JP2009144598A - External combustion engine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compact, high-power, failure-proof external combustion engine capable of achieving high energy exchanging efficiency. <P>SOLUTION: The external combustion engine 1A includes a Rankine cycle circuit 11 and a Stirling engine 12, and heats working medium of the Rankine cycle circuit 11 and a high-temperature side piston of the Stirling engine 12 by a heater 13. An integrally-formed housing 21 of the Stirling engine 12 is provided with a crank chamber 22, a generator chamber 23 and an expander receiving chamber 24. An output shaft 43 housed in the crank chamber 22, an output shaft 46 of an expander 15 housed in the expander receiving chamber 24 and an input shaft 45 of a generator 44 housed in the generator chamber 23 are connected to each other. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to an external combustion engine 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 and effective use of energy have become important issues. Conventionally, an external combustion engine in which a Stirling engine and another energy conversion engine are combined has been proposed.

  For example, Patent Document 1 describes an external combustion engine (composite refrigeration generator) 300 that generates electricity by combining a Rankine cycle circuit 210 and a Stirling engine 200 as shown in a schematic diagram of FIG.

  The external combustion engine 300 includes an expander (expansion turbine) 212 driven by a working medium evaporated by an evaporator (evaporator) 211 in the Rankine cycle circuit 210 and a condenser (condenser) for condensing the expanded working medium. 213, and a generator (generator) 214 that generates power by driving the expander 212 is attached to the expander 212.

  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 and contracts. It is driven by repeating. A generator (generator) 201 is also attached to the Stirling engine 200. The working medium of the Rankine cycle circuit 210 is condensed by the heat exchange with the liquefied natural gas as the second cooling medium in the condenser 213, and the cooling medium (cooling heat medium) of the Stirling engine 200 is vaporized with the Stirling engine 200. It circulates between it and the evaporator 203, and heat-exchanges with a 2nd cooling medium in the vaporizer 203, and is cooled.

On the other hand, in Patent Document 2, as shown in the schematic diagram of FIG. 19, the compressor 403 of the refrigeration air-conditioning cycle circuit 402 is connected to the output shaft 401 of the Stirling engine 400, and the compressor 403 is driven by driving the Stirling engine 400. A combustion engine (air conditioning / hot water supply system) 500 is described. In the external combustion engine 500, the refrigerating and air-conditioning cycle circuit 402 is provided with an expansion valve 404, an indoor heat exchanger 405, and an outdoor heat exchanger 406, which are connected by a second working medium conduction pipe to perform a second operation. A medium circulation path is formed, and the cooling medium conduction pipe (water supply path) 407 branches in the middle, and one side of the branch is supplied to the low temperature part (cooling part) 408 of the Stirling engine 400 to supply the cooling medium. The other side branched is allowed to pass a cooling medium around a high temperature part (heating part) 409 to generate hot water.
JP 2006-329059 A JP 58-12966 A

  However, the invention described in Patent Document 1 has a problem that the Rankine cycle circuit and the Stirling engine are formed as separate devices, which inevitably increases the size of the device. In addition, although the invention described in the cited document 2 can be used as an air conditioner, in order to drive the air conditioner with high output, the output of the Stirling engine must be increased, and in order to improve performance, the apparatus is still used. There is a problem of increasing the size. Further, the invention described in the cited document 2 has a problem that when the Stirling engine is stopped, the entire system is stopped and is vulnerable to failure.

  The present invention has been made in view of the above problems, and an object of the present invention is to provide an external combustion engine that is small and has high output, is resistant to obstacles, and can obtain 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, and the working gas. A Stirling engine that includes a low-temperature part that cools and contracts the heat, converts thermal energy into kinetic energy, a heating part that is provided in the Rankine cycle circuit and heats the working medium, and at least one of the high-temperature part of the Stirling engine An external combustion engine comprising a heater for heating and at least one of a rotary machine such as a generator and a compressor for compressing a second working medium circulating in a refrigeration air-conditioning cycle circuit, the output shaft of the Stirling engine And less than the output shaft of the expander, the rotating machine and the compressor Characterized in that it is connected and the one of the input shaft.

  In addition to the structure of Claim 1, the invention described in Claim 2 includes an output shaft of the Stirling engine, the expander constituting the Rankine cycle circuit, in an integrally formed main body, and At least one of the rotating machine and the compressor is accommodated, respectively.

  The invention according to claim 3 is provided with an exhaust heat recovery device that passes the heat output from the heater in addition to the configuration according to claim 1 or 2, and the output of the exhaust heat recovery device is output. On the exhaust side through which heat passes, a first liquid medium jacket as the heating unit through which the working medium supplied to the expander passes is disposed, and the low temperature unit has passed through the expander A second liquid medium jacket through which the working medium passes is provided.

  According to a fourth aspect of the present invention, in addition to the configuration of the second or third aspect, the main body portion includes a first chamber in which an output shaft of the Stirling engine is accommodated, the rotating machine, and the compressor. At least one of them and the expander for expanding the working medium circulating in the Rankine cycle circuit are accommodated, and a second chamber through which the working medium expanded by the expander passes is provided. It is characterized by that.

  According to a fifth aspect of the present invention, in addition to the configuration according to the second or third aspect, in the main body portion, the main body portion circulates the output shaft of the Stirling engine and the Rankine cycle circuit. The expander that expands the medium and at least one of the rotating machine and the compressor are housed in the same chamber, and the working medium expanded by the expander passes through the inside. A chamber is provided.

  According to a sixth aspect of the present invention, in addition to the configuration according to any one of the second to fifth aspects, the main body portion compresses the second working medium circulating in the refrigeration air-conditioning cycle circuit. A fourth chamber is provided in which is accommodated.

  According to a seventh aspect of the invention, in addition to the configuration of the second or third aspect, the main body compresses the second working medium that circulates through the output shaft of the Stirling engine and the refrigeration air conditioning cycle circuit. A fifth chamber in which the compressor is accommodated and a sixth chamber in which the expander for expanding the working medium circulating in the Rankine cycle circuit is accommodated are provided.

  The invention described in claim 8 is characterized in that, in addition to the structure described in claim 7, the working gas of the second working medium and the Stirling engine circulating in the refrigeration air-conditioning cycle circuit is carbon dioxide.

  According to a ninth aspect of the present invention, in addition to the configuration according to any one of the sixth to eighth aspects, a third liquid medium jacket through which the second working medium supplied to the compressor passes through the low temperature portion. And a fourth liquid medium jacket through which the second working medium that has passed through the compressor passes is provided on the intake side of the exhaust heat recovery unit for supplying air to the heater. .

  According to a tenth aspect of the present invention, in addition to the configuration according to any one of the sixth to ninth aspects, the compressor that compresses the second working medium that circulates the power of the Stirling engine through the refrigeration air-conditioning cycle circuit. The power transmission mechanism for transmitting to the input shaft has a connecting portion that moves forward and backward integrally with the piston that forms the expansion chamber of the Stirling engine, and an axial direction with respect to the forward and backward direction of the piston. The rotation main shaft provided in parallel and the rotation main shaft is connected to the center portion and the connecting portion is connected to the peripheral side, the plate surface direction is inclined with respect to the axial direction of the rotation main shaft. A swash plate provided to convert the movement of the piston in the advancing and retreating direction into the rotation of the rotation main shaft; and the input shaft and the rotation main shaft connected to the rotation main shaft in the axial direction. Characterized by comprising a rotation conversion unit for transmitting to convert the axially rotational movement.

  According to an eleventh aspect of the present invention, in addition to the configuration according to any one of the sixth to tenth aspects, the expander that expands the working medium that circulates through the Rankine cycle circuit and the refrigeration air-conditioning cycle circuit are circulated. At least one of the compressors that compress the second working medium is a scroll type.

  According to a twelfth aspect of the present invention, in addition to the configuration according to any one of the sixth to eleventh aspects, the compressor for compressing the second working medium circulating in the refrigeration air-conditioning cycle circuit includes a cylinder, a piston, A reciprocating compressor comprising: a second rotary main shaft driven by a driving force of at least one of the expander and the Stirling engine for expanding the working medium circulating in the Rankine cycle circuit; and a center A second swash plate that is connected to the second rotation main shaft and is inclined with respect to the axial direction of the second rotation main shaft, and the piston of the compressor includes the second swash plate The present invention is characterized in that a connecting portion for connecting to the swash plate is provided.

  According to a thirteenth aspect of the present invention, in addition to the configuration according to any one of the first to twelfth aspects, the piston is formed so that the advancing / retreating direction of the piston forming the expansion chamber of the Stirling engine is substantially horizontal. It is characterized by that.

  According to a fourteenth aspect of the present invention, in addition to the configuration according to any one of the second to thirteenth aspects, in the main body portion, any one of the second rotation main shaft and the output shaft is in the axial direction. The Stirling engine is arranged in a direction substantially orthogonal to the advancing / retreating direction of the piston, and the other is arranged in a substantially horizontal direction with respect to the advancing / retreating direction of the piston of the Stirling engine.

  According to a fifteenth aspect of the present invention, in addition to the configuration according to the thirteenth or fourteenth aspect, the heater is installed above the high-temperature portion, and the exhaust heat recovery unit is disposed on the exhaust side from the heater. It is characterized by extending downward toward the high temperature part.

  The invention according to claim 16 is the configuration according to claim 13 or 14, wherein the heater is installed to face the top of the high temperature portion, and the exhaust heat recovery device is disposed on the exhaust side. It has a horizontal part provided in the substantially horizontal direction from the said heater to the said high temperature part, and the upward extension part extended toward upper direction from a part of this horizontal part, It is characterized by the above-mentioned.

  According to a seventeenth aspect of the present invention, in addition to the configuration of the sixteenth aspect, the horizontal portion of the exhaust heat recovery device is bent at a substantially right angle at the position of the high temperature portion, and the upward extending portion is the horizontal portion. It is characterized by extending in a substantially vertical direction upward from the position of the high temperature portion where the portion is bent.

  According to the first aspect of the present invention, the heater includes a heating unit that is provided in the Rankine cycle circuit and that heats the working medium and that heats at least one of the high-temperature unit of the Stirling engine. The heat energy output from the heater can be used for heating the Rankine cycle circuit and the Stirling engine, and the energy conversion efficiency can be increased. In addition, since the output shaft of the Stirling engine, the output shaft of the expander, and the input shaft of at least one of the rotating machine and the compressor are connected, the driving force and expansion of the Stirling engine can be used as one input shaft. It can be operated by a combined force with the driving force of the machine, and a high output can be obtained. In addition, since driving of one output shaft can be continued by driving either one of the Stirling engine and the expander, the degenerate operation and the like are facilitated and are resistant to obstacles. As a result, it is possible to provide an external combustion engine that is small in size, can provide high output, is resistant to obstacles, and has high energy conversion efficiency.

  According to the second aspect of the present invention, the output shaft of the Stirling engine, the expander constituting the Rankine cycle circuit, and at least one of the rotating machine and the compressor are provided inside the integrally formed main body. Can be accommodated in the body portion integrally formed with the part where the driving force of the Stirling engine and Rankine cycle circuit is generated and the part rotated by the driving force. Thereby, the main part of an external combustion engine can be formed compactly, and the further size reduction of the whole apparatus can be achieved.

  According to the third aspect of the present invention, it is possible to collect and use the heat output from the heater in a concentrated manner by providing the exhaust heat recovery device that passes the heat output from the heater. become. In addition, on the exhaust side through which the heat output from the exhaust heat recovery unit passes, a working medium supplied to the expander passes, and a first liquid medium jacket as a heating unit is disposed, so that the working medium Thus, the heat generated by the heater can be absorbed to perform the isobaric heating process of the Rankine cycle circuit reliably. In addition, since the second fluid medium jacket through which the working medium that has passed through the expander passes is disposed in the low temperature portion, the working gas of the Stirling engine is changed to the working medium whose temperature has been lowered through the expansion process of the Rankine cycle circuit. Thus, the efficiency of the process of cooling and shrinking the working gas in the low temperature part can be improved. Thereby, an external combustion engine can be formed more compactly and energy conversion efficiency can be raised further.

  According to the fourth aspect of the present invention, the first chamber in which the output shaft of the Stirling engine is accommodated, the expander for expanding the working medium circulating in the Rankine cycle circuit, and at least one of the rotating machine and the compressor. And the second chamber through which the working medium expanded by the expander passes, the cooling mechanism for the rotating machine is controlled by the passage of the working medium whose temperature has decreased through the expansion stroke. At least one of the rotating machine and the compressor can be cooled without any special provision. Thereby, an external combustion engine can be formed more compactly and the fall of durability and reliability by the heating of a rotary machine can be prevented.

  According to invention of Claim 5, in a main-body part, the output shaft of a Stirling engine, the expander which expands the said working medium which circulates through a Rankine cycle circuit, and at least any one among a rotary machine and a compressor, Are housed in the same chamber, and the third chamber through which the working medium expanded by the expander passes is provided, so that the rotating machine is moved by the passage of the working medium whose temperature has decreased through the expansion stroke. Therefore, at least one of the rotating machine and the compressor can be cooled without any special cooling mechanism, and the external combustion engine can be formed more compactly to prevent the durability and reliability from being lowered due to the heating of the rotating machine.

  According to the invention described in claim 5, when the working medium is passed from the expander into the third chamber, the lubricating oil existing in the third chamber is agitated, or the working medium itself is the lubricating oil. When has a function, the function of the lubricating oil can be achieved only by passing the working medium through the third chamber. As a result, there is no need to provide a mechanism for stirring the lubricating oil stored in the oil pan, and no need to store the lubricating oil in the oil pan, and the external combustion engine can be made more compact. Further, since only one type of lubricating oil is used in the third chamber, maintenance can be performed easily.

  According to the sixth aspect of the present invention, in the main body, the Stirling engine and Rankine cycle are provided by providing the fourth chamber in which the compressor for compressing the second working medium circulating in the refrigeration air conditioning cycle circuit is provided. A portion where the driving force of the circuit is generated and a portion of the refrigeration / air-conditioning cycle circuit that needs to be supplied with the driving force can be accommodated in the integrally formed body. Thereby, the main part of the external combustion engine used in combination with power generation and the air conditioning can be formed compactly, and further downsizing of the entire apparatus can be achieved.

  According to the invention described in claim 7, in the main body portion, the fifth chamber in which the compressor for compressing the second working medium circulating in the output shaft of the Stirling engine and the refrigeration air-conditioning cycle circuit is housed, and the Rankine cycle circuit are provided. By providing the sixth chamber in which the expander that expands the circulating working medium is accommodated, the structure of the external combustion engine can be simply formed, and the main part of the external combustion engine can be compactly formed. In addition, since the output shaft of the Stirling engine and the compressor of the refrigeration air conditioning cycle circuit are housed in the same chamber, the fifth chamber filled with the second working medium of the refrigeration air conditioning cycle circuit is expanded with the working gas of the Stirling engine filled. It will be adjacent or close to the chamber. Therefore, even if the working gas of the Stirling engine and the second working medium of the refrigeration air-conditioning cycle circuit are shared, there is no trouble due to gas leakage between the fifth chamber and the expansion chamber, and maintenance is facilitated. Can do.

  According to the eighth aspect of the present invention, the working gas of the Stirling engine and the second working medium of the refrigeration air-conditioning cycle circuit are obtained by the second working medium circulating in the refrigeration air-conditioning cycle circuit and the working gas of the Stirling engine being carbon dioxide. Can be shared.

  According to the ninth aspect of the present invention, the low temperature part is provided with a third fluid medium jacket through which the second working medium supplied to the compressor passes, so that the low temperature before passing through the compression step in the compressor of the refrigeration air conditioning cycle circuit. The efficiency of the process of cooling and shrinking the working gas in the low temperature portion can be improved by exchanging heat between the second working medium and the working gas filled in the low temperature portion. Thereby, an external combustion engine can be formed more compactly and energy conversion efficiency can be raised further. In addition, a fourth fluid medium jacket through which the second working medium that has passed through the compressor passes is provided on the intake side that supplies air to the heater of the exhaust heat recovery unit, so that the high-temperature second through the compression process by the compressor. Heat exchange is performed between the two working medium and air before being supplied to the heater, and the air heated by this heat exchange is supplied to the heater to improve the heating efficiency. In order to cool the working medium), the efficiency of the refrigeration cycle is also improved. Thereby, the efficiency of a heater can be improved and the output and energy conversion efficiency of an external combustion engine can be improved.

  According to the tenth aspect of the present invention, the connecting portion that advances and retreats integrally with the piston in the advancing and retreating direction of the piston forming the expansion chamber of the Stirling engine, and the axial direction is provided in parallel to the advancing and retreating direction of the piston. The rotation main shaft is rotatable, the rotation main shaft is connected to the central portion, and the connecting portion is connected to the peripheral side. The plate surface direction is inclined with respect to the axial direction of the rotation main shaft, and the piston advances and retracts. A swash plate that converts the motion of the rotation main shaft into a rotation motion of the rotation main shaft, and a rotation conversion unit that is connected to the input shaft and the rotation main shaft and converts the axial rotation motion of the rotation main shaft to the axial rotation motion of the input shaft and transmits it. By providing, the length of the piston in the Stirling engine can be shortened, and the main part of the external combustion engine can be compactly formed. Further, the operation of the power transmission mechanism can be stabilized. Further, by adjusting the inclination angle of the swash plate, it is possible to easily change the stroke amount of the piston and adjust the driving state of the piston.

  According to the invention described in claim 11, at least one of the expander that expands the working medium circulating in the Rankine cycle circuit and the compressor that compresses the second working medium circulating in the refrigeration air-conditioning cycle circuit is a scroll type. As a result, the movable scroll can be swung and expanded or compressed, so there is no need to provide a mechanism for changing the direction of motion of the rotational energy transmitted from the output shaft, and therefore mechanical loss of energy is reduced. The energy efficiency in compression and expansion can be improved.

  According to the invention described in claim 12, the compressor for compressing the second working medium circulating in the refrigeration air-conditioning cycle circuit is a reciprocating compressor including a cylinder and a piston, and the working medium circulating in the Rankine cycle circuit A second rotating main shaft driven by a driving force of at least one of an expander and a Stirling engine that expands the plate, and a central portion connected to the second rotating main shaft so that the plate surface is in the axial direction of the second rotating main shaft. A second swash plate provided with a slanted direction, and a connecting portion connected to the second swash plate is provided on the piston of the compressor, thereby shortening the axial length of the second rotation main shaft. The main part of the external combustion engine can be formed compactly. Further, the operation of the compressor can be stabilized, and the compression state can be easily adjusted by easily changing the stroke amount of the piston by adjusting the inclination angle of the swash plate.

  According to the thirteenth aspect of the present invention, it is possible to increase the size of the expansion chamber in the height direction by forming the piston that forms the expansion chamber of the Stirling engine so that the advancing and retreating direction is substantially along the horizontal direction. Can be suppressed. Thereby, it becomes possible to install an external combustion engine in a space with a small size in the height direction.

  According to the fourteenth aspect of the present invention, in the main body portion, any one of the second rotation main shaft and the output shaft is disposed so that the axial direction is substantially orthogonal to the advancing / retreating direction of the piston of the Stirling engine. The other is arranged in a substantially horizontal direction with respect to the advancing and retreating direction of the piston of the Stirling engine, so that it is possible to prevent the main body from becoming large only in the horizontal direction. Thereby, an external combustion engine can be installed in a narrow space such as a corner of a room.

  According to the fifteenth aspect of the present invention, the heater is installed above the high temperature portion, and the exhaust heat recovery device extends downward from the heater to the high temperature portion, so that the heater The dust, oxides, etc. generated by the combustion, which is the heating means, fall along the direction of heat release and are accumulated below the exhaust heat recovery unit. Thereby, the heat conduction state inside the exhaust heat recovery device can be kept good, and the decrease in energy conversion efficiency and the use lifetime of the exhaust heat recovery device due to continuous use can be suppressed.

  According to invention of Claim 16, a heater is installed facing the top part of a high temperature part, and a waste heat recovery device is the horizontal provided in the horizontal direction from the heater to the high temperature part on the exhaust side. Part and an upwardly extending part extending upward from a part of the horizontal part, so that dust, oxides, etc. generated by combustion as heating means of the heater can be removed from the exhaust heat recovery unit. It is accumulated below the horizontal part. Thereby, the heat conduction state inside the exhaust heat recovery device can be kept good, and the decrease in energy conversion efficiency and the use lifetime of the exhaust heat recovery device due to continuous use can be suppressed. In addition, the exhaust heat that has not been used for heating the high temperature portion is released upward along the upward extending portion of the exhaust heat recovery device. That is, since the exhaust heat recovery device is arranged substantially in line with the direction of movement of the heat released from the heater, the heat conduction state inside the exhaust heat recovery device is kept good, and the exhaust heat recovery is performed. The situation where the inside of a vessel is damaged by heat can be suppressed, and the decrease in the service life of the exhaust heat recovery device can be suppressed.

  According to the seventeenth aspect of the present invention, the horizontal portion of the exhaust heat recovery device is bent at a substantially right angle at the position of the high temperature portion, and the upward extending portion is directed upward from the position of the high temperature portion where the horizontal portion is bent. Thus, the heat used for heating the high temperature part can be released upward as it is. As a result, the exhaust heat after heating is efficiently discharged to the outside of the exhaust heat recovery device while adjusting the heater to a state suitable for heating the high temperature part, and the heat conduction state inside the exhaust heat recovery device is further improved. And a decrease in the service life of the exhaust heat recovery device can be further suppressed.

Embodiments of the present invention will be described below.
Embodiment 1 of the Invention
1 to 6 show an embodiment of the present invention.

  The external combustion engine of this embodiment is used for a home cogeneration system. First, the configuration will be described. As shown in FIG. 1, the external combustion engine 1A according to this embodiment includes a Rankine cycle circuit 11 having an output of about several hundred W (more specifically, about 300 W to 700 W), and several kW. A Stirling engine 12, a heater 13 and an exhaust heat recovery device 14 having a power of about (more specifically, about 1 kW to 3 kW) are provided.

  As shown in FIG. 4, the Rankine cycle circuit 11 includes an expander 15, a heat exchanger 16, a pump 17, and a first liquid medium jacket 18 as a “heating unit”, and further a second liquid medium jacket 19. It has. The expander 15, the second liquid medium jacket 19, the heat exchanger 16, the pump 17, and the first liquid medium jacket 18 are respectively connected by working medium conducting tubes 20a, 20b, 20c, 20d, and 20e that are working medium conducting paths. Thus, a circulation path for the working medium is formed, and the working medium circulates in this circulation path by the operation of the pump 17.

  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 as shown in FIG. 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 (right side in FIG. 1) sucks air and the other side (left side in FIG. 1) discharges air. It is formed on the exhaust side. As shown in FIG. 1, 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, which is composed of a pair of spiral-shaped fixed scroll 15a and movable scroll 15b, and has a volume of a space partitioned by the two scrolls 15a and 15b by the pressure of the flowing working medium. Changes to expand the working medium and convert the expansion energy of the working medium into rotational kinetic energy.

  The heat exchanger 16 includes a fan, and performs heat exchange between the passing working medium and ambient air. The 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.

  The first fluid medium jacket 18 is disposed on the outer wall surface around the exhaust heat side of the exhaust heat recovery device 14. The second fluid medium jacket 19 is disposed on the outer wall surface of a low temperature side cylinder (described later) of the Stirling engine 12.

  On the other hand, the Stirling engine 12 is a two-piston type Stirling engine as shown in FIG. 1, and includes a housing 21 as a “main part” integrally formed by casting or the like, a high temperature side cylinder 27 communicated by a communication pipe 35 and a low temperature. And a side cylinder 28.

  The housing 21 is provided with a crank chamber 22 and a generator chamber 23 in communication with each other on the one side (the right side in FIG. 1), and is separated by a partition wall 25 on the other side (the left side in FIG. 1) to expand inside. An expander housing chamber 24 in which the machine 15 is housed is provided.

  An oil pan 26 formed in a dish shape is provided on the lower side of the crank chamber 22. Lubricating oil for smooth rotation of a crankshaft (described later) is stored in the oil pan 26.

  Above the crank chamber 22, a high temperature side cylinder 27 as a “high temperature part” and a low temperature side cylinder 28 as a “low temperature part” are provided. The high temperature side cylinder 27 and the low temperature side cylinder 28 are substantially cylindrical, and are formed vertically so that the axial direction of the substantially cylindrical shape of each of the cylinders 27 and 28 is substantially vertical. Partition portions 31 and 32 are respectively provided between the high temperature side cylinder 27 and the crank chamber 22 and between the low temperature side cylinder 28 and the crank chamber 22, and the high temperature side cylinder 27 and the crank chamber 22, and the low temperature side cylinder 28, respectively. The crank chamber 22 is formed in a semi-airtight state.

  A high temperature side piston 29 is provided inside the high temperature side cylinder 27, and a low temperature side piston 30 is provided inside the low temperature side cylinder 28, and is formed between the inside of the high temperature side cylinder 27 and the high temperature side piston 29. The space is formed in the expansion chamber 33, and the space formed between the low temperature side cylinder 28 and the low temperature side piston 30 is formed in the contraction chamber 34. The expansion chamber 33 and the contraction chamber 34 are communicated with each other by a communication pipe 35. A working gas is sealed in the expansion chamber 33 and the contraction chamber 34. The working gas moves through the expansion chamber 33 and the contraction chamber 34 through the communication pipe 35, is heated and expanded in the expansion chamber 33, and is cooled and contracted in the contraction chamber 34. As the working gas, non-condensable gas such as helium, hydrogen, carbon dioxide, nitrogen and air is used. The crank chamber 22 and the generator chamber 23 are filled with the same gas as the working gas. Even if gas leaks from the crank chamber 22 into the high temperature side cylinder 27 or the low temperature side cylinder 28, the function of the Stirling engine 12 is achieved. Is configured not to decrease.

  The high temperature side piston 29 and the low temperature side piston 30 pass through openings 36 and 37 formed in the partition walls 31 and 32, and are connected to one output shaft 43 provided in the crank chamber 22. Ring-shaped seal members 38 and 39 are fitted in the openings 36 and 37. The seal members 38 and 39 are formed of members that can ensure semi-airtightness between the high temperature side piston 29 and the crank chamber 22 and between the low temperature side piston 30 and the crank chamber 22.

  The output shaft 43 is a crankshaft and is formed as an “output transmission mechanism” that converts the vertical motion of each piston 29, 30 into a rotational motion. Specifically, the first crank portion 43a to which the connecting rod 40 of the high temperature side piston 29 is connected and the second crank portion 43b to which the connecting rod 41 of the low temperature side piston 30 are connected each have a predetermined angle (for example, about 90 degrees). ) With a phase difference of. Although not shown, a starter motor for starting the Stirling engine 12 is connected to the output shaft 43.

  It is desirable that the heights of the first crank portion 43a and the second crank portion 43b are formed such that the lubricating oil stored in the oil pan 26 can be stirred when the output shaft 43 rotates.

  One end side of the output shaft 43 is connected to an input shaft 45 of a generator 44 as a “rotating machine” disposed inside the generator chamber 23, and the other end side is connected to an output shaft 46 of the expander 15. ing. Further, one end side of the output shaft 43 is on the partition wall portion 25, the substantially central portion is on the support column portion 47 protruding substantially at the boundary position between the crank chamber 22 and the generator chamber 23, and the other end side is the other side wall surface of the housing 21. Is pivotally supported by the shaft. The generator 44 receives power from the expander 15 of the Rankine cycle circuit 11 and the Stirling engine 12 to generate electric power, but also functions as a starter motor when starting the Stirling engine 12. However, a configuration may be adopted in which a starter motor is provided separately from the generator 44 and the generator 44 only performs power generation.

  A rotation adjusting section 48 that mechanically adjusts the rotational speed of each of the output shafts 43 and 46 is provided at a connection portion between the output shaft 43 of the Stirling engine 12 and the output shaft 46 of the expander 15. The rotation adjusting portion 48 is formed by a speed change mechanism such as a planetary gear mechanism, and is provided in the partition wall portion 25. The rotation adjusting unit 48 may be formed by a gear mechanism other than the planetary gear mechanism, a torque converter, a continuously variable transmission, or the like, or a part or all of the gear mechanism, torque converter, continuously variable transmission, etc. You may form combining.

  The high temperature side cylinder 27 is accommodated on the exhaust side of the heater 13 inside the exhaust heat recovery device 14 and is heated by the heat released from the heater 13. As described above, the second fluid medium jacket 19 is disposed on the outer wall surface of the low temperature side cylinder 28.

  Next, the operation of this embodiment will be described.

  In the Stirling engine 12, when the high temperature side cylinder 27 is heated by the heat released from the heater 13, the working gas in the expansion chamber 33 is heated and expanded, and is sent to the contraction chamber 34 through the communication pipe 35. In the contraction chamber 34, heat exchange between the working gas and the working medium in the second liquid medium jacket 19 is performed through the wall surface of the low temperature side cylinder 28, the working gas is cooled and contracted, and is expanded through the communication pipe 35. The same process is repeated thereafter. The expansion and contraction of the working gas generates kinetic energy that moves the high temperature side piston 29 and the low temperature side piston 30 in the vertical direction. When the connecting rods 40 and 41 move up and down by this kinetic energy, the first crank portion 43a and the second The output shaft 43 rotates by converting the energy of this vertical movement into rotational motion in cooperation with the two crank portions 43b.

  On the other hand, when the pump 17 operates in the Rankine cycle circuit 11, the working medium circulates in the circulation path. The working medium pressurized and compressed by the pump 17 is supplied to the first liquid medium jacket 18 through the working medium conducting pipe 20d. In the first liquid medium jacket 18, the working medium is heated by exchanging heat with the waste heat passing through the exhaust heat recovery device 14, heated, and supplied to the expander 15 through the working medium conducting pipe 20 e. In the expander 15, the volume of the space partitioned by the fixed scroll 15a and the movable scroll 15b varies depending on the pressure of the supplied working medium. As a result, the working medium expands, and the movable scroll 15b rotates by the expansion of the working medium to rotate the output shaft 46.

  When both the output shafts 43 and 46 are rotated by the operations of the Rankine cycle circuit 11 and the Stirling engine 12, the input shaft 45 connected to the output shaft 43 is rotated by the resultant force of the rotational kinetic energy of both the output shafts 43 and 46. The generator 44 is driven to generate power.

  The working medium expanded by the expander 15 is sent to the second liquid medium jacket 19 through the working medium conducting pipe 20a, and is heated again by exchanging heat with the working gas through the wall surface of the low temperature side cylinder 28. Note that the temperature of the working gas inside the contraction chamber 34 is generally lower than the air inside the exhaust heat recovery unit 14 where the working medium exchanges heat in the first liquid medium jacket 18, so heat exchange in the second liquid medium jacket 19 is performed. However, the efficiency of the Rankine cycle circuit is not significantly reduced.

  The working medium heated again is supplied to the heat exchanger 16 through the working medium conducting pipe 20b and cooled, supplied to the pump 17 through the working medium conducting pipe 20c, and pressurized / compressed again. Is repeated.

  The rotation of the output shaft 46 is transmitted to the output shaft 43 through the rotation adjusting unit 48, and the rotation adjusting unit 48 adjusts the difference in the rotational speed between the output shafts 46 and 43. As a result, even if the rotational speeds of the output shafts 43 and 46 are different due to a difference in driving state between the Stirling engine 12 and the Rankine cycle circuit 11, the rotational speed difference can be adjusted by the rotation adjusting unit 48. Can prevent the transmission loss of energy.

  In this embodiment, the first fluid medium jacket 18 provided in the Rankine cycle circuit 11 for heating the Rankine cycle working medium and the heater 13 for heating the high temperature side cylinder 27 of the Stirling engine are provided. The thermal energy output from the heater 13 can be used for heating the Rankine cycle circuit 11 and the Stirling engine 12, and the energy conversion efficiency can be increased. Further, the output shaft 43 of the Stirling engine 12, the output shaft 46 of the expander 15 of the Rankine cycle circuit 11, and the input shaft 45 of the generator 44 are connected, whereby the input shaft 45 of the generator 44 is connected to the Stirling engine 12. Can be operated by a combined force of the driving force of and the driving force of the expander 15, and a high output can be obtained. In addition, since the drive of the input shaft 45 of the generator 44 can be continued by driving one of the Stirling engine 12 and the expander 15, the degenerate operation and the like are facilitated and are resistant to obstacles.

  In this embodiment, the output shaft 43 of the Stirling engine 12, the expander 15, and the generator 44 are housed in the integrally formed housing 21, whereby the Stirling engine 12 and Rankine cycle circuit are accommodated. The portion where the driving force 11 is generated and the portion rotated by the driving force can be accommodated in the integrally formed housing 21. Thereby, the main part of external combustion engine 1A can be formed compactly.

  In this embodiment, the exhaust heat recovery device 14 that allows the heat output from the heater 13 to pass therethrough is provided, so that the heat output from the heater 13 can be intensively recovered and used. Become. In addition, the first fluid medium jacket 18 through which the working medium supplied to the expander 15 passes is disposed on the exhaust side of the exhaust heat recovery unit 14 through which the heat output from the heater 13 passes. The heat generated by the heater 13 is absorbed by the working medium, and the isobaric heating process of the Rankine cycle circuit can be performed reliably. Further, around the low temperature side cylinder 28, the second fluid medium jacket 19 through which the working medium that has passed through the expander 15 is disposed, so that the operation of the temperature lowered through the expansion stroke of the Rankine cycle circuit 11. It is possible to improve the efficiency of the process of causing the medium to absorb the heat of the working gas of the Stirling engine 12 and cooling and shrinking the working gas in the low temperature side cylinder 28.

  In this embodiment, since the expander 15 is a scroll type, the working medium can be expanded by turning the movable scroll 15b, so that the direction of motion of the rotational energy transmitted from the output shafts 43 and 46 is converted. Therefore, it is not necessary to provide a mechanism for reducing the mechanical loss of energy, and the energy efficiency in the expansion stroke of the working medium can be improved.

  Note that the external combustion engine 1A of this embodiment can also be realized in a manner as shown in FIG. 2 or FIG.

An external combustion engine 1A ₂ shown in FIG. 2 includes a one-cylinder Stirling engine 12. In this Stirling engine 12, a first piston 51 is installed on one connecting rod 50 on the upper side and a second piston 52 is installed on the lower side with a space therebetween, and both pistons 51, 52 are installed inside one cylinder 53. Yes. In the cylinder 53, an upper side of the first piston 51 is formed as an expansion chamber 33, and a space between the first piston 51 and the second piston 52 is formed as a contraction chamber 34. A second fluid medium jacket 54 is provided surrounding the periphery of the cylinder 53 on the contraction chamber 34 side. Other configurations are the same as those of the external combustion engine 1A of FIG. In the external combustion engine 1A ₂ of this embodiment, the second fluid medium jacket 54 is provided so as to surround the periphery of the cylinder 53 on the contraction chamber 34 side, so that the contraction efficiency of the working gas in the contraction chamber 34 is good. Thus, the efficiency of the Stirling engine 12 can be increased.

The external combustion engine 1A ₃ in FIG. ₃ is provided with a two-piston type Stirling engine 12 in the same manner as the external combustion engine 1A in FIG. 1, but the Stirling engine 12 has a high temperature side cylinder 55 and a low temperature side cylinder 56 spaced apart. A second fluid medium jacket 57 is provided so as to surround the periphery of the low temperature side cylinder 56. Other configurations are the same as those of the external combustion engine 1A of FIG. Also in an external combustion engine 1A ₃ of this embodiment, since the second liquid medium jacket 57 surrounds the periphery of the low-temperature side cylinder 56 is provided, shrinkage efficiency of the working gas in the contraction chamber 34 are improved, The efficiency of the Stirling engine 12 can be increased.

As described above, the external combustion engines 1A to 1A ₃ of this embodiment are used in a household cogeneration system (Note that the external combustion engines of Embodiments 2 and 3 described later are also used in the same cogeneration system. Stuff.)

FIG. 4 is a diagram showing an example of a system configuration of a cogeneration system to which the external combustion engine 1A (or the external combustion engines 1A ₂ and 1A ₃ ) of this embodiment is applied. This cogeneration system 10A is provided with a cooling medium storage tank 58 which is a water storage tank for supplying a cooling medium (water here) to a low temperature side cylinder (not shown in FIG. 4) of the Stirling engine 12, and this cooling medium storage tank A cooling medium circulation circuit 60 for circulating the cooling medium is formed between 58 and a cooling medium water jacket 59 provided on the outer wall surface of the low temperature side cylinder. The cooling medium circulation circuit 60 includes a second pump 61 that sends the cooling medium supplied from the cooling medium storage tank 58 to the heat exchanger 62, and heat exchange provided in place of the heat exchanger 16 shown in FIGS. A water heater 59 for cooling medium, and an exhaust heat recovery unit 63e. The second pump 61, the heat exchanger 62, and the cooling medium water jacket 59 are respectively connected by cooling medium conduction pipes 63a, 63b, 63c, and 63d provided as a cooling medium conduction path, and the exhaust heat recovery unit 63e is cooled. A cooling medium circulation path is formed in the middle of the medium conduction pipe 63d.

  The heat exchanger 62 is supplied with the working medium that has passed through the expander 15 and the second liquid medium jacket 19 and the cooling medium before being supplied to the cooling medium water jacket 59, and between the working medium and the cooling medium. It is comprised so that heat exchange may be performed.

  A part of the cooling medium conducting pipe 63 d that connects the cooling medium water jacket 59 and the cooling medium storage tank 58 is located closer to the exhaust side than the heater 13 in the exhaust heat recovery apparatus 14. It arrange | positions helically along the internal peripheral surface.

  The cooling medium storage tank 58 is provided with an outflow pipe 58a for flowing out the stored cooling medium to the outside and an inflow pipe 58b for injecting the cooling medium from the outside. Other configurations are the same as those of the external combustion engine 1A shown in FIG.

  In the cogeneration system 10 </ b> A of FIG. 4, the cooling medium is supplied from the cooling medium storage tank 58 to the heat exchanger 62 via the second pump 61 and exchanges heat with the working medium. Heat exchange with the working gas in (not shown in FIG. 4), heat exchange with the air inside the exhaust heat recovery unit 14 in the cooling medium conducting pipe 63d, and the process stored in the cooling medium storage tank 58 is repeated. . Accordingly, the cooling medium is heated by heat exchange in the heat exchanger 62, the cooling medium water jacket 59, and the cooling medium conducting pipe 63d, and the heat recovered by this heating is stored in the cooling medium storage tank 58. The recovered heat can be used in various ways by allowing the cooling medium to flow out from the outflow pipe 58a.

  Here, the energy efficiency in this embodiment shown as an example of the calculation of the present invention will be considered. FIG. 5 is an energy flow diagram during power generation in the cogeneration system 10A according to this embodiment, and FIG. 6 is a Mollier diagram when the Rankine cycle circuit 11 in the cogeneration system 10A according to this embodiment is driven. is there. Both figures consider the case where the working medium of Rankine cycle 11 is R245ca and the working gas of Stirling engine 12 is helium (He).

  For example, in the cogeneration system 10 </ b> A, when the working medium flowing through the first fluid medium jacket 18 is heated to about 175 ° C. by the heating of the heater 13 (h <b> 1 in FIGS. 4 and 5) and the working medium expands in the expander 15. The temperature of the working medium when being sent out from the expander 15 becomes about 60 ° C. (h2 in FIGS. 4 and 5), and is supplied to the heat exchanger 62 through the second liquid medium jacket 19. The temperature of the working medium when it is sent out from the heat exchanger 62 becomes about 30 ° C. (h3 in FIGS. 4 and 5), and is supplied to the first pump 17 (h4 in FIGS. 4 and 5). As a result, as shown in FIG. 6, 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, consider a case where the working gas inside the expansion chamber 33 is heated to about 800 ° C. Assuming that the temperature of the cooling medium supplied to the water jacket 59 is about 15 ° C., when the working gas expanded in the expansion chamber 33 of the Stirling engine 12 is sent to the contraction chamber 34, the working gas is cooled to about 70 ° C. . The cooling medium supplied to the water jacket 59 is heat-exchanged in the shrink chamber 34 of the Stirling engine 12 and heated to about 50 ° C. This cooling medium is further heated by the exhaust heat recovery unit 63 e to a temperature close to the boiling point, and is sent to the cooling medium storage layer 58.

Here, if the Stirling engine 12 is driven as a Carnot cycle, from the output shaft 43 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. 6, considering the case where the heater 13 of the cogeneration system 10A of this embodiment is heated with a calorific value of 4 kW, the output shaft 43 of the Stirling engine 12 is 0.73 kW (ie, as described above). The output shaft 19 of the expander 15 of the Rankine cycle circuit 11 is 0.15 kW (30% of the heat energy (2.42 kW) input to the high temperature side cylinder 27 of the Stirling engine 12). That is, from 16% (0.22 kW) of the heat energy (1.38 kW) input to the first fluid medium jacket 18 of the Rankine cycle circuit 11, the output loss of the Rankine cycle circuit 11 is 32% (0.22 kW × 0. 32 = 0.07 (kW))). 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 cogeneration system 10A, assuming that 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 58, 2.1 kW. Is stored in the cooling medium storage tank 58. Therefore, the total amount of energy acquired by the cogeneration system 10A is 2.8 kW (0.7 (kW) +2.1 (kW) = 2.8 (kW)), and the overall efficiency of this cogeneration system 10A ( 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 generator 44 is driven, and the working medium of the Rankine cycle circuit 11 and the working gas of the Stirling engine 12 are driven. By collecting the exhaust heat inside the exhaust heat recovery unit 14 with the coolant of the Stirling engine 12 and accumulating it in the coolant storage tank 58, high energy conversion efficiency can be obtained. Furthermore, in this embodiment, the heat loss in the Stirling engine 12 shown in FIG. 6 and the Rankine cycle circuit 11 are performed by directly exchanging heat between the cooling medium and the working medium in the heat exchanger 62. Energy loss (b) can be further reduced, and higher energy conversion efficiency can be obtained.

[Embodiment 2 of the Invention]
FIG. 7 shows a second embodiment of the present invention.

  The external combustion engine 1 </ b> B of this embodiment is provided with a crank chamber 65 as a “first chamber” and an expander accommodation chamber 66 as a “second chamber” inside the housing 21. The space between the crank chamber 65 and the expander housing chamber 66 is blocked by a partition wall 67, and the space between the chambers 65, 66 is airtight. The crank chamber 65 accommodates the output shaft 43 of the Stirling engine 12 including the first crank portion 43a and the second crank portion 43b. The expander storage chamber 66 stores an expander 15 that expands the working medium circulating in the Rankine cycle circuit 11 and a generator 44. The output shaft 46 of the expander 15 and the input shaft 45 of the generator 44 are respectively connected to the rotation adjusting unit 48 inside the expander housing chamber 66. The other end of the input shaft 45 is connected to the output shaft 43 of the Stirling engine 12. The working medium expanded by the expander 15 is configured to be discharged into the expander accommodating chamber 66, and the expander accommodating chamber 66 is connected to a heat exchanger (not shown in FIG. 7). The end portion of the working medium conducting tube 20a is configured to face.

  The Rankine cycle circuit 11 of this embodiment is configured to heat the working medium (for example, the first liquid medium jacket 18 of the first embodiment) and cools the working medium in the same manner as the Rankine cycle circuit 11 shown in FIG. Configuration (for example, heat exchanger 62 of the first embodiment), configuration for pressurizing and compressing the working medium (for example, pump 17 of the first embodiment), configuration for cooling low temperature side cylinder 28 in Stirling engine 12 (for example, the embodiment) 1, which are omitted in FIG. 7 (note that the description of this configuration is omitted in the embodiments after this embodiment as well). ing.). Other configurations are the same as those in the first embodiment.

  Next, the operation of this embodiment will be described.

  In the Rankine cycle circuit 11, when the working medium is supplied from the working medium conducting tube 20 e to the expander 15 and expands, the expanded working medium is discharged into the expander housing chamber 66. The working medium exchanges heat with the generator 44 when passing through the inside of the expander housing chamber 66, absorbs the heat of the generator 44, and then is sent to the second fluid medium jacket 19 through the working medium conducting pipe 20 a. .

  In this embodiment, a crank chamber 65 in which the output shaft 43 of the Stirling engine 12 is accommodated, an expander 15 for expanding the working medium circulating in the generator 44 and the Rankine cycle circuit 11, and the expander 15 are accommodated. By providing the expander accommodating chamber 66 through which the expanded working medium passes, the generator 44 can be installed without any special cooling mechanism for the generator 44 due to the passage of the working medium whose temperature has decreased through the expansion stroke. Can be cooled.

Embodiment 3 of the Invention
FIG. 8 shows a third embodiment of the present invention. In the embodiment shown in the figure, the configuration of the Rankine cycle circuit 11 is partially omitted.

  In the external combustion engine 1 </ b> C of this embodiment, a crank chamber 68 as a “third chamber” is provided inside the housing 21. The crank chamber 68 accommodates the output shaft 43 of the Stirling engine 12, the expander 15 for expanding the working medium circulating in the Rankine cycle circuit 11, and the generator 44. The crank chamber 68 is filled with a working medium of the Rankine cycle circuit 11, for example, R245fa and R245ca. When the expanded working medium is discharged into the crank chamber 68, the expander 15 is preferably discharged at a pressure high enough to stir the lubricating oil in the oil pan 26. Further, it is desirable that the working medium is mixed with lubricating oil for the crank mechanism. In this embodiment, the kind of the gas filled in the crank chamber 68 and the working gas (helium, hydrogen, etc.) filled in the high temperature side cylinder 27 and the low temperature side cylinder 28 are different. It is desirable that the members 38 and 39 have high confidentiality. Other configurations are the same as those of the second embodiment.

  Next, the operation of this embodiment will be described.

  In the Rankine cycle circuit 11, when the working medium is supplied from the working medium conducting tube 20 e to the expander 15 and expands, the expanded working medium is discharged into the crank chamber 68. The working medium exchanges heat with the generator 44 when passing through the crank chamber 68, absorbs the heat of the generator 44, and then is sent to the second fluid medium jacket 19 through the working medium conducting pipe 20 a. When the working medium is discharged into the crank chamber 68, the lubricating oil stored in the oil pan 26 is agitated, and the lubricating oil is attached to the first crank portion 43a and the second crank portion 43b of the output shaft 43. In addition, when the working medium is mixed with the lubricating oil of the crank mechanism, the working medium has an effect of improving the driving of the crank mechanism when passing through the crank chamber 68.

  In this embodiment, in the housing 21, the output shaft 43 of the Stirling engine 12, the expander 15 for expanding the working medium circulating in the Rankine cycle circuit 11, and the generator 44 are accommodated in the same chamber. In addition, since the crank chamber 68 through which the working medium expanded by the expander 15 passes is provided, the generator 44 is not provided with a cooling mechanism for the generator 44 due to the passage of the working medium whose temperature has decreased through the expansion stroke. 44 can be cooled.

  In this embodiment, when the working medium is passed from the expander 15 to the inside of the crank chamber 68, the lubricating oil existing in the crank chamber 68 is agitated, or the working medium itself has the function of the lubricating oil. If it is provided, the function of the lubricating oil can be achieved only by passing the working medium through the crank chamber 68. Accordingly, it is necessary to provide a mechanism for stirring the lubricating oil stored in the oil pan 26 (for example, when the output shaft 43 rotates, the first crank portion 43a and the second crank portion 43b are disposed inside the oil pan 26. Therefore, it is not necessary to design the balance between the output shaft 43 and the oil pan 26 so that the amount of the lubricant is repelled, and the oil pan 26 does not need to store the lubricating oil. Can be made more compact. Further, since only one type of lubricating oil is used in the crank chamber 68, maintenance can be performed easily.

  [Embodiment 4 of the Invention]

  9 and 10 show an embodiment of the present invention.

  The external combustion engine of this embodiment is used in a cogeneration system whose system configuration is shown in FIG. 9 (Note that all the external combustion engines of Embodiments 5 to 11 described later are also used in the same cogeneration system. That is.) In addition to the Rankine cycle circuit 11 and the Stirling engine 12, the cogeneration system 10B includes a refrigerating and air conditioning cycle circuit 70 that circulates the second working medium.

  This refrigeration air-conditioning cycle circuit 70 includes a compressor 71, a third heat exchanger 72, an expansion valve 73, and a second heat exchanger 74, and further includes a four-way valve 76, which includes second working medium conduction pipes 75a, 75b, 75c, 75d, 75e, 75f are connected to form a circulation path for the second working medium. 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 71 is a scroll type similar to the expander 15 of the first embodiment (details will be described later), and compresses the second working medium based on the rotational kinetic energy.

  The third heat exchanger 72 is an outdoor heat exchanger and includes a fan for blowing air, and performs heat exchange between the second working medium and ambient air.

  The expansion valve 73 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 73 as long as it has the same function.

  The second heat exchanger 74 is an indoor heat exchanger, and includes a blower fan, forcibly exchanging heat between the second working medium passing through and the indoor air.

  The four-way valve 76 switches the flow path of the second working medium in the refrigeration air conditioning cycle circuit 70. That is, the four-way valve 76 forms a first circulation path for using the second heat exchanger 74 as an evaporator at the first position shown in FIG. At the position (conduction relationship indicated by a dotted line in FIG. 9), a second circulation path for using the second heat exchanger 74 as a condenser is formed. Although not shown, a cooling medium circulation circuit 60 similar to the case of the cogeneration system 10A shown in FIG. 4 may be provided in the cogeneration system 10B.

  FIG. 10 shows a schematic view of the main part of the external combustion engine 1D of this embodiment. In the figure, the configurations of the Rankine cycle circuit 11 and the refrigerating and air conditioning cycle circuit 70 are partially omitted.

  In this embodiment, the input shaft 77 of the compressor 71 is connected to the output shaft 43 of the Stirling engine 12 instead of the generator 44 in the second embodiment. The compressor 71 is composed of a pair of spiral scrolls 71a and a movable scroll 71b, and the volume of the space partitioned by the two scrolls 71a and 71b is changed by the kinetic energy in the rotational direction supplied from the input shaft 77. To compress the second working medium.

  Further, the housing 21 is provided with an expander accommodating chamber 24 in which the expander 15 is accommodated, a crank chamber 78 in which a crank mechanism is accommodated, and a compressor accommodating chamber 79 as a “fourth chamber” in which the compressor 71 is accommodated. Partition walls 25 and 80 are provided between the expander accommodating chamber 24 and the crank chamber 78, and between the crank chamber 78 and the expander accommodating chamber 24 so that the chambers 24, 78, and 79 are formed in an airtight state. Has been. Other configurations are the same as those of the first embodiment.

  Next, the operation of this embodiment will be described.

  The case where the second heat exchanger 74 of the refrigeration air conditioning cycle circuit 70 shown in FIG. 9 is used as an evaporator (that is, when indoors are cooled) will be described as an example. When the Stirling engine 12 or the expander 15 is driven, the compressor 71 is driven by the kinetic energy supplied from the output shaft 43 to the input shaft 77 to compress the second working medium. The high-temperature and high-pressure second working medium compressed by the compressor 71 is supplied to the third heat exchanger 72 via the second working medium conducting pipes 75a and 75b, and is cooled by heat exchange with the cooling medium. The second working medium in the liquid state cooled by heat exchange is supplied to the expansion valve 73 via the second working medium conducting pipe 75c and expands. The expanded low-temperature and low-pressure second working medium is supplied to the second heat exchanger 74 through the second working medium conducting pipe 75d in a gas-liquid mixed state, and heat exchange with indoor air is performed. 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 second heat exchanger 74 via the second working medium conducting pipe 75e to the compressor 71 and compressed again, and the second working medium is circulated in the same manner. Done.

  In this embodiment, a refrigerating and air-conditioning cycle circuit 70 including a compressor 71 that compresses a second working medium and a second heat exchanger 74 that performs heat exchange between indoor air and the second working medium is provided. Provided, the input shaft 77 of the compressor 71 is connected to the output shaft 43 of the Stirling engine 12, so that a driving force is supplied to the refrigeration / air-conditioning cycle circuit 70 with the output of at least one of the Stirling engine 12 and the expander 15. Thus, the second heat exchanger 74 can realize a temperature adjustment mechanism that heats or cools indoor air.

  In this embodiment, the housing 21 is provided with a compressor housing chamber 79 in which the compressor 71 that compresses the second working medium is housed, so that the driving force of the Stirling engine 12 and the Rankine cycle circuit 11 is generated. The portion that needs to be supplied with the driving force in the refrigeration / air-conditioning cycle circuit 70 can be accommodated in the integrally formed housing 21. Thereby, the main part of the external combustion engine 1D used together with electric power generation etc. and air conditioning can be formed compactly.

[Embodiment 5 of the Invention]
FIG. 11 shows an embodiment of the present invention. In the figure, the structures of the Rankine cycle circuit 11 and the refrigerating and air conditioning cycle circuit 70 are partially omitted (the following drawings are all the same).

  As shown in FIG. 11, the housing 21 in the external combustion engine 1 </ b> E of this embodiment contains a compressor 71 that compresses the second working medium circulating in the output shaft 43 of the Stirling engine 12 and the refrigeration air conditioning cycle circuit 70. A crank chamber 81 as a “fifth chamber” and an expander accommodating chamber 24 as a “sixth chamber” in which the expander 15 is accommodated are provided. A partition 25 separates the crank chamber 81 and the expander storage chamber 24. In this embodiment, carbon dioxide is used for the second working medium and the working gas filled in the expansion chamber 33 and the contraction chamber 34. Other configurations are the same as those of the fourth embodiment.

  Next, the operation of this embodiment will be described.

  The second working medium supplied to the compressor 71 is compressed and supplied to the second working medium conducting pipe 75a. The second working medium flows into the crank chamber 81 from the second working medium conducting pipe 75f, and the second working medium is also filled into the crank chamber 81.

  In this embodiment, a crank chamber 81 in which the output shaft 43 of the Stirling engine 12 and the compressor 71 are accommodated in the housing 21, and an expander in which an expander 15 for expanding the working medium circulating in the Rankine cycle circuit 11 is accommodated. Since the housing chamber 24 is provided integrally, the structure of the external combustion engine 1E can be simply formed, and the main part of the external combustion engine 1E can be formed compactly. Further, since the output shaft 43 of the Stirling engine 12 and the compressor 71 of the refrigerating and air conditioning cycle circuit 70 are accommodated in the same chamber, the working gas filled in the expansion chamber 33 and the contraction chamber 34 of the Stirling engine 12 and the refrigerating and air conditioning cycle circuit 70 The second working medium can be shared, and maintenance can be performed easily.

  Further, in this embodiment, the second working medium circulating in the refrigeration air conditioning cycle circuit 70 and the working gas of the Stirling engine 12 are carbon dioxide. Sharing with two working media can be realized.

Embodiment 6 of the Invention
FIG. 12 shows an embodiment of the present invention.

  As shown in FIG. 12, in the external combustion engine 1 </ b> F of this embodiment, a third fluid medium jacket 82 is provided on the outer wall surface of the low temperature side cylinder 28, and is closer to the intake side than the heater 13 of the exhaust heat recovery device 14. Is provided with a fourth fluid medium jacket 83. The third working medium 82 of the refrigeration air conditioning cycle circuit 70 supplied to the compressor 71 passes through the third fluid medium jacket 82. The fourth working medium 83 that has passed through the compressor 71 passes through the fourth fluid medium jacket 83. The third fluid medium jacket 82, the compressor 71, and the fourth fluid medium jacket 83 are connected by second working medium conducting tubes 75g and 75h, respectively. The other configuration is the same as that of the fourth embodiment.

  Next, the operation of this embodiment will be described.

  When the second working medium heated and cooled in the third heat exchanger 72 or the second heat exchanger 74 as an evaporator is supplied to the third liquid medium jacket 82 through the second cooling medium conducting pipe 75f. In the third fluid medium jacket 82, heat exchange between the working gas and the second working medium is performed via the wall surface of the low temperature side cylinder 28, and the working gas is cooled and the second working medium is heated. The second working medium that has undergone heat exchange is supplied to the compressor 71 through the second working medium conducting pipe 75g and compressed, and the compressed second working medium passes through the second working medium conducting pipe 75h to form the fourth liquid medium. It is supplied to the jacket 83. In the fourth liquid medium jacket 83, heat exchange between the air before being supplied to the heater 13 through the wall surface of the exhaust heat recovery device 14 and the second working medium is performed, and the air is heated and the second operation is performed. The medium is cooled. The second working medium subjected to the heat exchange is supplied to the second heat exchanger 74 or the third heat exchanger 72 as a condenser.

  In this embodiment, the low temperature side cylinder 28 is provided with a third fluid medium jacket 82 through which the second working medium supplied to the compressor 71 passes, so that the compression process in the compressor 71 of the refrigeration air conditioning cycle circuit 70 is performed. To improve the efficiency of the process of cooling and shrinking the working gas inside the low temperature side cylinder 28 by exchanging heat between the low temperature second working medium and the working gas filled in the shrinking chamber 34 inside the low temperature side cylinder 28 before passing. Can do. Further, in this embodiment, the fourth fluid medium jacket 83 through which the second working medium that has passed through the compressor 71 passes is provided on the intake side of the exhaust heat recovery device 14, so that the compression process by the compressor 71 is performed. Heat exchange is performed between the high-temperature second working medium that has passed and the air before being supplied to the heater 13, and the air heated by this heat exchange is supplied to the heater to improve the heating efficiency, and the compressed high temperature Since the high-pressure gas (second working medium) is cooled, the efficiency of the refrigeration cycle is also improved. Thereby, the efficiency of the heater 13 can be improved.

Embodiment 7 of the Invention
FIG. 13 shows an embodiment of the present invention.

  As shown in FIG. 13, in the external combustion engine 1 </ b> G of this embodiment, the housing 21 has a first power transmission chamber 84, and one side of the first power transmission chamber 84 (left side in FIG. 13) has an expander accommodating chamber 24. The compressor housing chamber 79 is provided on the other side of the first power transmission chamber 84 (the right side in FIG. 13), and the second power transmission chamber 85 is provided on the upper side of the first power transmission chamber 84. Between the first power transmission chamber 84 and the expander housing chamber 24, between the first power transmission chamber 84 and the compressor housing chamber 79, between the first power transmission chamber 84 and the second power transmission chamber 85, and second. The power transmission chamber 85 and the high temperature side cylinder 27 and the low temperature side cylinder 28 provided on the upper side thereof are partitioned by partition walls 25, 80 and 86, respectively. A ring-shaped seal member 87 is provided below the boundary position between the cylinders 27 and 28 in the partition wall 86. The seal member 87 in this embodiment is formed by a mechanical seal having high airtightness, but may be formed by another member having high airtightness such as a gland packing. The output shaft 46 connected to the expander 15 and the input shaft 77 connected to the compressor 71 pass through the partition portions 25 and 80, respectively, and the tip side is disposed inside the first power transmission chamber 84. .

  In the external combustion engine 1G, a swash plate mechanism is used as a “power transmission mechanism” that transmits the power of the Stirling engine 12 to the input shaft 77 of the compressor 71. Specifically, the inclined plate mechanism includes a rotation main shaft 88 that is rotatably inserted into the seal member 87, a swash plate 89 provided at an upper end portion of the rotation main shaft 88, and a first engagement as a “connecting portion”. It comprises a joint portion 90, a second engaging portion 91 as a “connecting portion”, and a cross shaft face gear 92 as a “rotation converting portion”.

  The axial direction of the rotation main shaft 88 is provided so as to be parallel to the axial direction of the connecting rods 40 and 41.

  The swash plate 89 is formed in a substantially disc shape by a highly rigid material, and the center portion is connected to the upper end portion of the rotation main shaft 88. The swash plate 89 is provided such that the plate surface direction is inclined with respect to the axial direction of the rotary main shaft 88. The inclination angle in the plate surface direction with respect to the rotation main shaft 88 can be changed by an angle adjusting mechanism (not shown).

  The first engaging portion 90 is provided at the lower end portion of the connecting rod 40 of the high temperature side piston 29, and the second engaging portion 91 is provided at the lower end portion of the connecting rod 41 of the low temperature side piston 30. Both the first engaging portion 90 and the second engaging portion 91 are formed in a substantially U-shape when viewed from the side, and are connected by sandwiching the outer edge portion of the swash plate 89. The cross shaft face gear 92 includes a gear 92 a provided at the lower end of the rotary main shaft 88, a gear 92 b provided at the end of the output shaft 46 connected to the expander 15, and an end of the input shaft 77 connected to the compressor 71. A gear 92c provided in the section is formed by meshing with each other. 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 is driven and the high temperature side piston 29 and the low temperature side piston 30 are advanced and retracted in the vertical direction, the connecting rod 40 and the connecting rod 41 are integrated with the pistons 29 and 30 in the vertical direction, and the movement in this forward and backward direction is performed. Energy is transmitted to the swash plate 89 via the first engagement portion 90 and the second engagement portion 91, and the movement of the pistons 29 and 30 in the forward and backward direction of the swash plate 89 is centered on the rotation main shaft 88 of the swash plate 89. Converted to rotational motion. As a result, the rotation main shaft 88 is rotated, and this rotation is transmitted from the gear 92 a to the gear 92 c, converted into the axial rotational motion of the input shaft 77, and the compressor 71 is driven by the rotation of the input shaft 77. On the other hand, the rotation of the output shaft 46 by the drive of the expander 15 is adjusted by the rotation adjusting unit 48 and then transmitted to the input shaft 77 via the gears 92b, 92a, 92c to drive the compressor 71.

  In this embodiment, the power transmission mechanism that transmits the power of the Stirling engine 12 to the input shaft 77 of the compressor 71 of the refrigeration air conditioning cycle circuit 70 is connected to the high temperature side piston 29 and the low temperature side piston 30 of the Stirling engine 12. The first engagement portion 90 and the second engagement portion 91 that move forward and backward together with the pistons 29 and 30 in the forward and backward direction of both pistons 29 and 30, and the axial direction with respect to the forward and backward direction of both pistons 29 and 30 , A rotatable rotating spindle 88 provided in parallel, a rotating spindle 88 connected to the center of the rotating spindle 88 and having a first engaging portion 90 and a second engaging portion 91 disposed on the peripheral side. A swash plate 89 that is provided with an inclined plate surface direction with respect to the axial direction of the two pistons 29, 30 to convert the movement of the pistons 29, 30 in the advancing / retreating direction into the rotational movement of the rotary main shaft 88; The cross shaft face gear 92 that is connected and converts the rotational motion of the rotary main shaft 88 into the axial rotational motion of the input shaft 77 and transmits it, thereby connecting the lengths of the connecting rods 40 and 41 and the Stirling engine 12. The length of each piston 29, 30 in the advance / retreat direction can be shortened, and the main part of the external combustion engine 1G can be formed compactly. Further, the operation of the power transmission mechanism can be stabilized. Further, by adjusting the inclination angle of the swash plate 89, the stroke amounts of the high temperature side piston 29 and the low temperature side piston 30 can be easily changed, and the drive states of the high temperature side piston 29 and the low temperature side piston 30 can be adjusted.

[Embodiment 8 of the Invention]
FIG. 14 shows an embodiment of the present invention.

  As shown in FIG. 14, the main body portion of the external combustion engine 1 </ b> H according to this embodiment includes a first power transmission chamber 84, a second power transmission chamber 85, and an expander housing chamber 24 in the housing 21. A second power transmission chamber 85 is provided on one side of the first power transmission chamber 84 (left side in FIG. 14), and the expander housing chamber 24 is provided above the first power transmission chamber 84. A high temperature side cylinder 27 and a low temperature side cylinder 28 are provided on one side of the second power transmission chamber 85. Partitions 86 and 69 define the space between the first power transmission chamber 84 and the expander housing chamber 24 and the space between the first power transmission chamber 84 and the second power transmission chamber 85, respectively. The high temperature side cylinder 27 and the low temperature side cylinder 28 provided on the side communicate with each other via the second power transmission chamber 85.

  The Stirling engine 12 in this embodiment is placed side by side with the high temperature side cylinder 27 and the low temperature side cylinder 28, that is, the advancing and retreating directions of both pistons 29 and 30 are formed in a substantially horizontal direction. The connecting rod 40 connected to the high temperature side piston 29 and the connecting rod 41 connected to the low temperature side piston 30 are provided in substantially parallel axial directions.

  A “power transmission mechanism” that transmits power from the high temperature side cylinder 27 and the low temperature side cylinder 28 to the input shaft 100 of the compressor 94 is a swash plate mechanism similar to that of the seventh embodiment, but the rotation main shaft 88 has both axial directions. It is provided in a substantially parallel direction (that is, a horizontal direction) with respect to the advancing / retreating direction of the pistons 29 and 30.

  The axial direction of the output shaft 46 connected to the expander 15 is disposed so as to be substantially orthogonal to the forward / backward direction of both pistons 29 and 30 (that is, substantially vertical direction). Is disposed in the first power transmission chamber 84 through the partition wall 69.

  A gear 92a provided at the right end of the rotary main shaft 88 and a gear 92b provided at the tip of the output shaft 46 connected to the expander 15 mesh with each other to form a cross shaft face gear 93.

  A compressor 94 is accommodated in the first power transmission chamber 84. The compressor 94 is a reciprocating compressor, and a plurality of, for example, two cylinders 95a and 95b are placed horizontally, that is, the axial direction of both cylinders 95a and 95b is formed in a substantially horizontal direction. 96a and 96b are provided to be able to advance and retract in the horizontal direction. Compression chambers 99a and 99b for compressing the second working medium are formed in a space surrounded by the inner walls of the cylinders 95a and 95b and the tip portions (right side in FIG. 14) of the pistons 96a and 96b.

  On the base end side (left side in FIG. 14) of the pistons 96a and 96b, sandwiching recesses 97a and 97b are provided as “connecting portions” that are substantially concave in a side view. A plurality of, for example, two valves 98a and 98b for adjusting the intake / exhaust state between the second working medium conducting pipes 75f and 75a and the cylinders 95a and 95b are provided on the tip side of the cylinders 95a and 95b.

On the other hand, the second rotation main shaft 100 as an “input shaft” is connected to the gear 92 a on the back surface of the connection surface with the rotation main shaft 88. The axial direction of the second rotation main shaft 100 is provided so as to be substantially parallel to the forward and backward directions of the pistons 29 and 30 of the Stirling engine 12 (that is, the horizontal direction).
A second swash plate 101 is provided at the tip of the second rotation main shaft 100. The center portion of the second swash plate 101 is connected to the second rotation main shaft 100, and the plate surface direction is inclined with respect to the axial direction of the second rotation main shaft 100. The inclination angle of the second swash plate 101 in the plate surface direction with respect to the second rotation main shaft 100 can be changed by an angle adjusting mechanism (not shown).

  The sandwiching recesses 97a and 97b of the cylinders 95a and 95b are connected by sandwiching the outer edge portion of the second swash plate 101.

  The heater 13 of this embodiment is installed in the vicinity of the high temperature side cylinder 27 and above the high temperature side cylinder 27. Further, the exhaust heat recovery device 102 is formed so that the air flow passage is substantially L-shaped. Specifically, the intake side of the exhaust heat recovery unit 102 is located above the heater 13, and the exhaust side extends from the upper side to the lower side from the heater 13 to the high temperature side cylinder 27, It is bent at a substantially right angle below the side cylinder 27 and extends laterally. Note that the oil pan 26 present in the first embodiment does not exist in this embodiment. Other configurations are the same as those in the first embodiment.

  Next, the operation of this embodiment will be described.

  The heat released from the heater 13 is released from the upper side to the lower side through the exhaust heat recovery unit 102 to heat the high temperature side cylinder 27. Dust, oxides, and the like generated by combustion, which is a heating means of the heater 13, are accumulated below the exhaust heat recovery unit 102. The exhaust heat is bent along the exhaust heat recovery unit 102 from the upper side to the lower side and further at a substantially right angle and is discharged to the side.

  On the other hand, when the Stirling engine 12 is driven by the heating of the heater 13 and the high temperature side piston 29 and the low temperature side piston 30 advance and retreat in the horizontal direction, the swash plate 89 rotates to rotate the rotation main shaft 88. Further, when the expander 15 rotates, the output shaft 46 is rotated, and the rotational energy is transmitted from the gear 92b to the gear 92a, and the rotational energy is applied to the rotation main shaft 88. When the second rotation main shaft 100 is rotated by the rotation of the rotation main shaft 88 and the second swash plate 101 is rotated, the pistons 96a and 96b advance and retract in the horizontal direction. Along with this, the valves 98a and 98b are opened and closed, the second working medium flows into the compression chambers 99a and 99b from the second working medium conducting pipe 75f, is compressed, and the second is compressed by opening and closing the valves 98a and 98b. The working medium is discharged to the second working medium conducting tube 75a.

  In this embodiment, the size of the expansion chamber 33 and the contraction chamber 34 in the height direction is increased because the pistons 29 and 30 of the Stirling engine 12 are formed so that the advancing and retracting directions are substantially horizontal. Can be suppressed. Thereby, it becomes possible to install the external combustion engine 1H in a space with a small size in the height direction.

  In this embodiment, in the housing 21, the output shaft 46 is disposed so that the axial direction thereof is substantially perpendicular to the advancing and retracting directions of the pistons 29 and 30 of the Stirling engine 12, and the second rotating main shaft 100. Since the pistons 29 and 30 of the Stirling engine 12 are arranged in a direction substantially parallel to the advancing / retreating direction of the Stirling engine 12, it is possible to prevent the housing 21 from becoming large only in the horizontal direction. Thereby, the external combustion engine 1H can be installed in a narrow space such as a corner of the room.

  In this embodiment, the heater 13 is installed above the high temperature side cylinder 27, and the exhaust heat recovery unit 102 is extended downward from the heater 13 to the high temperature side cylinder 27. The dust, oxides, etc. generated by the combustion that is the heating means of the heater 13 fall along the heat release direction and are accumulated below the exhaust heat recovery unit 102. As a result, the heat conduction state inside the exhaust heat recovery unit 102 can be kept good, and a decrease in energy conversion efficiency accompanying continuous use and a decrease in the service life of the exhaust heat recovery unit 102 can be suppressed.

  In this embodiment, a compressor 94 is provided in the first power transmission chamber 84, the expander accommodating chamber 24 is provided above the first power transmission chamber 84, and the output shaft 46 has an axial direction in the Stirling engine 12. The second rotation main shaft 100 is arranged in a direction substantially parallel to the advancing and retreating directions of the pistons 29 and 30 of the Stirling engine 12. However, conversely, the expander accommodating chamber 24 is provided in the first power transmission chamber 84, the compressor 94 is provided above the first power transmission chamber 84, and the output shaft 46 has a stirling engine in the axial direction. The second rotary main shaft 100 is disposed in a substantially parallel direction with respect to the forward and backward directions of the 12 pistons 29 and 30, and the forward and backward movements of the pistons 29 and 30 of the Stirling engine 12. It may be a configuration that is disposed substantially orthogonally to direction. In this embodiment, the compressor 94 is a reciprocating compressor, but a scroll compressor may be used instead.

Embodiment 9 of the Invention
FIG. 15 shows an embodiment of the present invention.

  As shown in FIG. 15, the main body portion of the external combustion engine 1 </ b> I according to this embodiment does not have the partition wall portion 86 existing in the eighth embodiment, and the first power transmission chamber 84 and the second power transmission chamber 84 in the eighth embodiment. A crank chamber 103 is formed instead of the power transmission chamber 85, and corresponds to the partition wall portion 86 (see FIG. 14) of the external combustion engine 1H between the crank chamber 103 and the high temperature side cylinder 27 and the low temperature side cylinder 28. There is no configuration, and therefore the crank chamber 103 and the high temperature side cylinder 27 and the low temperature side cylinder 28 are in communication with each other. The working gas of the second working medium and the Stirling engine is formed by carbon dioxide, and the inside of the crank chamber 103, the high temperature side cylinder 27, and the low temperature side cylinder 28 is filled with carbon dioxide as the second working medium and working gas. . Other configurations are the same as those in the eighth embodiment.

  In this embodiment, the structure of the external combustion engine 1I can be formed simply, and the main part of the external combustion engine 1I can be formed compactly. Further, there is no partition wall portion 86 (see FIGS. 13 and 14) between the crank chamber 103 and the high temperature side cylinder 27 and the low temperature side cylinder 28. Therefore, the crank chamber 103, the high temperature side cylinder 27, and the low temperature side cylinder 28 With this configuration, the working gas of the Stirling engine 12 and the second working medium of the refrigeration air conditioning cycle circuit 70 can be shared, and maintenance can be performed easily.

[Embodiment 10]
FIG. 16 shows an embodiment of the present invention.

  As shown in FIG. 16, the external combustion engine 1J of this embodiment is provided with a scroll compressor 71 housed in a compressor housing chamber 79 in place of the compressor 94 that is a reciprocating compressor present in the ninth embodiment. It has been. The compressor accommodating portion 79 and the crank chamber 103 are partitioned by a partition wall portion 80. The other configuration is the same as that of the ninth embodiment.

  In this embodiment, by providing the scroll type compressor 71, the external combustion engine 1J in which the main body portion can be installed in a space having a small size in the height direction can be formed with a simple configuration.

[Embodiment 11 of the Invention]
FIG. 17 shows an embodiment of the present invention.

  As shown in FIG. 17, in the external combustion engine 1 </ b> K of this embodiment, an exhaust heat recovery device 104 is provided instead of the exhaust heat recovery device 102 in the eighth embodiment. The heater 13 installed in the exhaust heat recovery device 104 is installed to face the top portion (left end portion in FIG. 17) of the high temperature side cylinder 27 in a substantially horizontal direction. The exhaust heat recovery device 104 includes a horizontal portion 104a and an upward extending portion 104b extending upward from a part of the horizontal portion 104a on the exhaust side. Specifically, the exhaust heat recovery device 104 forms a horizontal portion 104 a provided in a substantially horizontal direction on the exhaust side from the heater 13 to the high temperature side cylinder 27, and the horizontal portion 104 a is located at the position of the high temperature side cylinder 27. The upper extended portion 104b is bent in a substantially vertical direction upward from the position of the high temperature side cylinder 27 where the horizontal portion 104a is bent, and the air flow passage is substantially L-shaped. It is formed to become. The other configuration is the same as that of the eighth embodiment.

  Next, the operation of this embodiment will be described.

  The heater 13 is installed facing the top of the high temperature side cylinder 27, and the exhaust heat recovery device 104 has a horizontal portion 104 a provided on the exhaust side from the heater 13 to the high temperature side cylinder 27 in a substantially horizontal direction, and a horizontal portion. By having an upwardly extending portion 104b that extends upward from a part of 104a, dust, oxides, and the like generated by combustion, which is a heating means of the heater 13, are horizontal in the exhaust heat recovery device 104. It is accumulated below the portion 104a. Thereby, the heat conduction state inside the exhaust heat recovery unit 104 can be kept good, and a decrease in energy conversion efficiency and a decrease in the service life of the exhaust heat recovery unit due to continuous use can be suppressed.

  In this embodiment, the exhaust heat that has not been used to heat the high temperature side cylinder 27 is released upward along the upwardly extending portion 104 b of the exhaust heat recovery unit 104. That is, since the exhaust heat recovery device 104 is disposed substantially coincident with the direction of movement of the heat released from the heater 13, the heat conduction state inside the exhaust heat recovery device 104 is kept good, It is possible to suppress a situation in which the inside of the exhaust heat recovery unit 104 is damaged by heat, and it is possible to suppress a decrease in the service life of the exhaust heat recovery unit 104.

  Further, in this embodiment, the exhaust heat recovery device 104 has the horizontal portion 104a bent at a substantially right angle at the position of the high temperature side cylinder 27, and the upper extending portion 104b has the high temperature side cylinder 27 bent by the horizontal portion 104a. As a result, the heat used for heating the high temperature side cylinder 27 can be released upward as it is. As a result, while adjusting the heater 13 to a state suitable for heating the high temperature side cylinder 27, the exhaust heat after heating is efficiently discharged to the outside of the exhaust heat recovery unit 104, and the heat inside the exhaust heat recovery unit 104 is reduced. It is possible to keep the conduction state better and further suppress the decrease in the service life of the exhaust heat recovery unit 104.

  In this embodiment, the upper extending portion 104b of the exhaust heat recovery device 104 is extended in a substantially vertical direction upward from the position of the high temperature side cylinder 27. However, the present invention is not limited to this. The upper extending portion 104 of the exhaust heat recovery device 104 extends upward in an approximately vertical direction from an arbitrary position of the portion 104a, depending on the installation state of the exhaust heat recovery device 104 and the state of the heater 13 In this way, the heat conduction state inside the exhaust heat recovery unit 104 and the service life of the exhaust heat recovery unit 104 can be appropriately kept good.

  Although the external combustion engines 1A to 1K of the above-described embodiments are formed as household cogeneration systems, the present invention is 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 generator 44 of the cogeneration system. However, the present invention is not limited to this, and the output shafts 46 and 43 such as a motor and a fan (in Embodiments 7 to 11). In addition to these, any device can be applied as the “rotating machine” as long as it is rotationally driven by the rotational energy of the rotation main shaft 88).

  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.

It is the schematic of the structure of the external combustion engine which concerns on Embodiment 1 of this invention. It is the schematic which shows the structure which a part of external combustion engine which concerns on the embodiment deform | transformed. It is the schematic of the structure which a part of external combustion engine which concerns on the embodiment deform | transformed. It is a figure which shows the system configuration | structure of the cogeneration system to which the external combustion engine which concerns on the embodiment is applied. It is an energy flow figure at the time of the electric power generation in the cogeneration system concerning the embodiment. It is a Mollier diagram when the Rankine cycle circuit in the cogeneration system concerning the embodiment operates. It is the schematic of the structure of the principal part of the external combustion engine which concerns on Embodiment 2 of this invention. It is the schematic of the structure of the principal part of the external combustion engine which concerns on Embodiment 3 of this invention. It is a figure which shows the system configuration | structure of the cogeneration system to which the external combustion engine which concerns on Embodiment 4 of this invention is applied. It is the schematic of the structure of the principal part of the external combustion engine which concerns on the embodiment. It is the schematic of the structure of the principal part of the external combustion engine which concerns on Embodiment 5 of this invention. It is the schematic of the structure of the principal part of the external combustion engine which concerns on Embodiment 6 of this invention. It is the schematic of the structure of the principal part of the external combustion engine which concerns on Embodiment 7 of this invention. It is the schematic of the structure of the principal part of the external combustion engine which concerns on Embodiment 8 of this invention. It is the schematic of the structure of the principal part of the external combustion engine which concerns on Embodiment 9 of this invention. It is the schematic of the structure of the principal part of the external combustion engine which concerns on Embodiment 10 of this invention. It is the schematic of the structure of the principal part of the external combustion engine which concerns on Embodiment 11 of this invention. It is a system block diagram of the external combustion engine which concerns on a prior art example. It is a system block diagram of the external combustion engine which concerns on a prior art example.

Explanation of symbols

_{1A, 1A 2, 1A 3,} 1B, 1C, 1D, 1E, 1F, 1G, 1H, 1I, 1J, 1K external combustion engine
11 Rankine cycle circuit
12 Stirling engine
13 Heater
14,102,104 Waste heat recovery unit
15 Expander
18 First fluid jacket (heating unit)
19 Second fluid jacket
21 Housing (main part)
24 Expansion room (6th room)
27 High temperature side cylinder (High temperature part)
28 Low temperature side cylinder (low temperature part)
29 High temperature side piston
30 Low temperature side piston
33 Expansion chamber
34 Shrink chamber
40,41 connecting rod
43,46 Output shaft
44 Generator (Rotating machine)
45 Input shaft
70 Refrigeration and air conditioning cycle circuit
71,94 Compressor
79 Compressor chamber (fourth chamber)
81 Crank chamber (Room 5)
82 Third medium jacket
83 Fourth fluid jacket
88 Rotating spindle
89 Swashplate
90 First engaging part (connecting part)
91 Second engaging part (connecting part)
92,93 Cross shaft face gear (rotation converter)
95a, 95b cylinder
96a, 96b Piston
97a, 97b Holding recess (connecting part)
100 Second rotation spindle
101 Second swash plate

Claims (17)

A Stirling that includes 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, and a low-temperature portion that cools and contracts the working gas and converts the heat energy into kinetic energy An engine, a heater provided in the Rankine cycle circuit for heating the working medium, a heater for heating at least one of the high-temperature parts of the Stirling engine, a rotating machine such as a generator, and a refrigeration air-conditioning cycle circuit An external combustion engine provided with at least one of compressors for compressing a circulating second working medium,
An external combustion engine comprising: an output shaft of the Stirling engine; an output shaft of the expander; and an input shaft of at least one of the rotating machine and the compressor. Inside the integrally formed body part,
2. The outside according to claim 1, wherein an output shaft of the Stirling engine, the expander constituting the Rankine cycle circuit, and at least one of the rotating machine and the compressor are respectively accommodated. Combustion engine. An exhaust heat recovery device for passing the heat output from the heater is provided;
On the exhaust side through which the output heat of the exhaust heat recovery unit passes, a first liquid medium jacket as the heating unit through which the working medium supplied to the expander passes is disposed,
3. The external combustion engine according to claim 1, wherein a second fluid medium jacket through which the working medium that has passed through the expander passes is disposed in the low-temperature portion.   The main unit includes a first chamber in which an output shaft of the Stirling engine is accommodated, and at least one of the rotating machine and the compressor, and the expander that expands the working medium circulating in the Rankine cycle circuit. And a second chamber through which the working medium expanded by the expander passes through the interior of the external combustion engine.   In the main body, the output shaft of the Stirling engine, the expander that expands the working medium circulating in the Rankine cycle circuit, and at least one of the rotating machine and the compressor are in the same chamber. 4. The external combustion engine according to claim 2, wherein a third chamber is provided which is accommodated and through which the working medium expanded by the expander passes.   The said main-body part was provided with the 4th chamber in which the said compressor which compresses the said 2nd working medium which circulates through the said refrigerating and air-conditioning cycle circuit was accommodated. External combustion engine described in 1.   In the main body, a fifth chamber in which the compressor for compressing the second working medium circulating in the output shaft of the Stirling engine and the refrigeration air-conditioning cycle circuit is housed, and the working medium circulating in the Rankine cycle circuit The external combustion engine according to claim 2, further comprising a sixth chamber in which the expander that expands the engine is accommodated.   The external combustion engine according to claim 7, wherein the second working medium circulating in the refrigeration air-conditioning cycle circuit and the working gas of the Stirling engine are carbon dioxide.   The low temperature part is provided with a third fluid medium jacket through which the second working medium supplied to the compressor passes, and the compressor is provided on the intake side for supplying air to the heater of the exhaust heat recovery unit. The external combustion engine according to any one of claims 6 to 8, further comprising a fourth fluid medium jacket through which the second working medium that has passed passes. In the power transmission mechanism that transmits the power of the Stirling engine to the input shaft of the compressor that compresses the second working medium circulating in the refrigeration air conditioning cycle circuit,
A connecting portion that advances and retreats integrally with the piston in the advancing and retreating direction of the piston that forms the expansion chamber of the Stirling engine;
A rotatable rotating spindle provided with an axial direction parallel to the advancing and retracting direction of the piston;
The rotation main shaft is connected to the central portion and the connecting portion is connected to the peripheral side, the plate surface direction is inclined with respect to the axial direction of the rotation main shaft, and the piston moves forward and backward. A swash plate that converts rotational motion of the rotating spindle;
7. A rotation conversion unit connected to the input shaft and the rotation main shaft to convert an axial rotation motion of the rotation main shaft into an axial rotation motion of the input shaft and to transmit the rotation conversion portion. The external combustion engine according to any one of 9 above.   At least one of the expander that expands the working medium circulating in the Rankine cycle circuit and the compressor that compresses the second working medium circulating in the refrigeration air-conditioning cycle circuit is a scroll type. The external combustion engine according to any one of claims 6 to 10.   The compressor that compresses the second working medium circulating in the refrigeration air-conditioning cycle circuit is a reciprocating compressor including a cylinder and a piston, and the expander that expands the working medium circulating in the Rankine cycle circuit And a second rotation main shaft driven by at least one of the Stirling engines, and a central portion is connected to the second rotation main shaft so that the plate surface direction is relative to the axial direction of the second rotation main shaft. An inclined second swash plate is provided, and the piston of the compressor is provided with a connecting portion connected to the second swash plate. The listed external combustion engine.   The external combustion engine according to any one of claims 1 to 12, wherein the piston that forms the expansion chamber of the Stirling engine is formed so that an advancing and retreating direction thereof is along a substantially horizontal direction.   In the main body, either one of the second rotation main shaft and the output shaft is disposed so that an axial direction is substantially perpendicular to an advancing / retreating direction of the piston of the Stirling engine, and the other is the Stirling engine. The external combustion engine according to any one of claims 2 to 13, wherein the external combustion engine is disposed in a substantially horizontal direction with respect to a forward / backward direction of the piston.   The said heater is installed above the said high temperature part, and the said exhaust heat recovery device is extended in the said exhaust side toward the said high temperature part toward the downward direction from the said heater. External combustion engine described in 1.   The heater is installed to face the top of the high temperature part, and the exhaust heat recovery unit is provided on the exhaust side on a horizontal part provided in a substantially horizontal direction from the heater to the high temperature part, and the horizontal part. The external combustion engine according to claim 13, further comprising an upwardly extending portion that extends upward from a part of the portion.   In the exhaust heat recovery device, the horizontal portion is bent at a substantially right angle at the position of the high temperature portion, and the upward extending portion is substantially vertically upward from the position of the high temperature portion where the horizontal portion is bent. The external combustion engine according to claim 16, wherein the external combustion engine is extended.

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