second working medium and outdoor air. The working medium can be cooled without relying on heat exchange with the cooling medium or the working medium.

  It should be noted that the circulation of the second working medium in this embodiment can be reversed, and the fourth heat exchanger 58 can be used as an evaporator and the indoor heat exchanger 54 can be used as a condenser to heat the room indoors. .

Embodiment 9 of the Invention
FIG. 14 shows an embodiment of the present invention.

  In the energy conversion system 1 </ b> I of this embodiment, a compressor 51 and a generator 22 are connected to the output shaft 29 of the Stirling engine 12. A rotation adjusting unit 59 for adjusting the transmission state of the driving force output from the Stirling engine 12 and the expander 14 to the compressor 51 and the generator 22 is provided at a connection portion between the output shaft 29 and the compressor 51 and the generator 22. It has been. The rotation adjusting unit 59 is a speed change and power distribution mechanism, and is formed by, for example, a clutch mechanism and a gear mechanism. Other configurations are the same as those of the sixth embodiment.

  Next, the operation of this embodiment will be described.

  When at least one of the Stirling engine 12 and the expander 15 operates, the output shaft 29 rotates. The kinetic energy of the output shaft 29 is transmitted to at least one of the compressor 51 and the generator 22 under the control of the rotation adjusting unit 59, and at least one of the compressor 51 and the generator 22 that receives the kinetic energy is rotated. To do. Further, the rotational state such as the rotational speed at this time is adjusted by the control of the rotation adjusting unit 59. That is, the output shaft 29 and the output shaft of the compressor 51 or the generator 22 can be rotated at a predetermined rotation ratio.

  In this embodiment, the compressor 51 and the generator 22 are connected to the output shaft 29 of the Stirling engine 12, and the connecting portion between the output shaft 29, the compressor 51 and the generator 22 includes the Stirling engine 12 and the expander 15. A rotation adjusting unit 59 that adjusts the transmission state of the driving force output from at least one of the compressor 51 and the generator 22 to one or both of them is connected to one output shaft 29. With respect to the compressor 51 and the generator 22, it is possible to select a driving target and control a driving state.

  Thereby, for example, when the refrigerating and air conditioning cycle circuit 50 is not driven, the rotation adjusting unit 59 is switched so that the kinetic energy of the output shaft 29 is transmitted to the generator 22 and the refrigerating and air conditioning cycle circuit 50 is driven. Control to switch the rotation adjusting unit 59 so that the kinetic energy of the output shaft 29 is transmitted to the compressor 51 becomes possible.

  In this embodiment, the compressor 51, the generator 22, and the rotation adjusting unit 59 are connected to the output shaft 29 of the Stirling engine 12. However, instead of this, the compressor 51 is connected to the output shaft 19 of the expander 15. The generator 22 and the rotation adjusting unit 59 may be connected.

  Further, in this embodiment, the rotation adjusting unit 59 is formed by a clutch mechanism and a gear mechanism, but is not limited to this, and may be formed by a planetary gear mechanism, a torque converter, a continuously variable transmission, etc. Moreover, you may form combining some or all, such as a clutch mechanism, a gear mechanism, a torque converter, a continuously variable transmission.

[Embodiment 10 of the invention]
15 to 17 show an embodiment of the present invention.

  In the energy conversion system 1J of this embodiment, a four-way valve 61 is provided in the refrigerating and air-conditioning cycle circuit 50 shown in the eighth embodiment, and one end of the four-way valve 61 is connected to the indoor heat exchanger 54. The other end of the second working medium conduction pipe 55a, the other end of the second working medium conduction pipe 55i, one end of which is connected to the inflow side of the compressor 51, and one end of the second working medium conduction pipe 55a are connected to the outflow side of the compressor 51. The other end of the second working medium conducting tube 55j is connected to the other end of the second working medium conducting tube 55b having one end connected to the fourth heat exchanger 58. Both the indoor heat exchanger 54 and the fourth heat exchanger 58 are configured to be usable both as an evaporator and a condenser.

  The four-way valve 61 switches the flow path of the second working medium in the refrigeration air conditioning cycle circuit 50. That is, the four-way valve 61 forms a first circulation path 50a for using the indoor heat exchanger 54 as an evaporator at the first position shown in FIG. In the second position, a second circulation path 50b for using the indoor heat exchanger 54 as a condenser is formed. Other configurations are the same as those of the eighth embodiment.

  Next, the operation of this embodiment will be described.

  When the four-way valve 61 is in the first position shown in FIG. 15, the fourth heat exchanger 58 functions as a condenser and the indoor heat exchanger 54 functions as an evaporator. In this case, as shown in FIG. 15, when the compressor 51 is driven, the second working medium is supplied to the compressor 51 via the second working medium conducting pipe 55i and compressed, and after being compressed, the second working medium is conducted. It is supplied to the fourth heat exchanger 58 through the pipes 55j and 55b, condensed, condensed, supplied to the expansion valve 53 through the second working medium conducting pipe 55c, expanded, and then expanded. The air is supplied to the indoor heat exchanger 54 through the medium conducting pipe 55d and exchanges heat with the indoor air, whereby cold air is supplied indoors and the second working medium absorbs heat. The second working medium that has exchanged heat with the indoor air is again supplied from the indoor heat exchanger 54 to the compressor 51 via the second working medium conducting pipes 55a and 55i, and is compressed. Circulation is performed.

  On the other hand, when the four-way valve 61 is in the second position shown in FIG. 16, the fourth heat exchanger 58 functions as an evaporator and the indoor heat exchanger 54 functions as a condenser. In this case, as shown in FIG. 16, when the compressor 51 is driven, the second working medium is supplied to the expansion valve 53 via the second working medium conducting pipe 55d to expand and expand, and then the second working medium is conducted. It is supplied to the fourth heat exchanger 58 via the pipe 55c to absorb heat, absorbs heat, is then supplied to the compressor 51 via the second working medium conducting pipes 55b and 55i, is compressed, and is compressed and then the second working medium. It is supplied to the indoor heat exchanger 54 through the conduction pipes 55j and 55a and exchanges heat with indoor air, whereby warm air is supplied indoors and the second working medium dissipates heat. The second working medium that has exchanged heat with the indoor air is supplied again to the expansion valve 53 from the indoor heat exchanger 54 via the second working medium conducting pipe 55d, and then expands. Circulation takes place.

  In this embodiment, in the refrigeration air conditioning cycle circuit 50, the flow path of the second working medium is switched, and the first circulation path 50a and the indoor heat exchanger 54 for using the indoor heat exchanger 54 as an evaporator. By using the four-way valve 61 that forms any one of the second circulation paths 50b for use as a condenser, the indoor heat exchanger 54 can be used for both an indoor unit for cooling and an indoor unit for heating. Become.

  Here, the energy efficiency at the time of heating in this embodiment shown as an example of the calculation of the present invention will be considered. FIG. 17 is an energy flow diagram during heating in the energy conversion system 1J according to this embodiment. In the same figure as in FIGS. 3 and 11, the heater 13 is heated with a heating value of 4 kW, the output shaft 29 of the Stirling engine 12 is 0.73 kW, and the output shaft 19 of the expander 15 of the Rankine cycle circuit 11. Is driven with an output of 0.15 kW, and the compressor 51 is driven. In this case, assuming that the transmission efficiency of the generators 22 and 20 is 90%, the shaft output on the generator 22 side is 0.66 kW, the shaft output on the generator 20 side is 0.13 kW, and when COP = 4.3, the total About 3.4 kW ({0.66 (kW) +0.13 (kW)) × 4.3≈3.4 (kW) Further, 2.1 kW heat as in the case of FIGS. Energy is accumulated in the cooling medium storage tank 34. Therefore, the total amount of energy acquired by the energy conversion system 1J is 5.5 kW (3.4 (kW) +2.1 (kW) = 5.5 (kW) )), And the overall efficiency of the energy conversion system 1F is 137.5%.

  That is, also in this embodiment, high energy conversion efficiency can be obtained as in the first and sixth embodiments. Furthermore, also in this embodiment, by performing heat exchange directly between the cooling medium and the working medium in the heat exchanger 16, the energy loss (e) and Rankine in the Stirling engine 12 shown in FIGS. The energy loss (f) in the cycle circuit 11 can be further reduced, and higher energy conversion efficiency can be obtained.

[Embodiment 11 of the Invention]
FIG. 18 shows an embodiment of the present invention.

  In the energy conversion system 1 </ b> K of this embodiment, a fifth heat exchanger 62 is provided in parallel with the heat exchanger 16 in the Rankine cycle circuit 11. That is, the other end portion side of the working medium conducting pipe 18b whose one end is connected to the expander 15 is branched, and the working medium conducting pipe 63a as the “first working medium flow path” on one side of the branch is a heat exchanger. The working medium that has flowed out of the expander 15 is caused to flow into the heat exchanger 16. On the other hand, the working medium conducting pipe 64a as the “second working medium flow path” on the other side of the branch is connected to the inflow side of the fifth heat exchanger 62, and the working medium flowing out of the expander 15 is supplied to the fifth heat. It flows into the exchanger 62. Furthermore, the other end side of the working medium conduction pipe 18c whose one end is connected to the first pump 17 is branched, and the working medium conduction pipe 63b as the “first working medium flow path” on one side of the branch is heat exchanged. The working medium conducting pipe 64 b connected to the outflow side of the vessel 16 and serving as the “second working medium flow path” on the other side branched is connected to the outflow side of the fifth heat exchanger 62.

  The fifth heat exchanger 62 is a condenser and includes a fan for blowing air, and forcibly exchanges heat between the working medium passing therethrough and ambient air. A working medium flow rate adjustment valve 65 is provided at a portion where the working medium conduction pipe 63b connected to the outflow side of the heat exchanger 16 and the working medium conduction pipe 64b connected to the outflow side of the fifth heat exchanger 62 branch. Is provided. The working medium flow rate adjustment valve 65 is a three-way valve, and adjusts the flow rate of the working medium passing through the heat exchanger 16 and the flow rate of the working medium passing through the fifth heat exchanger 62. The working medium flow rate adjustment valve 65 may be provided at a portion where the working medium conduction pipe 63a and the working medium conduction pipe 64a branch. Other configurations are the same as those of the tenth embodiment.

  Next, the operation of this embodiment will be described.

  When heat exchange is performed on the working medium of the Rankine cycle circuit 11 in the heat exchanger 16, the working medium flow rate adjustment valve 65 is adjusted so that a flow path from the heat exchanger 16 side to the first pump 17 side is formed. Accordingly, the working medium is supplied from the expander 15 to the heat exchanger 16 through the working medium conducting pipe 63a, and is cooled by heat exchange with the cooling medium. On the other hand, when exchanging heat in the fifth heat exchanger 62, the working medium flow rate adjustment valve 65 is adjusted so that a flow path from the fifth heat exchanger 62 side to the first pump 17 side is formed. Thereby, the working medium is supplied from the expander 15 to the fifth heat exchanger 62 through the working medium conducting pipe 64a and cooled by heat exchange with the surrounding air.

  In this embodiment, the fifth heat exchanger 62 that cools the working medium by forcibly exchanging heat between the working medium of the Rankine cycle circuit 11 and the surrounding air is provided. The working medium can be cooled without heat exchange with the cooling medium. In addition, working medium flow pipes 63a and 63b for passing the working medium flowing out from the expander 15 to the heat exchanger 16 and the working medium flowing out from the expander 15 to the fifth heat exchanger 62 as a working medium flow path. The working medium conducting pipes 64a and 64b to be passed are provided, and the working medium conducting pipes 63a and 63b and the working medium conducting pipes 64a and 64b are provided with the working medium flow adjusting valve 65 for adjusting the flow rate of the working medium. The heat energy discharged from the Rankine cycle circuit 11 can be recovered by the cooling medium, or can be forcibly exchanged with the surrounding air to dissipate heat, and heat can be generated based on the operating state of the Stirling engine 12 or the temperature state. Adjusting the flow rate of the working medium for the exchanger 16 and the fifth heat exchanger 62 and driving the Rankine cycle circuit 11 in a good state at all times. Possible to become.

  Accordingly, for example, when the temperature of the cooling medium is sufficiently low and the working medium can be cooled by heat exchange, the working medium flow rate adjustment valve 65 is adjusted so that the working medium passes through the heat exchanger 16, and the temperature of the cooling medium is thereby adjusted. Is increased to a point where it is difficult to cool the working medium, or when the temperature is lower than the temperature of the cooling medium, the working medium flow control valve is set so that the working medium passes through the fifth heat exchanger 62. Control to adjust 65 is possible.

  The energy conversion systems 1A to 1K of the above-described embodiments are formed as home cogeneration systems, but are not limited to this, and can be applied to cogeneration systems for factories and power plants. In addition, the “rotary machine” in each of the above embodiments is formed as the generators 20 and 22 of the cogeneration system, but is not limited to this, and is rotated by the rotational energy of the output shafts 19 and 29 such as a motor and a fan. Any device may be used as the “rotating machine”.

  It is needless to say that each of the above embodiments is an exemplification, and does not mean that the present invention is limited to the above embodiment.

1 is a system configuration diagram of an energy conversion system according to Embodiment 1 of the present invention. It is a conceptual diagram of the energy conversion system which concerns on the same embodiment. It is an energy flow figure at the time of the electric power generation in the energy conversion system concerning the embodiment. It is a Mollier diagram in case the Rankine cycle circuit in the energy conversion system concerning the embodiment operates. It is a system block diagram of the energy conversion system which concerns on Embodiment 2 of this invention. It is a conceptual diagram of the energy conversion system which concerns on the same embodiment. It is a system block diagram of the energy conversion system which concerns on Embodiment 3 of this invention. It is a system configuration | structure figure of the energy conversion system which concerns on Embodiment 4 of this invention. It is a system block diagram of the energy conversion system which concerns on Embodiment 5 of this invention. It is a system block diagram of the energy conversion system which concerns on Embodiment 6 of this invention. It is an energy flow figure at the time of cooling in the energy conversion system concerning the embodiment. It is a system configuration | structure figure of the energy conversion system which concerns on Embodiment 7 of this invention. It is a system configuration | structure figure of the energy conversion system which concerns on Embodiment 8 of this invention. It is a system configuration | structure figure of the energy conversion system which concerns on Embodiment 9 of this invention. It is a system configuration | structure figure of the energy conversion system which concerns on Embodiment 10 of this invention. It is a system configuration figure of the energy conversion system concerning the embodiment. It is an energy flow figure at the time of heating in the energy conversion system concerning the embodiment. It is a system configuration | structure figure of the energy conversion system which concerns on Embodiment 11 of this invention. It is a system configuration | structure figure of the energy conversion system which concerns on a prior art example.

Explanation of symbols

1A, 1B, 1C, 1D, 1E, 1F, 1G, 1H, 1I, 1J, 1K Energy conversion system
11 Rankine cycle circuit
12 Stirling engine
13 Heater
14 Waste heat recovery unit
15 Expander
16 Heat exchanger
18d heating section
19,29 Output shaft
20,22 Generator (Rotating machine)
24 High temperature side cylinder (High temperature part)
25 Low temperature side cylinder (low temperature part)
34 Cooling medium storage tank
37a, 37b, 37c, 37d, 37e, 37f, 37g Cooling medium conduit
37h Waste heat recovery section
40,59 Rotation adjuster
42 Cooling medium conduit (first cooling medium flow path)
43 Cooling medium conduit (second cooling medium flow path)
44 Coolant flow control valve
46a, 46b, 46c Cooling medium conduit (external flow path)
48 Outflow control valve
50 Refrigeration and air conditioning cycle circuit
50a First circuit
50b Second circuit
51 Compressor
52 3rd heat exchanger
54 Indoor heat exchanger (second heat exchanger)
56a Cooling medium conduit (third cooling medium flow path)
56b Cooling medium conduit (fourth cooling medium flow path)
57 Coolant flow control valve (second coolant flow control valve)
58 Fourth heat exchanger
61 Four-way valve
62 Fifth heat exchanger
63a, 63b Working medium conducting tube (first working medium flow path)
64a, 64b Working medium conducting pipe (second working medium flow path)
65 Working medium flow control valve

Claims (18)

A Rankine cycle circuit having an expander that converts expansion energy of the working medium into kinetic energy, a high-temperature portion that heats and expands the working gas in the expansion chamber, and a low-temperature portion that cools and contracts the working gas are used to convert the heat energy into kinetic energy. In an energy conversion system with a Stirling engine for conversion,
An energy conversion system comprising: a heat exchanger that exchanges heat between a cooling medium that cools the low temperature portion of the Stirling engine and the working medium.   The heat exchanger is supplied with the working medium in which the expansion energy is converted into kinetic energy through the expander and the cooling medium before being supplied to the low temperature part of the Stirling engine. The energy conversion system according to claim 1, wherein   A heating unit that absorbs heat to give expansion energy to the working medium provided in the Rankine cycle circuit, and a heater that heats at least one of the high-temperature unit of the Stirling engine, and the heater And a waste heat recovery unit that passes the cooling medium through the exhaust heat recovery unit and exchanges heat between the cooling medium and the air inside the exhaust heat recovery unit. The energy conversion system according to claim 1 or 2, wherein   A rotating machine such as a generator and a motor is provided, and the rotating machine is connected to each of the output shaft of the Stirling engine and the output shaft of the expander of the Rankine cycle circuit, or only one of them. The energy conversion system according to any one of claims 1 to 3, wherein the kinetic energy is supplied and driven.   The energy conversion system according to any one of claims 1 to 4, wherein an output shaft of the Stirling engine and an output shaft of the expander are connected.   At the connecting portion between the output shaft of the Stirling engine and the output shaft of the expander, the output shaft is rotated at a predetermined rotation ratio by adjusting the rotational speed of the output shaft with a mechanism, fluid, or the like. The energy conversion system according to claim 5, further comprising a rotation adjusting unit to be operated.   The energy conversion system according to claim 6, wherein the rotation adjusting unit is formed by a transmission unit having a gear mechanism such as a planetary gear mechanism, a torque converter, a continuously variable transmission, or the like.   The energy conversion system according to any one of claims 1 to 7, further comprising a cooling medium storage tank that stores the cooling medium that has passed through the low temperature portion.   A cooling medium conducting pipe is provided for supplying the cooling medium stored in the cooling medium storage tank to the low temperature part and circulating the cooling medium between the cooling medium storage tank and the low temperature part. The energy conversion system according to claim 8. As the cooling medium flow path, a first cooling medium flow path for allowing the cooling medium flowing out from the cooling medium storage tank to flow into the heat exchanger, and the cooling medium flowing out from the cooling medium storage tank as the low temperature A second cooling medium flow path for flowing into the part,
The energy conversion according to claim 8 or 9, further comprising a cooling medium flow rate adjusting valve for adjusting a flow rate of the cooling medium with respect to the first cooling medium flow path and the second cooling medium flow path. system. The cooling medium stored in the cooling medium and the cooling medium storage layer, connected to at least one of the cooling medium conducting tube and the cooling medium storage tank through which the cooling medium that has passed through the low temperature portion is conducted. An external flow path for causing at least one of the flow out to the outside,
The energy conversion system according to any one of claims 8 to 10, further comprising an outflow amount adjustment valve that adjusts a flow rate of the cooling medium in the external flow path. A refrigeration air conditioning cycle circuit comprising a compressor for compressing the second working medium, and a second heat exchanger for exchanging heat between indoor air and the second working medium;
The energy conversion system according to any one of claims 1 to 11, wherein the compressor is connected to at least one of an output shaft of the Stirling engine and an output shaft of the expander.   The energy conversion system according to claim 12, further comprising a third heat exchanger that exchanges heat between the second working medium of the refrigeration air-conditioning cycle circuit and a cooling medium of the Stirling engine. The third heat exchanger and the heat exchanger for exchanging heat between the working medium of the Rankine cycle circuit and the cooling medium of the Stirling engine are provided, respectively.
As the cooling medium flow path, a third cooling medium flow path for allowing the cooling medium flowing out from the cooling medium storage tank to flow into the heat exchanger, and the cooling medium flowing out from the cooling medium storage tank as the first cooling medium. A fourth coolant flow path for flowing into the three heat exchangers,
The energy conversion system according to claim 13, further comprising a cooling medium flow rate adjustment valve that adjusts a flow rate of the cooling medium with respect to the third cooling medium flow path and the fourth cooling medium flow path.   The said refrigeration air-conditioning cycle circuit is provided with the 4th heat exchanger which forcibly heat-exchanges said 2nd working medium and outdoor air, The one of Claim 12 thru | or 14 characterized by the above-mentioned. Energy conversion system. The compressor and the rotating machine are connected to at least one of the output shaft of the Stirling engine and the output shaft of the expander,
One or both of the compressor and the rotating machine having a driving force output from at least one of the Stirling engine and the expander is connected to the output shaft, the compressor, and the rotating machine. The energy conversion system according to any one of claims 12 to 15, further comprising a rotation adjustment unit that adjusts a transmission state with respect to the energy.   In the refrigeration air-conditioning cycle circuit, the flow path of the second working medium is switched, and the first circulation path for using the second heat exchanger as an evaporator and the second heat exchanger as a condenser are used. The energy conversion system according to any one of claims 12 to 16, further comprising a four-way valve forming any one of the second circulation paths. A fifth heat exchanger for cooling the working medium by forcibly exchanging heat between the working medium of the Rankine cycle circuit and ambient air;
As the working medium flow path, a first working medium flow path for allowing the working medium flowing out from the expander to pass through the heat exchanger, and the working medium flowing out from the expander as the fifth heat exchanger. A second working medium flow path that is passed through,
18. A working medium flow rate adjusting valve for adjusting a flow rate of the working medium with respect to the first working medium flow path and the second working medium flow path is provided. Energy conversion system as described in.

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