WO2010143418A1 - Engine for electrical recovery - Google Patents

Engine for electrical recovery Download PDF

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Publication number
WO2010143418A1
WO2010143418A1 PCT/JP2010/003816 JP2010003816W WO2010143418A1 WO 2010143418 A1 WO2010143418 A1 WO 2010143418A1 JP 2010003816 W JP2010003816 W JP 2010003816W WO 2010143418 A1 WO2010143418 A1 WO 2010143418A1
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WIPO (PCT)
Prior art keywords
piston
displacer
heat
heat exchanger
recovery engine
Prior art date
Application number
PCT/JP2010/003816
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French (fr)
Japanese (ja)
Inventor
赤澤輝行
中塚勉
星野健
吉原正一
Original Assignee
株式会社ｅスター
独立行政法人 宇宙航空研究開発機構
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Application filed by 株式会社ｅスター, 独立行政法人 宇宙航空研究開発機構 filed Critical 株式会社ｅスター
Publication of WO2010143418A1 publication Critical patent/WO2010143418A1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G1/00—Hot gas positive-displacement engine plants
    • F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
    • F02G1/043—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines
    • F02G1/0435—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines the engine being of the free piston type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G2243/00—Stirling type engines having closed regenerative thermodynamic cycles with flow controlled by volume changes
    • F02G2243/02—Stirling type engines having closed regenerative thermodynamic cycles with flow controlled by volume changes having pistons and displacers in the same cylinder
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G2280/00—Output delivery
    • F02G2280/10—Linear generators

Definitions

  • the present invention relates to an electricity recovery engine using a Stirling engine.
  • the present inventor can increase the heating temperature in the heat exchanger, and by suppressing the heat loss due to the connection between the high temperature part in this heat exchanger and the low temperature part in the cooler, the heat efficiency is high.
  • An efficient Stirling engine has been proposed (Patent Document 1).
  • the present inventor has reduced the variation in dimensions, angles, flatness, etc.
  • Patent Document 2 a displacer piston, a power piston, and a leaf spring to reduce the cost of a Stirling engine
  • Patent Document 3 a cooler with high cooling efficiency
  • Patent Document 4 a highly reliable Scotch-Yoke mechanism with reduced sliding loss
  • Patent Document 5 Stirling Engine to which a small and high-performance actuator can be applied
  • Patent Document 5 Stirling Engine Have proposed high-efficiency heat exchangers (Patent Documents 6, 7, and 8) for increasing the efficiency of the heat exchanger.
  • the present invention is a low-temperature exhaust heat exchanger having sufficient heat transfer performance, which has a low ineffective volume and low passage resistance even from low-temperature exhaust heat in the 200 ° C region discharged from a flue of a factory or the like, and is efficient for electric energy.
  • An object of the present invention is to provide an electricity recovery engine that can be converted into
  • An electricity recovery engine includes a pair of Stirling engines in which a displacer piston and a power piston are coaxially arranged.
  • Each of the Stirling engines has a regenerator and a cooler, and the one Stirling engine is provided.
  • the displacer piston of the other Stirling engine and the displacer piston of the other Stirling engine are arranged to face each other, wherein the displacer piston has one gas passage communicating with the expansion space of the one displacer piston, and the other displacer.
  • One Stirling engine and the other Stirling engine are formed by a heat exchanger that forms the other gas passage communicating with the expansion space of the piston and the heat medium passage for heating the one gas passage and the other gas passage. And Characterized in that the phased.
  • the heat exchanger in the electricity recovery engine according to the first aspect of the invention, oil or molten salt is used as the heat medium flowing through the heat medium passage.
  • the heat exchanger in the electricity recovery engine according to the second aspect of the invention, includes an outer peripheral portion on the piston head side of the one displacer piston and an outer peripheral portion on the piston head side of the other displacer piston. And arranged in a ring shape.
  • an inlet for introducing the heat medium into the heat medium passage and an outlet for deriving the heat medium from the heat medium passage are provided in the heat recovery passage.
  • the heat medium circulates through the heat absorption heat exchanger provided in the exhaust heat gas duct, the heat absorption heat exchanger, and the heat exchanger.
  • a pipe is provided.
  • a sixth invention is the electricity recovery engine according to the first invention, wherein one gas passage is communicated with the regenerator of the other Stirling engine, and the other gas passage is connected to one Stirling engine. The regenerator is communicated with each other.
  • the gas passage is disposed between a pair of opposing displacer pistons, and the flow direction of the gas flowing through the heat medium passage is determined by the displacer. The direction is perpendicular to the axis of the piston.
  • the gas passage is constituted by a plurality of straight pipes, and the straight pipes are arranged in an arc shape.
  • the pair of Stirling engines are operated synchronously at a phase of 0 degrees.
  • a linear generator is attached to each of the power pistons, and a control motor is attached to each of the displacer pistons.
  • An eleventh invention is the electricity recovery engine according to the ninth invention, wherein one power generator and one displacer piston are attached to one linear generator, the other power piston and the other displacer piston. Is characterized in that the other linear generator is attached.
  • a twelfth invention is characterized in that, in the electricity recovery engine according to the ninth invention, a rotary generator is attached to each of the power pistons, and a control motor is attached to each of the displacer pistons. To do.
  • a thirteenth aspect of the invention is the electricity recovery engine according to the ninth aspect of the invention, wherein one rotary generator is attached to the one power piston and the one displacer piston, and the other power piston and the other displacer.
  • the piston is equipped with the other rotary generator.
  • the present invention by arranging a pair of Stirling engines to face each other, it is possible to provide an electric recovery engine that has a simpler and higher performance structure and can realize electric recovery from unused low-temperature exhaust heat.
  • the present invention can provide an electric recovery engine that can reduce the ineffective volume and passage resistance even when using low-temperature exhaust heat, and can therefore be efficiently converted into electric energy.
  • FIG. 1 is an external perspective view of an electricity recovery engine according to an embodiment of the present invention.
  • FIG. 2 is a cross-sectional perspective view of the main part of the electricity recovery engine.
  • FIG. 3 is a sectional view of the electricity recovery engine.
  • FIG. 4 is a cross-sectional view showing an endothermic heat exchanger of the electricity recovery engine.
  • FIG. 5 is a sectional view taken along line XX in FIG.
  • FIG. 6 is a cross-sectional view showing another heat absorption heat exchanger of the electricity recovery engine according to this embodiment.
  • FIG. 7 is a sectional view taken along line XX in FIG.
  • FIG. 8 is a conceptual configuration diagram of an electricity recovery engine according to another embodiment of the present invention.
  • FIG. 9 is a perspective view of an essential part of the electricity recovery engine.
  • FIG. 9 is a perspective view of an essential part of the electricity recovery engine.
  • FIG. 10 is a conceptual configuration diagram of an electricity recovery engine according to still another embodiment of the present invention.
  • FIG. 11 is a conceptual configuration diagram of an electricity recovery engine according to still another embodiment of the present invention.
  • FIG. 12 is a conceptual configuration diagram of an electricity recovery engine according to still another embodiment of the present invention.
  • the electricity recovery engine includes one gas passage communicating with the expansion space of one displacer piston, the other gas passage communicating with the expansion space of the other displacer piston, and one gas.
  • One Stirling engine and the other Stirling engine are connected and unitized by a heat exchanger that forms a passage and a heat medium passage for heating the other gas passage.
  • a pair of Stirling engines are opposed to each other, a heat exchanger necessary for each Stirling engine is configured by one heat exchanger, and the pair of Stirling engines are connected by this heat exchanger.
  • a simple configuration can be achieved.
  • the second embodiment of the present invention uses oil or molten salt as a heat medium flowing in the heat medium passage in the electricity recovery engine according to the first embodiment. According to the present embodiment, by using oil or molten salt as a heat medium, sufficient heat recovery can be performed even when the heat transfer area is small, particularly when using low-temperature exhaust heat, and the heat exchanger The dead space, that is, the ineffective volume can be reduced.
  • the pressure change can be increased, the illustrated power can be increased, and the power generation output can be increased.
  • the heat exchanger by configuring the heat exchanger with a material with good thermal conductivity (SiC, copper material, etc.) once the heat energy of the low-temperature exhaust heat is stored in the heat medium, the heat exchanger loss can be reduced, Since the heat exchanger loss using the medium can be covered, an efficient electricity recovery engine can be realized.
  • the heat exchanger is arranged on the piston head side outer peripheral portion of one displacer piston and on the piston head side of the other displacer piston. It is arranged in a ring shape on the outer periphery.
  • an inlet for introducing the heat medium into the heat medium passage and an outlet for deriving the heat medium from the heat medium passage are heated. It arrange
  • a small heat exchanger using oil or molten salt only on the outer periphery of the piston head, not between the piston heads the axial length of the displacer piston can be shortened.
  • the heat medium includes an endothermic heat exchanger provided in the exhaust heat gas duct, an endothermic heat exchanger, and the heat exchanger.
  • Circulating piping is provided.
  • the heat of the exhaust heat gas duct is conveyed to the Stirling engine using oil or molten salt as a heat medium, so that the exhaust heat can be utilized with high thermal efficiency.
  • the Stirling engine can be constructed without being affected by the arrangement of the exhaust heat gas duct, the workability is good. Therefore, it is possible to increase the degree of freedom in layout and cope with various exhaust heat sources even in high places and narrow places where it is difficult to install the exhaust gas duct.
  • one gas passage is communicated with a regenerator of the other Stirling engine, and the other gas passage is connected to one Stirling engine.
  • the regenerator In communication with the regenerator.
  • the gas derived from the expansion space of one Stirling engine is led to the regenerator of the opposite Stirling engine without returning the gas to the regenerator of the same Stirling engine, and the expansion of the other Stirling engine is performed.
  • the gas led out from the space is led to the regenerator of the opposite Stirling engine without returning it to the regenerator of the same Stirling engine, for example, it is not necessary to bend the gas passage into a U-shape and the gas has low flow resistance Since it can be a passage, pressure loss can be reduced and efficiency can be increased. Furthermore, compared with the case where there exists a bending part like a U-shaped part, reliability is improved, without thinning. Furthermore, even when thermal spraying (metal, ceramics) and coating are applied to the corrosive gas, since there is no bend, the adhesion strength between the corrosion-resistant film and the gas passage material is increased, Durability can be improved.
  • the gas passage is disposed between a pair of opposing displacer pistons, and the flow direction of the gas flowing through the heat medium passage is determined. The direction is perpendicular to the axis of the displacer piston. According to this Embodiment, when it constructs in a flue like an exhaust heat gas duct, the exhaust heat of the gas which flows through a flue can be collect
  • the gas passage is constituted by a plurality of straight pipes, and the respective straight pipes are arranged in an arc shape.
  • a pair of Stirling engines are operated synchronously with a phase of 0 degrees.
  • the vibration can be reduced by the synchronous operation of the pair of Stirling engines.
  • a linear generator is attached to each power piston, and a control motor is attached to each displacer piston. is there.
  • the present embodiment by using a linear generator, it is possible to perform highly efficient electricity recovery with less transmission loss compared to a rotary generator, and synchronization can be easily performed by each control motor.
  • one power generator and one displacer piston are attached with one linear generator, and the other power piston and the other displacer.
  • the other linear generator is attached to the piston.
  • by using a linear generator it is possible to perform highly efficient electricity recovery with less transmission loss compared to a rotary generator and to keep the load of each linear generator constant. Can be easily performed.
  • a rotary generator is attached to each power piston, and a control motor is attached to each displacer piston. It is. According to this embodiment, since the phases of the power piston and the displacer piston are fixed, synchronization can be easily performed.
  • one power generator and one displacer piston are attached with one rotary generator, the other power piston and the other power piston.
  • the displacer piston is provided with the other rotary generator. According to this embodiment, since the phases of the power piston and the displacer piston are fixed, synchronization can be easily performed.
  • FIG. 1 is an external perspective view of the electricity recovery engine according to the present embodiment
  • FIG. 2 is a cross-sectional perspective view of the main part of the electricity recovery engine
  • FIG. 3 is a sectional view of the electricity recovery engine
  • FIG. FIG. 5 is a sectional view showing the heat exchanger
  • FIG. 5 is a sectional view taken along line XX in FIG.
  • the sealed container 10 of the electricity recovery engine according to the present embodiment includes a cylindrical body 11 and container ends 12 ⁇ / b> A and 12 ⁇ / b> B disposed at both ends of the body 11.
  • the container end portions 12 ⁇ / b> A and 12 ⁇ / b> B are formed in a cylindrical shape having a larger diameter than the body portion 11.
  • a heat medium introduction port 13 for introducing the heat medium and a heat medium outlet port 14 for deriving the heat medium are attached to the outer peripheral surface of the central portion in the longitudinal direction of the body 11.
  • cooling water inlets 15A and 15B for introducing cooling water and cooling water outlets 16A and 16B for leading cooling water are attached to the outer peripheral surfaces of both ends of the body portion 11, respectively.
  • the respective container end portions 12A and 12B are provided with wiring connection portions 17A and 17B for taking out the wiring for the linear generator arranged inside the container end portions 12A and 12B.
  • a central portion in the longitudinal direction of the body portion 11 is divided by an end plate 18 (the end plate 18 is omitted in FIG. 2), and a pair of cylinder portions 19A and 19B are formed inside the body portion 11 with the end plate 18 interposed therebetween.
  • Displacer pistons 20A and 20B are disposed in the respective cylinder portions 19A and 19B.
  • the displacer piston 20A of one Stirling engine and the displacer piston 20B of the other Stirling engine are arranged to face each other.
  • Power pistons 21A and 21B are arranged coaxially in the axial direction of the displacer pistons 20A and 20B.
  • the power pistons 21A and 21B are disposed in the container end portions 12A and 12B.
  • Inner yokes 31A and 31B that reciprocate together with the power pistons 21A and 21B are fixed to the outer periphery of the power pistons 21A and 21B.
  • Inner yoke 31A, 31B is comprised by the cylindrical shape, and magnet 32A, 32B is fixed to the outer periphery.
  • Cylindrical outer yokes 33A and 33B are arranged on the outer periphery of the inner yokes 31A and 31B with a predetermined gap from the inner yokes 31A and 31B.
  • Coils 34A and 34B are fixed to the inner peripheral sides of the outer yokes 33A and 33B.
  • the coils 34A and 34B and the magnets 32A and 32B are arranged to face each other.
  • Linear generators 30A and 30B are configured by inner yokes 31A and 31B having magnets 32A and 32B and outer yokes 33A and 33B having coils 34A and 34B.
  • Regenerators 41A and 41B and coolers 42A and 42B are provided on the outer periphery of the displacer pistons 20A and 20B in the body portion 11.
  • the regenerators 41A and 41B and the coolers 42A and 42B are configured in a ring shape.
  • a cooling water inlet 15A and a cooling water outlet 16A are connected to the cooler 42A, and a cooling water inlet 15B and a cooling water outlet 16B are connected to the cooler 42B.
  • the expansion space 22A of the displacer piston 20A is formed by the cylinder portion 19A, the end plate 18, and the piston head of the displacer piston 20A.
  • the expansion space 22B of the displacer piston 20B is formed by the cylinder portion 19B, the end plate 18, and the piston head of the displacer piston 20B.
  • the end plate 18 can be omitted.
  • the expansion space 22A of one displacer piston 20A and the expansion space 22B of the other displacer piston 20B are a common expansion space.
  • the heat exchanger 50 is a ring-shaped central portion in the longitudinal direction of the body portion 11 and includes an outer peripheral portion on the piston head side of one displacer piston 20A and an outer peripheral portion on the piston head side of the other displacer piston 20B. Is arranged.
  • the coolers 42A and 42B are disposed at both ends of the trunk portion 11, and the regenerators 41A and 41B are disposed between the heat exchanger 50 and the coolers 42A and 42B.
  • the heat exchanger 50 includes one gas passage 51A that communicates with the expansion space 22A of one displacer piston 20A, the other gas passage 51B that communicates with the expansion space 22B of the other displacer piston 20B, one gas passage 51A, A heat medium passage 52 for heating the other gas passage 51B is formed.
  • the heat exchanger 50 is configured as a unit by connecting the one Stirling engine and the other Stirling engine by integrally configuring the one gas passage 51A and the other gas passage 51B. .
  • the heat exchanger 50 is arranged in a ring shape on the outer periphery of the one displacer piston 20A on the piston head side and on the outer periphery of the other displacer piston 20B on the piston head side, and the heat medium passage 52 is a pair of opposed ones.
  • the displacer pistons 20A and 20B are not arranged. Oil is used as the heat medium flowing through the heat medium passage 52. Further, when the exhaust heat temperature is high, a molten salt may be used as the heat medium.
  • One gas passage 51A communicates with one regenerator 41A, one regenerator 41A communicates with one cooler 42A, and one cooler 42A communicates with the compression space 23A of one displacer piston 20A.
  • the other gas passage 51B communicates with the other regenerator 41B, the other regenerator 41B communicates with the other cooler 42B, and the other cooler 42B communicates with the compression space 23B of the other displacer piston 20B.
  • One end of the rod is composed of large-diameter rods 24A and 24B, and the other end of the rod is composed of small-diameter rods 25A and 25B.
  • the large-diameter rods 24A and 24B are fixed to the displacer pistons 20A and 20B.
  • Container edge part 12A, 12B accommodates power piston 21A, 21B and linear generator 30A, 30B inside.
  • one Stirling engine is configured by the displacer piston 20A, the power piston 21A, the heat exchanger 50 as a heating unit, the regenerator 41A, and the cooler 42A, and the other Stirling engine is the displacer piston 20B, The power piston 21B, the heat exchanger 50 as a heating unit, a regenerator 41B, and a cooler 42B are included.
  • the enclosed gas expands by heating in the heat exchanger 50 and moves the displacer pistons 20A and 20B away from the end plate 18 (end portion direction).
  • the gas in the compression spaces 23A and 23B is compressed, and the power pistons 21A and 21B are moved in the end direction. Due to the movement of the power pistons 21A and 21B in the end direction, the gas passes from the expansion spaces 22A and 22B of the displacer pistons 20A and 20B through the heat exchanger 50, the regenerators 41A and 41B, and the coolers 42A and 42B.
  • the power pistons 21A and 21B move in the central direction when the compression spaces 23A and 23B become low pressure due to the movement of the displacer pistons 20A and 20B in the direction close to the end plate 18 (center direction). Due to the movement of the power pistons 21A and 21B toward the center, the gas in the compression spaces 23A and 23B passes through the coolers 42A and 42B, the regenerators 41A and 41B, and the heat exchanger 50, and enters the expansion spaces 22A and 22B. Moving.
  • the gas reciprocates between the expansion spaces 22A and 22B and the compression spaces 23A and 23B while performing expansion and contraction, thereby displacer piston 20A, While moving 20B, power piston 21A, 21B is moved. And electric power generation can be performed by movement of power piston 21A, 21B.
  • the pair of Stirling engines according to the present embodiment are preferably operated synchronously.
  • the heat absorption heat exchanger 60 is provided in the flue of the exhaust heat gas duct 71.
  • the heat-absorbing heat exchanger 60 is constituted by a double pipe shell, and a plurality of tubes 61 for flowing exhaust gas are provided in the double pipe shell.
  • the outer circumferential space 62 of the tube 61 serves as a heat medium passage, and the heat medium passage includes an inlet 63 and an outlet 64.
  • the outer diameter of the double pipe shell is larger than that of the exhaust heat gas duct 71, and the total cross sectional area of the tube 61 is larger than the cross sectional area of the exhaust heat gas duct 71. Is made smaller.
  • the introduction port 63 is arranged on the downstream side of the exhaust gas flow, and the outlet port 64 is arranged on the upstream side of the exhaust gas flow, so that the flow of the heat medium and the exhaust gas flow are opposed to each other.
  • the inlet 63 is connected to the heat medium outlet 14 shown in FIGS. 1 to 3 by piping, and the outlet 64 is connected to the heat medium inlet 13 shown in FIGS. 1 to 3 by piping. Is circulated through the heat-absorbing heat exchanger 60 and the heat exchanger 50.
  • FIGS. 6 is a cross-sectional view showing another heat absorption heat exchanger of the same electricity recovery engine
  • FIG. 7 is a cross-sectional view taken along line XX in FIG.
  • the heat absorption heat exchanger 80 is provided in the flue of the exhaust heat gas duct 71.
  • the heat-absorbing heat exchanger 80 is constituted by a double pipe shell, and an exhaust gas passage space is formed in the inner periphery of the double pipe shell, and fins 81 are provided in the exhaust gas passage space.
  • the fins 81 are constituted by a plurality of flat plates, and each flat plate is erected radially on the inner pipe with the pipe axis direction of the double pipe shell as the longitudinal direction.
  • a spiral heat medium passage 82 is formed on the outer periphery of the double tube shell. If the heat transfer area in the exhaust gas passage space is sufficient, the exhaust gas passage space may be formed by through holes without providing the fins 81.
  • the heat medium passage 82 includes an inlet 83 and an outlet 84.
  • the outer diameter of the double pipe shell is larger than that of the exhaust heat gas duct 71, and the total cross-sectional area of the exhaust gas flow path between the fins 81 is larger than the cross-sectional area of the exhaust heat gas duct 71, thereby passing through the heat absorption heat exchanger 80.
  • the flow resistance of exhaust gas is reduced.
  • the introduction port 83 is disposed on the downstream side of the exhaust gas flow, and the outlet port 84 is disposed on the upstream side of the exhaust gas flow, so that the flow of the heat medium and the exhaust gas flow are opposed to each other.
  • the inlet 83 is connected to the heat medium outlet 14 shown in FIGS. 1 to 3 through a pipe, and the outlet 84 is connected to the heat medium inlet 13 shown in FIGS. 1 to 3 through a pipe. Is circulated through the heat-absorbing heat exchanger 80 and the heat exchanger 50.
  • FIG. 8 is a conceptual configuration diagram of the electricity recovery engine according to the present embodiment
  • FIG. 9 is a perspective view of the main part of the electricity recovery engine.
  • the displacer piston 120A of one Stirling engine and the displacer piston 120B of the other Stirling engine are arranged to face each other, and in the axial direction of the displacer pistons 120A, 120B, a power piston 121A, 121B is arranged on the same axis.
  • Displacer pistons 120A and 120B are arranged in cylinder portions 119A and 119B.
  • Linear power generators 130A and 130B are attached to the power pistons 121A and 121B.
  • Regenerators 141A and 141B and coolers 142A and 142B are provided on the outer periphery of the displacer pistons 120A and 120B.
  • the regenerators 141A and 141B and the coolers 142A and 142B are configured in a ring shape.
  • Cooling water inlets 115A and 115B and cooling water outlets 116A and 116B are connected to the coolers 142A and 142B.
  • the expansion space 122A of the displacer piston 120A is formed by the cylinder portion 119A, the end plate 118A, and the piston head of the displacer piston 120A.
  • the expansion space 122B of the displacer piston 120B is formed by the cylinder portion 119B, the end plate 118B, and the piston head of the displacer piston 120B.
  • the heat exchanger 150 is disposed between the end plate 118A of one displacer piston 120A and the end plate 118B of the other displacer piston 120B.
  • the coolers 142A and 142B are disposed at the ends of the cylinder portions 119A and 119B, and the regenerators 141A and 141B are disposed between the heat exchanger 150 and the coolers 142A and 142B.
  • the heat exchanger 150 includes one gas passage 151A communicating with the expansion space 122A of one displacer piston 120A, the other gas passage 151B communicating with the expansion space 122B of the other displacer piston 120B, one gas passage 151A, and A heat medium passage 152 for heating the other gas passage 151B is formed.
  • the heat exchanger 150 is configured as a unit by connecting the one Stirling engine and the other Stirling engine by integrally configuring the one gas passage 151A and the other gas passage 151B.
  • the heat medium passage 152 may be installed in a factory, or may directly use an exhaust gas passage or a heat exhaust duct mounted on a vehicle.
  • the heat medium passage 152 has exhaust gas as a heat medium. Flowing.
  • the gas passages 151A and 151B are disposed between a pair of opposing displacer pistons 120A and 120B, and the flow direction of the gas flowing through the heat medium passage 152 is orthogonal to the axis of the displacer pistons 120A and 120B. The direction.
  • the gas passages 151 ⁇ / b> A and 151 ⁇ / b> B are disposed in the exhaust heat gas duct 171.
  • the gas passages 151A and 151B are constituted by a plurality of straight pipes, and the respective straight pipes are arranged in an arc shape.
  • one gas passage 151A communicates with the other regenerator 141B
  • the other regenerator 141B communicates with the other cooler 142B
  • the other cooler 142B is the other displacer piston. It communicates with the 120B compression space 123B.
  • control motors 180A and 180B are attached to the displacer pistons 120A and 120B, respectively, and the pair of Stirling engines are synchronously operated with a phase of 0 degrees by the control motors 180A and 180B.
  • the enclosed gas expands by heating in the heat exchanger 150 and moves the displacer pistons 120A and 120B away from the end plates 118A and 118B (end direction).
  • the gas in the compression space 123A is compressed, and the power piston 121A is moved in the end direction. Due to the movement of the power piston 121A toward the end, the gas in the expansion space 122B of the other displacer piston 120B passes through the heat exchanger 150, the regenerator 141A, and the cooler 142A, and the displacer piston 120A and the power piston 121A. It moves to the compression space 123A between.
  • the displacement of the compression space 123A by the movement of the displacer piston 120A in the direction (center direction) close to the end plate 118A causes the power piston 121A to move in the center direction.
  • the gas in one compression space 123A passes through the cooler 142A, the regenerator 141A, and the heat exchanger 150 and moves to the expansion space 122B of the other displacer piston 120B.
  • the gas in the compression space 123B is compressed by the movement of the other displacer piston 120B in the end direction, and the power piston 121B is moved in the end direction.
  • the gas in the expansion space 122A of one displacer piston 120A passes through the heat exchanger 150, the regenerator 141B, and the cooler 142B, and the displacer piston 120B and the power piston 121B. It moves to the compression space 123B between. Then, the displacement of the compression space 123B due to the movement of the displacer piston 120B in the center direction causes the power piston 121B to move in the center direction. By the movement of the power piston 121B toward the center, the gas in the other compression space 123B passes through the cooler 142B, the regenerator 141B, and the heat exchanger 150, and moves to the expansion space 122A of the one displacer piston 120A. .
  • the gas reciprocates between the expansion spaces 22A and 22B and the compression spaces 23A and 23B while performing expansion and contraction, thereby displacer piston 20A, While moving 20B, power piston 21A, 21B is moved. And electric power generation can be performed by movement of power piston 21A, 21B.
  • the gas led out from the expansion space 122A of one Stirling engine is led to the compression space 123B of the other Stirling engine facing the other Stirling engine without returning to the compression space 123A of the same Stirling engine.
  • the gas passage can have a low flow resistance, and the efficiency can be increased and the gas passages 151A and 151B can be configured by straight pipes. Therefore, the durability can be improved as compared with the case where there is a bent portion such as a U-shaped portion. Can be improved.
  • FIG. 10 to 12 are conceptual configuration diagrams of an electricity recovery engine according to different embodiments.
  • components having the same functions as those in FIG.
  • the reciprocating motion of the displacer pistons 120A and 120B is electrically generated from the power pistons 121A and 121B attached to the linear generators 130A and 130B.
  • the synchronous control part 190 which performs load control of the linear generators 130A and 130B is provided.
  • rotary generators 200A and 200B are provided via crank mechanisms 201A and 201B instead of the linear generators 130A and 130B in the embodiment shown in FIG.
  • displacer pistons 120A and 120B are connected to rotary generators 200A and 200B via crank mechanisms 201A and 201B instead of the control motors 180A and 180B in the embodiment shown in FIG.
  • a synchronous control unit 190 that performs load control of the rotary generators 200A and 200B is provided.
  • the electricity recovery engine according to the embodiment shown in FIG. 10 to FIG. 12 causes a pair of Stirling engines to operate synchronously at a phase of 0 degrees depending on the respective configurations.
  • the configuration for synchronous operation shown in FIGS. 8 and 9 and the configuration for synchronous operation shown in FIGS. 10 to 12 can be applied to the embodiments shown in FIGS. .
  • the electricity recovery engine communicates with one gas passage 51A, 151A communicating with the expansion spaces 22A, 122A of one displacer piston 20A, 120A and with expansion spaces 22B, 122B of the other displacer pistons 20B, 120B.
  • the heat exchangers 50 and 150 that form the other gas passages 51B and 151B, the one gas passages 51A and 151A, and the heat medium passages 52 and 152 that heat the other gas passages 51B and 151B are combined with one Stirling engine. Since the other Stirling engine is connected and unitized, a simple configuration can be obtained as compared with two separate Stirling engines.
  • the heat exchangers 50 and 150 can be arranged in the flue and the Stirling engine can be projected from the flue, so that the exhaust heat gas duct Good workability in flues.
  • the electricity recovery engine according to the present embodiment uses oil or molten salt as the heat medium flowing in the heat medium passage 52, so that sufficient heat recovery is possible even when the heat transfer area is small, particularly when using low-temperature exhaust heat. This can be done and the dead space of the heat exchanger can be reduced.
  • the heat exchanger 50 is arranged in a ring shape on the outer periphery of the one displacer piston 20A on the piston head side and on the outer periphery of the other displacer piston 20B on the piston head side.
  • the thermal efficiency can be increased.
  • the heat medium passage 52 is not disposed between the pair of opposing displacer pistons 20A and 20B, and the introduction port 13 for introducing the heat medium into the heat medium passage 52, and the heat medium passage.
  • the electricity recovery engine includes heat absorption heat exchangers 60 and 80 provided in the exhaust heat gas duct 71, and a pipe through which a heat medium circulates between the heat absorption heat exchangers 60 and 80 and the heat exchanger 50.
  • exhaust heat can be used with high thermal efficiency, and the Stirling engine can be constructed without being affected by the arrangement of the exhaust heat gas duct, so that the workability is good.
  • one gas passage 151A is communicated with the regenerator 141B of the other Stirling engine, and the other gas passage 151B is communicated with the regenerator 141A of one Stirling engine.
  • the gas passage 150 is disposed between a pair of opposing displacer pistons 120A and 120B, and the flow direction of the gas flowing through the heat medium passage 152 is orthogonal to the axis of the displacer pistons 120A and 120B.
  • the gas passages 151A and 151B are constituted by a plurality of straight pipes, and the respective straight pipes are arranged in a ring shape, so that the gas flow flowing through the flue such as the exhaust heat gas duct 171 can be prevented.
  • the pair of Stirling engines can be operated synchronously with a phase of 0 degrees, so that the vibration can be reduced by the synchronous operation of the pair of Stirling engines.
  • the electricity recovery engine according to the present embodiment is rotated by attaching linear generators 130A and 130B to the power pistons 120A and 120B, respectively, and attaching control motors 180A and 180B to the displacer pistons 120A and 120B, respectively.
  • the electric power generators 200A and 200B there is less transmission loss and highly efficient electricity recovery can be performed, and synchronization can be easily performed by the respective control motors.
  • one power generator 121A and one displacer piston 120A have one linear generator 130A attached, and the other power piston 121B and the other displacer piston 120B have the other linear generator 130B.
  • By attaching the linear generators 130A and 130B it is possible to perform highly efficient electricity recovery with less transmission loss compared to the rotary generators 200A and 200B, and keep the load of each linear generator constant. Thus, synchronization can be easily performed.
  • rotary power generators 200A and 200B are attached to the power pistons 121A and 121B, respectively, and control motors 180A and 180B are attached to the displacer pistons 120A and 120B, respectively.
  • one rotary generator 200A is attached to one power piston 121A and one displacer piston 120A
  • the other rotary power generator is attached to the other power piston 121B and the other displacer piston 120B.
  • the machine 200B is attached.
  • the phases of power pistons 121A and 121B and displacer pistons 120A and 120B are fixed, synchronization can be easily performed.
  • the electricity recovery engine of the present invention can be applied not only to factory exhaust heat but also to exhaust heat of engines such as automobiles and ships.

Abstract

Disclosed is an engine for electrical recovery characterized in that one Stirling engine and another Stirling engine are unitized by being coupled to each other, using a heat exchanger (50) comprised of one gas passage (51A) which communicates with an expansion space (22A) of one displacer piston (20A), another gas passage (51B) which communicates with an expansion space (22B) of the other displacer piston (20B), and a heat medium passage (52) which heats the gas passage (51A) and the gas passage (51B). In the engine for electrical recovery, even a low-temperature exhaust heat of around 200°C which has been exhausted from a flue of a factory can be efficiently converted into electric energy by a heat exchanger for a low-temperature exhaust heat having a sufficient heat-transfer performance.

Description

電気回収エンジンElectric recovery engine
　本発明は、スターリングエンジンを用いた電気回収エンジンに関する。 The present invention relates to an electricity recovery engine using a Stirling engine.
　現在、出力数ｋW～数十ｋWのスターリングエンジンの実用開発が欧州をはじめとした諸外国で活発に進められている。しかし、これらの装置は、高コストな熱交換器や低メンテナンス性などの問題により民生レベルで広く普及するには至っていない。
　また、国内においても、１９８０年代に国家プロジェクトとして『汎用スターリングエンジンの研究開発』が実施された。しかし、当時のスターリングエンジンは量産技術を活かしにくく、高コストな構造であったため、現在でもその研究成果が活用された製品は完成していないのが実情である。
　一方、スターリングエンジンは理論熱効率が高い外燃機関であり、省エネルギー技術の分野で有望視されている。
　既に、本発明者は、熱交換器での加熱温度を高くすることができ、この熱交換器における高温部と冷却器における低温部との連結による熱損失を抑えることで、熱効率に優れた高効率なスターリングエンジンを提案している（特許文献１）。
　また、本発明者は、ディスプレーサピストン、パワーピストン、板バネなどの部品の寸法や角度、平面度などのばらつきを緩和して低コストのスターリングエンジン（特許文献２）、冷却効率の高い冷却器（特許文献３）、摺動損失を低減し、信頼性の高いスコッチ・ヨーク機構を用いたスターリングエンジン（特許文献４）、小型で高性能なアクチュエータを適用できるスターリングエンジン（特許文献５）、スターリングエンジンの効率を上げるための高効率な熱交換器（特許文献６、７、８）を提案している。 Currently, practical development of Stirling engines with output of several kW to several tens of kW is being actively promoted in various countries including Europe. However, these devices have not been widely spread at the consumer level due to problems such as high-cost heat exchangers and low maintainability.
In Japan, “R & D of general-purpose Stirling engine” was implemented as a national project in the 1980s. However, since the Stirling engine at that time was difficult to make use of mass-production technology and was a high-cost structure, the actual situation is that a product utilizing the research results is not yet completed.
On the other hand, the Stirling engine is an external combustion engine with high theoretical thermal efficiency, and is considered promising in the field of energy saving technology.
Already, the present inventor can increase the heating temperature in the heat exchanger, and by suppressing the heat loss due to the connection between the high temperature part in this heat exchanger and the low temperature part in the cooler, the heat efficiency is high. An efficient Stirling engine has been proposed (Patent Document 1).
In addition, the present inventor has reduced the variation in dimensions, angles, flatness, etc. of parts such as a displacer piston, a power piston, and a leaf spring to reduce the cost of a Stirling engine (Patent Document 2), a cooler with high cooling efficiency ( Patent Document 3), Stirling Engine (Patent Document 4) using a highly reliable Scotch-Yoke mechanism with reduced sliding loss (Patent Document 4), Stirling Engine to which a small and high-performance actuator can be applied (Patent Document 5), Stirling Engine Have proposed high-efficiency heat exchangers (Patent Documents 6, 7, and 8) for increasing the efficiency of the heat exchanger.
特開２００５－１３３６５３号公報JP 2005-133653 A 特開２００５－１４７０６１号公報JP 2005-147061 A 特開２００７－２２４８５５号公報JP 2007-224855 A 特開２００８－１０１５０１号公報JP 2008-101501 A 特開２００９－４１４２６号公報JP 2009-41426 A 特開２００６－２８３６５８号公報JP 2006-283658 A 特開２００７－２７０７８９号公報JP 2007-270789 A 特開２００８－１４２１８号公報JP 2008-14218 A
　これまで大気中に捨てられてきた熱エネルギーを、電気エネルギーとして回収することは、省エネルギーに大きく貢献でき、利用価値も高い。特に、工場などの煙道から排出される熱は現在まで有効に利用できていない。
　しかし、工場から出る排熱の温度領域は、必ずしも高温ではなく、１００℃から３００℃程度の低温域であることも最も多い。
　低温排熱を用いるスターリングエンジンは、理論熱効率が低下し、高い発電出力を得ることは容易ではない。これは、理論熱効率が低くなるため、発電出力が低下する。そのため、低温排熱をエンジン内にできるだけ多くの熱エネルギーを取り込み、発電出力量を多くする必要がある。従って、低温排熱を用いるスターリングエンジンは、排熱と接する伝熱面積を、高温排熱を利用できる場合よりも非常に大きくとる必要がある。その結果、エンジン内の無効容積や流路抵抗が大きくなるために、出力低下となり、低温排熱からの電気回収を困難なものにしている。 Recovering thermal energy that has been discarded in the atmosphere as electrical energy can greatly contribute to energy saving and has high utility value. In particular, the heat exhausted from flues in factories and the like has not been effectively utilized until now.
However, the temperature range of exhaust heat from the factory is not necessarily high, but is most often a low temperature range of about 100 ° C to 300 ° C.
A Stirling engine using low-temperature exhaust heat has low theoretical thermal efficiency, and it is not easy to obtain a high power generation output. This is because the theoretical thermal efficiency is lowered, and the power generation output is reduced. Therefore, it is necessary to take in as much heat energy as possible from the low-temperature exhaust heat into the engine to increase the power generation output. Therefore, a Stirling engine using low-temperature exhaust heat needs to take a much larger heat transfer area in contact with the exhaust heat than when high-temperature exhaust heat can be used. As a result, the ineffective volume in the engine and the flow path resistance increase, resulting in a decrease in output, making it difficult to recover electricity from low-temperature exhaust heat.
　そこで本発明は、十分な伝熱性能を有する低温排熱用熱交換器により、工場などの煙道から排出される２００℃域の低温排熱からでも無効容積や通路抵抗が小さく効率よく電気エネルギーに変換できる電気回収エンジンを提供することを目的とする。 Therefore, the present invention is a low-temperature exhaust heat exchanger having sufficient heat transfer performance, which has a low ineffective volume and low passage resistance even from low-temperature exhaust heat in the 200 ° C region discharged from a flue of a factory or the like, and is efficient for electric energy. An object of the present invention is to provide an electricity recovery engine that can be converted into
　第１の発明による電気回収エンジンは、ディスプレーサピストンとパワーピストンとを同軸上に配置した一対のスターリングエンジンを備え、前記スターリングエンジンはそれぞれが再生器と冷却器とを有し、一方の前記スターリングエンジンの前記ディスプレーサピストンと、他方の前記スターリングエンジンの前記ディスプレーサピストンとを対向させて配置した電気回収エンジンであって、一方の前記ディスプレーサピストンの膨張空間と連通する一方のガス通路と、他方の前記ディスプレーサピストンの膨張空間と連通する他方のガス通路と、一方の前記ガス通路及び他方の前記ガス通路を加熱する熱媒体通路とを形成する熱交換器によって、一方の前記スターリングエンジンと他方の前記スターリングエンジンとを連結してユニット化したことを特徴とする。
　第２の発明は、第１の発明に記載の電気回収エンジンにおいて、前記熱媒体通路を流れる熱媒体としてオイル又は溶融塩を用いたことを特徴とする。
　第３の発明は、第２の発明に記載の電気回収エンジンにおいて、前記熱交換器を、一方の前記ディスプレーサピストンのピストンヘッド側の外周部と、他方の前記ディスプレーサピストンのピストンヘッド側の外周部とに、リング状に配置したことを特徴とする。
　第４の発明は、第３の発明に記載の電気回収エンジンにおいて、前記熱媒体通路に前記熱媒体を導入する導入口と、前記熱媒体通路から前記熱媒体を導出する導出口とを前記熱交換器の外周面に配置し、前記熱媒体通路を、対向する一対の前記ディスプレーサピストンの間には配置しないことを特徴とする。
　第５の発明は、第２の発明に記載の電気回収エンジンにおいて、排熱ガスダクトに設けた吸熱用熱交換器と、前記吸熱用熱交換器と前記熱交換器とを前記熱媒体が循環する配管とを設けたことを特徴とする。
　第６の発明は、第１の発明に記載の電気回収エンジンにおいて、一方の前記ガス通路を、他方の前記スターリングエンジンの前記再生器と連通させ、他方の前記ガス通路を、一方の前記スターリングエンジンの前記再生器と連通させたことを特徴とする。
　第７の発明は、第６の発明に記載の電気回収エンジンにおいて、前記ガス通路を、対向する一対の前記ディスプレーサピストンの間に配置し、前記熱媒体通路を流れるガスの流れ方向を、前記ディスプレーサピストンの軸に直交する方向としたことを特徴とする。
　第８の発明は、第６の発明に記載の電気回収エンジンにおいて、前記ガス通路を、複数の直管で構成し、それぞれの前記直管を円弧状に配置したことを特徴とする。
　第９の発明は、第１の発明に記載の電気回収エンジンにおいて、一対の前記スターリングエンジンを０度の位相で同期運転させることを特徴とする。
　第１０の発明は、第９の発明に記載の電気回収エンジンにおいて、それぞれの前記パワーピストンにはそれぞれリニア発電機を取り付け、それぞれの前記ディスプレーサピストンにはそれぞれ制御モータを取り付けたことを特徴とする。
　第１１の発明は、第９の発明に記載の電気回収エンジンにおいて、一方の前記パワーピストン及び一方の前記ディスプレーサピストンには一方のリニア発電機を取り付け、他方の前記パワーピストン及び他方の前記ディスプレーサピストンには他方のリニア発電機を取り付けたことを特徴とする。
　第１２の発明は、第９の発明に記載の電気回収エンジンにおいて、それぞれの前記パワーピストンにはそれぞれ回転式発電機を取り付け、それぞれの前記ディスプレーサピストンにはそれぞれ制御モータを取り付けたことを特徴とする。
　第１３の発明は、第９の発明に記載の電気回収エンジンにおいて、一方の前記パワーピストン及び一方の前記ディスプレーサピストンには一方の回転式発電機を取り付け、他方の前記パワーピストン及び他方の前記ディスプレーサピストンには他方の回転式発電機を取り付けたことを特徴とする。 An electricity recovery engine according to a first aspect of the present invention includes a pair of Stirling engines in which a displacer piston and a power piston are coaxially arranged. Each of the Stirling engines has a regenerator and a cooler, and the one Stirling engine is provided. The displacer piston of the other Stirling engine and the displacer piston of the other Stirling engine are arranged to face each other, wherein the displacer piston has one gas passage communicating with the expansion space of the one displacer piston, and the other displacer. One Stirling engine and the other Stirling engine are formed by a heat exchanger that forms the other gas passage communicating with the expansion space of the piston and the heat medium passage for heating the one gas passage and the other gas passage. And Characterized in that the phased.
According to a second aspect of the invention, in the electricity recovery engine according to the first aspect of the invention, oil or molten salt is used as the heat medium flowing through the heat medium passage.
According to a third aspect of the present invention, in the electricity recovery engine according to the second aspect of the invention, the heat exchanger includes an outer peripheral portion on the piston head side of the one displacer piston and an outer peripheral portion on the piston head side of the other displacer piston. And arranged in a ring shape.
According to a fourth aspect of the present invention, in the electricity recovery engine according to the third aspect of the present invention, an inlet for introducing the heat medium into the heat medium passage and an outlet for deriving the heat medium from the heat medium passage are provided in the heat recovery passage. It arrange | positions on the outer peripheral surface of an exchanger, The said heat-medium channel | path is not arrange | positioned between a pair of said displacer pistons which oppose, It is characterized by the above-mentioned.
According to a fifth aspect of the present invention, in the electricity recovery engine according to the second aspect, the heat medium circulates through the heat absorption heat exchanger provided in the exhaust heat gas duct, the heat absorption heat exchanger, and the heat exchanger. A pipe is provided.
A sixth invention is the electricity recovery engine according to the first invention, wherein one gas passage is communicated with the regenerator of the other Stirling engine, and the other gas passage is connected to one Stirling engine. The regenerator is communicated with each other.
According to a seventh aspect of the present invention, in the electricity recovery engine according to the sixth aspect of the invention, the gas passage is disposed between a pair of opposing displacer pistons, and the flow direction of the gas flowing through the heat medium passage is determined by the displacer. The direction is perpendicular to the axis of the piston.
According to an eighth aspect of the present invention, in the electricity recovery engine according to the sixth aspect, the gas passage is constituted by a plurality of straight pipes, and the straight pipes are arranged in an arc shape.
According to a ninth invention, in the electricity recovery engine according to the first invention, the pair of Stirling engines are operated synchronously at a phase of 0 degrees.
According to a tenth aspect of the present invention, in the electricity recovery engine according to the ninth aspect, a linear generator is attached to each of the power pistons, and a control motor is attached to each of the displacer pistons. .
An eleventh invention is the electricity recovery engine according to the ninth invention, wherein one power generator and one displacer piston are attached to one linear generator, the other power piston and the other displacer piston. Is characterized in that the other linear generator is attached.
A twelfth invention is characterized in that, in the electricity recovery engine according to the ninth invention, a rotary generator is attached to each of the power pistons, and a control motor is attached to each of the displacer pistons. To do.
A thirteenth aspect of the invention is the electricity recovery engine according to the ninth aspect of the invention, wherein one rotary generator is attached to the one power piston and the one displacer piston, and the other power piston and the other displacer. The piston is equipped with the other rotary generator.
　本発明は、一対のスターリングエンジンを対向配置することで、一層シンプルで高性能な構造となり、未利用な低温排熱からの電気回収を実現できる電気回収エンジンを提供することができる。
　また、本発明は、低温排熱を利用する場合でも、無効容積や通路抵抗を小さくでき、そのため、効率よく電気エネルギーに変換できる電気回収エンジンを提供することができる。 According to the present invention, by arranging a pair of Stirling engines to face each other, it is possible to provide an electric recovery engine that has a simpler and higher performance structure and can realize electric recovery from unused low-temperature exhaust heat.
In addition, the present invention can provide an electric recovery engine that can reduce the ineffective volume and passage resistance even when using low-temperature exhaust heat, and can therefore be efficiently converted into electric energy.
図１は本発明の一実施例による電気回収エンジンの外観斜視図である。FIG. 1 is an external perspective view of an electricity recovery engine according to an embodiment of the present invention. 図２は同電気回収エンジンの要部断面斜視図である。FIG. 2 is a cross-sectional perspective view of the main part of the electricity recovery engine. 図３は同電気回収エンジンの断面図である。FIG. 3 is a sectional view of the electricity recovery engine. 図４は同電気回収エンジンの吸熱用熱交換器を示す断面図である。FIG. 4 is a cross-sectional view showing an endothermic heat exchanger of the electricity recovery engine. 図５は図４におけるＸ－Ｘ線による断面図である。FIG. 5 is a sectional view taken along line XX in FIG. 図６は本実施例による電気回収エンジンの他の吸熱用熱交換器を示す断面図である。FIG. 6 is a cross-sectional view showing another heat absorption heat exchanger of the electricity recovery engine according to this embodiment. 図７は図６におけるＸ－Ｘ線による断面図である。FIG. 7 is a sectional view taken along line XX in FIG. 図８は本発明の他の実施例による電気回収エンジンの概念構成図である。FIG. 8 is a conceptual configuration diagram of an electricity recovery engine according to another embodiment of the present invention. 図９は同電気回収エンジンの外観要部斜視図である。FIG. 9 is a perspective view of an essential part of the electricity recovery engine. 図１０は本発明の更に他の実施例による電気回収エンジンの概念構成図である。FIG. 10 is a conceptual configuration diagram of an electricity recovery engine according to still another embodiment of the present invention. 図１１は本発明の更に他の実施例による電気回収エンジンの概念構成図である。FIG. 11 is a conceptual configuration diagram of an electricity recovery engine according to still another embodiment of the present invention. 図１２は本発明の更に他の実施例による電気回収エンジンの概念構成図である。FIG. 12 is a conceptual configuration diagram of an electricity recovery engine according to still another embodiment of the present invention.
　　２０Ａ、２０Ｂ　ディスプレーサピストン
　　２１Ａ、２１Ｂ　パワーピストン
　　２２Ａ、２２Ｂ　膨脹空間
　　３０Ａ、３０Ｂ　リニア発電機
　　４１Ａ、４１Ｂ　再生器
　　４２Ａ、４２Ｂ　冷却器
　　５０　熱交換器
　１２０Ａ、１２０Ｂ　ディスプレーサピストン
　１２１Ａ、１２１Ｂ　パワーピストン
　１２２Ａ、１２２Ｂ　膨脹空間
　１３０Ａ、１３０Ｂ　リニア発電機
　１４１Ａ、１４１Ｂ　再生器
　１４２Ａ、１４２Ｂ　冷却器
　１５０　熱交換器
　１８０Ａ、１８０Ｂ　制御モータ
　１９０　同期制御部
　２００Ａ、２００Ｂ　回転式発電機 20A, 20B Displacer piston 21A, 21B Power piston 22A, 22B Expansion space 30A, 30B Linear generator 41A, 41B Regenerator 42A, 42B Cooler 50 Heat exchanger 120A, 120B Displacer piston 121A, 121B Power piston 122A, 122B Expansion space 130A, 130B linear generator 141A, 141B regenerator 142A, 142B cooler 150 heat exchanger 180A, 180B control motor 190 synchronous control unit 200A, 200B rotary generator
　本発明の第１の実施の形態による電気回収エンジンは、一方のディスプレーサピストンの膨張空間と連通する一方のガス通路と、他方のディスプレーサピストンの膨張空間と連通する他方のガス通路と、一方のガス通路及び他方のガス通路を加熱する熱媒体通路とを形成する熱交換器によって、一方のスターリングエンジンと他方のスターリングエンジンとを連結してユニット化したものである。本実施の形態によれば、一対のスターリングエンジンを対向させ、それぞれのスターリングエンジンに必要な熱交換器を一つの熱交換器で構成し、この熱交換器によって一対のスターリングエンジンを連結することで、２つの別々のスターリングエンジンと比較してシンプルな構成とすることができる。また、熱交換器の両側にスターリングエンジンが配置されるため、例えば、熱交換器を煙道中に配置してスターリングエンジンを煙道から突出させて施工できるため、排熱ガスダクトなどの煙道への施工性が良い。
　本発明の第２の実施の形態は、第１の実施の形態による電気回収エンジンにおいて、熱媒体通路に流れる熱媒体としてオイル又は溶融塩を用いたものである。本実施の形態によれば、オイル又は溶融塩を熱媒体として用いることで、特に低温排熱を利用する場合に、伝熱面積が小さくても十分な熱回収を行うことができ、熱交換器のデッドスペース、すなわち無効容積を少なくすることができる。そのため、圧力変化を高めることができ、図示動力を高め、発電出力を高めることができる。また、低温排熱の熱エネルギーを一旦、熱媒体に蓄熱するロスを熱伝導性のよい材料（ＳｉＣや銅材料等）で熱交換器を構成することで、熱交換器損失を小さくでき、熱媒体を使った熱交換器損失をカバーすることができるため、効率のよい電気回収エンジンを実現できる。
本発明の第３の実施の形態は、第２の実施の形態による電気回収エンジンにおいて、熱交換器を、一方のディスプレーサピストンのピストンヘッド側の外周部と、他方のディスプレーサピストンのピストンヘッド側の外周部とに、リング状に配置したものである。本実施の形態によれば、ディスプレーサピストンの膨張空間外周を加熱できるので熱効率を高めることができる。
　本発明の第４の実施の形態は、第３の実施の形態による電気回収エンジンにおいて、熱媒体通路に熱媒体を導入する導入口と、熱媒体通路から熱媒体を導出する導出口とを熱交換器の外周面に配置し、熱媒体通路を、対向する一対のディスプレーサピストンの間には配置しないものである。本実施の形態によれば、オイル又は溶融塩を用いた小型の熱交換器をピストンヘッド間ではなくピストンヘッド外周だけに配置することで、ディスプレーサピストンの軸方向の長さを短くできる。
　本発明の第５の実施の形態は、第２の実施の形態による電気回収エンジンにおいて、排熱ガスダクトに設けた吸熱用熱交換器と、吸熱用熱交換器と熱交換器とを熱媒体が循環する配管とを設けたものである。本実施の形態によれば、オイル又は溶融塩を熱媒体として排熱ガスダクトの熱をスターリングエンジンに搬送するため、高い熱効率で排熱を利用することができる。また、スターリングエンジンを排熱ガスダクトの配置に影響されずに施工できるために、施工性が良い。したがって、排気ガスダクトをエンジン設置が困難な高所や狭所の場所でも、レイアウトの自由度を高め、様々な排熱源に対応することができる。
　本発明の第６の実施の形態は、第１の実施の形態による電気回収エンジンにおいて、一方のガス通路を、他方のスターリングエンジンの再生器と連通させ、他方のガス通路を、一方のスターリングエンジンの再生器と連通させたものである。本実施の形態によれば、一方のスターリングエンジンの膨張空間から導出させたガスを同じスターリングエンジンの再生器に戻すことなく、対向する他方のスターリングエンジンの再生器に導き、他方のスターリングエンジンの膨張空間から導出させたガスを同じスターリングエンジンの再生器に戻すことなく、対向する一方のスターリングエンジンの再生器に導くため、例えばガス通路をＵ字状に曲げる必要が無く、流路抵抗の少ないガス通路とすることができるため、圧力損失を低減し、効率を高めることができる。さらに、Ｕ字部のような曲げ部分がある場合と比較して、減肉することもなく、信頼性を高める。さらに、腐食性のガスに対して、溶射（金属、セラミックス）並びにコーティングをガス通路材料に施した場合でも、曲げ部がないことから、耐腐食性膜とガス通路材料との密着強度を高め、耐久性を向上させることができる。
　本発明の第７の実施の形態は、第６の実施の形態による電気回収エンジンにおいて、ガス通路を、対向する一対のディスプレーサピストンの間に配置し、熱媒体通路を流れるガスの流れ方向を、ディスプレーサピストンの軸に直交する方向としたものである。本実施の形態によれば、排熱ガスダクトのような煙道に施工した場合に、煙道を流れるガスの排熱を効率よく回収することができる。
　本発明の第８の実施の形態は、第６の実施の形態による電気回収エンジンにおいてガス通路を、複数の直管で構成し、それぞれの直管を円弧状に配置したものである。本実施の形態によれば、排熱ガスダクトのような煙道を流れるガス流に対する抵抗を小さくでき、効率よく熱回収を行うことができる。
　本発明の第９の実施の形態は、第１の実施の形態による電気回収エンジンにおいて、一対のスターリングエンジンを０度の位相で同期運転させるものである。本実施の形態によれば、一対のスターリングエンジンの同期運転によって低振動化を図ることができる。
　本発明の第１０の実施の形態は、第９の実施の形態による電気回収エンジンにおいて、それぞれのパワーピストンにはそれぞれリニア発電機を取り付け、それぞれのディスプレーサピストンにはそれぞれ制御モータを取り付けたものである。本実施の形態によれば、リニア発電機を用いることで回転式発電機と比較して伝達ロスが少なく高効率な電気回収が行えるとともに、それぞれの制御モータによって同期を容易に行うことができる。
　本発明の第１１の実施の形態は、第９の実施の形態による電気回収エンジンにおいて、一方のパワーピストン及び一方のディスプレーサピストンには一方のリニア発電機を取り付け、他方のパワーピストン及び他方のディスプレーサピストンには他方のリニア発電機を取り付けたものである。本実施の形態によれば、リニア発電機を用いることで回転式発電機と比較して伝達ロスが少なく高効率な電気回収が行えるとともに、それぞれのリニア発電機の負荷を一定に保つことで同期を容易に行うことができる。
　本発明の第１２の実施の形態は、第９の実施の形態による電気回収エンジンにおいて、それぞれのパワーピストンにはそれぞれ回転式発電機を取り付け、それぞれのディスプレーサピストンにはそれぞれ制御モータを取り付けたものである。本実施の形態によれば、パワーピストンとディスプレーサピストンとの位相が固定されているので同期を容易に行うことができる。
　本発明の第１３の実施の形態は、第９の実施の形態による電気回収エンジンにおいて、一方のパワーピストン及び一方のディスプレーサピストンには一方の回転式発電機を取り付け、他方のパワーピストン及び他方のディスプレーサピストンには他方の回転式発電機を取り付けたものである。本実施の形態によれば、パワーピストンとディスプレーサピストンとの位相が固定されているので同期を容易に行うことができる。 The electricity recovery engine according to the first embodiment of the present invention includes one gas passage communicating with the expansion space of one displacer piston, the other gas passage communicating with the expansion space of the other displacer piston, and one gas. One Stirling engine and the other Stirling engine are connected and unitized by a heat exchanger that forms a passage and a heat medium passage for heating the other gas passage. According to the present embodiment, a pair of Stirling engines are opposed to each other, a heat exchanger necessary for each Stirling engine is configured by one heat exchanger, and the pair of Stirling engines are connected by this heat exchanger. Compared to two separate Stirling engines, a simple configuration can be achieved. In addition, since the Stirling engine is arranged on both sides of the heat exchanger, for example, the heat exchanger can be placed in the flue and the Stirling engine can be projected from the flue so that it can be connected to the flue such as the exhaust heat gas duct. Good workability.
The second embodiment of the present invention uses oil or molten salt as a heat medium flowing in the heat medium passage in the electricity recovery engine according to the first embodiment. According to the present embodiment, by using oil or molten salt as a heat medium, sufficient heat recovery can be performed even when the heat transfer area is small, particularly when using low-temperature exhaust heat, and the heat exchanger The dead space, that is, the ineffective volume can be reduced. Therefore, the pressure change can be increased, the illustrated power can be increased, and the power generation output can be increased. In addition, by configuring the heat exchanger with a material with good thermal conductivity (SiC, copper material, etc.) once the heat energy of the low-temperature exhaust heat is stored in the heat medium, the heat exchanger loss can be reduced, Since the heat exchanger loss using the medium can be covered, an efficient electricity recovery engine can be realized.
According to a third embodiment of the present invention, in the electricity recovery engine according to the second embodiment, the heat exchanger is arranged on the piston head side outer peripheral portion of one displacer piston and on the piston head side of the other displacer piston. It is arranged in a ring shape on the outer periphery. According to the present embodiment, since the outer periphery of the expansion space of the displacer piston can be heated, the thermal efficiency can be increased.
According to a fourth embodiment of the present invention, in the electricity recovery engine according to the third embodiment, an inlet for introducing the heat medium into the heat medium passage and an outlet for deriving the heat medium from the heat medium passage are heated. It arrange | positions at the outer peripheral surface of an exchanger, and does not arrange | position a heat-medium channel | path between a pair of displacer pistons which oppose. According to the present embodiment, by disposing a small heat exchanger using oil or molten salt only on the outer periphery of the piston head, not between the piston heads, the axial length of the displacer piston can be shortened.
According to a fifth embodiment of the present invention, in the electricity recovery engine according to the second embodiment, the heat medium includes an endothermic heat exchanger provided in the exhaust heat gas duct, an endothermic heat exchanger, and the heat exchanger. Circulating piping is provided. According to the present embodiment, the heat of the exhaust heat gas duct is conveyed to the Stirling engine using oil or molten salt as a heat medium, so that the exhaust heat can be utilized with high thermal efficiency. Further, since the Stirling engine can be constructed without being affected by the arrangement of the exhaust heat gas duct, the workability is good. Therefore, it is possible to increase the degree of freedom in layout and cope with various exhaust heat sources even in high places and narrow places where it is difficult to install the exhaust gas duct.
According to a sixth embodiment of the present invention, in the electricity recovery engine according to the first embodiment, one gas passage is communicated with a regenerator of the other Stirling engine, and the other gas passage is connected to one Stirling engine. In communication with the regenerator. According to the present embodiment, the gas derived from the expansion space of one Stirling engine is led to the regenerator of the opposite Stirling engine without returning the gas to the regenerator of the same Stirling engine, and the expansion of the other Stirling engine is performed. Since the gas led out from the space is led to the regenerator of the opposite Stirling engine without returning it to the regenerator of the same Stirling engine, for example, it is not necessary to bend the gas passage into a U-shape and the gas has low flow resistance Since it can be a passage, pressure loss can be reduced and efficiency can be increased. Furthermore, compared with the case where there exists a bending part like a U-shaped part, reliability is improved, without thinning. Furthermore, even when thermal spraying (metal, ceramics) and coating are applied to the corrosive gas, since there is no bend, the adhesion strength between the corrosion-resistant film and the gas passage material is increased, Durability can be improved.
According to a seventh embodiment of the present invention, in the electricity recovery engine according to the sixth embodiment, the gas passage is disposed between a pair of opposing displacer pistons, and the flow direction of the gas flowing through the heat medium passage is determined. The direction is perpendicular to the axis of the displacer piston. According to this Embodiment, when it constructs in a flue like an exhaust heat gas duct, the exhaust heat of the gas which flows through a flue can be collect | recovered efficiently.
In the eighth embodiment of the present invention, in the electricity recovery engine according to the sixth embodiment, the gas passage is constituted by a plurality of straight pipes, and the respective straight pipes are arranged in an arc shape. According to the present embodiment, resistance to a gas flow flowing through a flue such as an exhaust heat gas duct can be reduced, and heat can be recovered efficiently.
In the ninth embodiment of the present invention, in the electricity recovery engine according to the first embodiment, a pair of Stirling engines are operated synchronously with a phase of 0 degrees. According to the present embodiment, the vibration can be reduced by the synchronous operation of the pair of Stirling engines.
According to a tenth embodiment of the present invention, in the electricity recovery engine according to the ninth embodiment, a linear generator is attached to each power piston, and a control motor is attached to each displacer piston. is there. According to the present embodiment, by using a linear generator, it is possible to perform highly efficient electricity recovery with less transmission loss compared to a rotary generator, and synchronization can be easily performed by each control motor.
According to an eleventh embodiment of the present invention, in the electricity recovery engine according to the ninth embodiment, one power generator and one displacer piston are attached with one linear generator, and the other power piston and the other displacer. The other linear generator is attached to the piston. According to the present embodiment, by using a linear generator, it is possible to perform highly efficient electricity recovery with less transmission loss compared to a rotary generator and to keep the load of each linear generator constant. Can be easily performed.
In the twelfth embodiment of the present invention, in the electricity recovery engine according to the ninth embodiment, a rotary generator is attached to each power piston, and a control motor is attached to each displacer piston. It is. According to this embodiment, since the phases of the power piston and the displacer piston are fixed, synchronization can be easily performed.
In a thirteenth embodiment of the present invention, in the electricity recovery engine according to the ninth embodiment, one power generator and one displacer piston are attached with one rotary generator, the other power piston and the other power piston. The displacer piston is provided with the other rotary generator. According to this embodiment, since the phases of the power piston and the displacer piston are fixed, synchronization can be easily performed.
　以下本発明の一実施例による電気回収エンジンについて図面とともに説明する。
　図１は本実施例による電気回収エンジンの外観斜視図、図２は同電気回収エンジンの要部断面斜視図、図３は同電気回収エンジンの断面図、図４は同電気回収エンジンの吸熱用熱交換器を示す断面図、図５は図４におけるＸ－Ｘ線による断面図である。
　図１に示すように、本実施例による電気回収エンジンの密閉容器１０は、円筒形状の胴部１１と、胴部１１の両端に配置された容器端部１２Ａ、１２Ｂとで構成されている。ここで容器端部１２Ａ、１２Ｂは、胴部１１よりも大きな径の円筒形状で構成されている。
　胴部１１の長手方向の中央部外周面には、熱媒体を導入する熱媒体導入口１３と、熱媒体を導出する熱媒体導出口１４とが取り付けられている。
　また、胴部１１の両端部外周面には、それぞれ冷却水を導入する冷却水導入口１５Ａ、１５Ｂと、冷却水を導出する冷却水導出口１６Ａ、１６Ｂが取り付けられている。
　それぞれの容器端部１２Ａ、１２Ｂには、容器端部１２Ａ、１２Ｂ内部に配置されるリニア発電機用配線を取り出す配線接続部１７Ａ、１７Ｂを設けている。 Hereinafter, an electricity recovery engine according to an embodiment of the present invention will be described with reference to the drawings.
FIG. 1 is an external perspective view of the electricity recovery engine according to the present embodiment, FIG. 2 is a cross-sectional perspective view of the main part of the electricity recovery engine, FIG. 3 is a sectional view of the electricity recovery engine, and FIG. FIG. 5 is a sectional view showing the heat exchanger, and FIG. 5 is a sectional view taken along line XX in FIG.
As shown in FIG. 1, the sealed container 10 of the electricity recovery engine according to the present embodiment includes a cylindrical body 11 and container ends 12 </ b> A and 12 </ b> B disposed at both ends of the body 11. Here, the container end portions 12 </ b> A and 12 </ b> B are formed in a cylindrical shape having a larger diameter than the body portion 11.
A heat medium introduction port 13 for introducing the heat medium and a heat medium outlet port 14 for deriving the heat medium are attached to the outer peripheral surface of the central portion in the longitudinal direction of the body 11.
Further, cooling water inlets 15A and 15B for introducing cooling water and cooling water outlets 16A and 16B for leading cooling water are attached to the outer peripheral surfaces of both ends of the body portion 11, respectively.
The respective container end portions 12A and 12B are provided with wiring connection portions 17A and 17B for taking out the wiring for the linear generator arranged inside the container end portions 12A and 12B.
　次に、本実施例による電気回収エンジンの内部構成について、図２及び図３を用いて説明する。
　胴部１１の長手方向の中央部は端板１８で区切られ（図２では端板１８は省略）、胴部１１内部には、この端板１８を挟んで一対のシリンダ部１９Ａ、１９Ｂが形成されている。
　それぞれのシリンダ部１９Ａ、１９Ｂ内には、ディスプレーサピストン２０Ａ、２０Ｂが配置されている。
　本実施例による電気回収エンジンは、一方のスターリングエンジンのディスプレーサピストン２０Ａと、他方のスターリングエンジンのディスプレーサピストン２０Ｂとを対向させて配置している。
　ディスプレーサピストン２０Ａ、２０Ｂの軸方向にはパワーピストン２１Ａ、２１Ｂが同軸上に配置されている。パワーピストン２１Ａ、２１Ｂは容器端部１２Ａ、１２Ｂ内に配置されている。
　パワーピストン２１Ａ、２１Ｂの外周には、パワーピストン２１Ａ、２１Ｂとともに往復動作するインナーヨーク３１Ａ、３１Ｂが固定されている。インナーヨーク３１Ａ、３１Ｂは、円筒状に構成され、その外周には磁石３２Ａ、３２Ｂが固定される。
　インナーヨーク３１Ａ、３１Ｂの外周部には、円筒状のアウターヨーク３３Ａ、３３Ｂがインナーヨーク３１Ａ、３１Ｂと所定のギャップを持って配置される。アウターヨーク３３Ａ、３３Ｂの内周側にはコイル３４Ａ、３４Ｂが固定されている。コイル３４Ａ、３４Ｂと磁石３２Ａ、３２Ｂとは対向して配置されている。磁石３２Ａ、３２Ｂを有するインナーヨーク３１Ａ、３１Ｂと、コイル３４Ａ、３４Ｂを有するアウターヨーク３３Ａ、３３Ｂによってリニア発電機３０Ａ、３０Ｂが構成される。
　胴部１１内の、ディスプレーサピストン２０Ａ、２０Ｂの外周部には、再生器４１Ａ、４１Ｂ及び冷却器４２Ａ、４２Ｂを備えている。再生器４１Ａ、４１Ｂ及び冷却器４２Ａ、４２Ｂは、リング状に構成されている。冷却器４２Ａには、冷却水導入口１５Ａと冷却水導出口１６Ａが接続され、冷却器４２Ｂには、冷却水導入口１５Ｂと冷却水導出口１６Ｂが接続されている。
　ディスプレーサピストン２０Ａの膨脹空間２２Ａは、シリンダ部１９Ａ、端板１８、及びディスプレーサピストン２０Ａのピストンヘッドによって形成している。また、ディスプレーサピストン２０Ｂの膨脹空間２２Ｂは、シリンダ部１９Ｂ、端板１８、及びディスプレーサピストン２０Ｂのピストンヘッドによって形成している。
　なお、一対のスターリングエンジンを同期運転させる場合には、端板１８を設けずに構成することもできる。この場合には、一方のディスプレーサピストン２０Ａの膨脹空間２２Ａと、他方のディスプレーサピストン２０Ｂの膨脹空間２２Ｂとは共通の膨張空間となる。 Next, the internal configuration of the electricity recovery engine according to this embodiment will be described with reference to FIGS.
A central portion in the longitudinal direction of the body portion 11 is divided by an end plate 18 (the end plate 18 is omitted in FIG. 2), and a pair of cylinder portions 19A and 19B are formed inside the body portion 11 with the end plate 18 interposed therebetween. Has been.
Displacer pistons 20A and 20B are disposed in the respective cylinder portions 19A and 19B.
In the electricity recovery engine according to the present embodiment, the displacer piston 20A of one Stirling engine and the displacer piston 20B of the other Stirling engine are arranged to face each other.
Power pistons 21A and 21B are arranged coaxially in the axial direction of the displacer pistons 20A and 20B. The power pistons 21A and 21B are disposed in the container end portions 12A and 12B.
Inner yokes 31A and 31B that reciprocate together with the power pistons 21A and 21B are fixed to the outer periphery of the power pistons 21A and 21B. Inner yoke 31A, 31B is comprised by the cylindrical shape, and magnet 32A, 32B is fixed to the outer periphery.
Cylindrical outer yokes 33A and 33B are arranged on the outer periphery of the inner yokes 31A and 31B with a predetermined gap from the inner yokes 31A and 31B. Coils 34A and 34B are fixed to the inner peripheral sides of the outer yokes 33A and 33B. The coils 34A and 34B and the magnets 32A and 32B are arranged to face each other. Linear generators 30A and 30B are configured by inner yokes 31A and 31B having magnets 32A and 32B and outer yokes 33A and 33B having coils 34A and 34B.
Regenerators 41A and 41B and coolers 42A and 42B are provided on the outer periphery of the displacer pistons 20A and 20B in the body portion 11. The regenerators 41A and 41B and the coolers 42A and 42B are configured in a ring shape. A cooling water inlet 15A and a cooling water outlet 16A are connected to the cooler 42A, and a cooling water inlet 15B and a cooling water outlet 16B are connected to the cooler 42B.
The expansion space 22A of the displacer piston 20A is formed by the cylinder portion 19A, the end plate 18, and the piston head of the displacer piston 20A. The expansion space 22B of the displacer piston 20B is formed by the cylinder portion 19B, the end plate 18, and the piston head of the displacer piston 20B.
When the pair of Stirling engines are operated synchronously, the end plate 18 can be omitted. In this case, the expansion space 22A of one displacer piston 20A and the expansion space 22B of the other displacer piston 20B are a common expansion space.
　熱交換器５０は、胴部１１の長手方向の中央部であって、一方のディスプレーサピストン２０Ａのピストンヘッド側の外周部と、他方のディスプレーサピストン２０Ｂのピストンヘッド側の外周部とに、リング状に配置している。冷却器４２Ａ、４２Ｂは、胴部１１の両端に配置し、再生器４１Ａ、４１Ｂは熱交換器５０と冷却器４２Ａ、４２Ｂとの間に配置している。
　熱交換器５０は、一方のディスプレーサピストン２０Ａの膨張空間２２Ａと連通する一方のガス通路５１Ａと、他方のディスプレーサピストン２０Ｂの膨張空間２２Ｂと連通する他方のガス通路５１Ｂと、一方のガス通路５１Ａ及び他方のガス通路５１Ｂを加熱する熱媒体通路５２とを形成している。このように熱交換器５０は、一方のガス通路５１Ａと他方のガス通路５１Ｂとを一体に構成することで、一方のスターリングエンジンと他方のスターリングエンジンとを連結しており、ユニット化されている。
　熱交換器５０は、一方のディスプレーサピストン２０Ａのピストンヘッド側の外周部と、他方のディスプレーサピストン２０Ｂのピストンヘッド側の外周部とに、リング状に配置し、熱媒体通路５２は、対向する一対のディスプレーサピストン２０Ａ、２０Ｂの間には配置していない。熱媒体通路５２を流れる熱媒体にはオイルを用いている。また、排熱温度が高い場合は熱媒体に溶融塩を使用してもよい。 The heat exchanger 50 is a ring-shaped central portion in the longitudinal direction of the body portion 11 and includes an outer peripheral portion on the piston head side of one displacer piston 20A and an outer peripheral portion on the piston head side of the other displacer piston 20B. Is arranged. The coolers 42A and 42B are disposed at both ends of the trunk portion 11, and the regenerators 41A and 41B are disposed between the heat exchanger 50 and the coolers 42A and 42B.
The heat exchanger 50 includes one gas passage 51A that communicates with the expansion space 22A of one displacer piston 20A, the other gas passage 51B that communicates with the expansion space 22B of the other displacer piston 20B, one gas passage 51A, A heat medium passage 52 for heating the other gas passage 51B is formed. As described above, the heat exchanger 50 is configured as a unit by connecting the one Stirling engine and the other Stirling engine by integrally configuring the one gas passage 51A and the other gas passage 51B. .
The heat exchanger 50 is arranged in a ring shape on the outer periphery of the one displacer piston 20A on the piston head side and on the outer periphery of the other displacer piston 20B on the piston head side, and the heat medium passage 52 is a pair of opposed ones. The displacer pistons 20A and 20B are not arranged. Oil is used as the heat medium flowing through the heat medium passage 52. Further, when the exhaust heat temperature is high, a molten salt may be used as the heat medium.
　一方のガス通路５１Ａは一方の再生器４１Ａと連通し、一方の再生器４１Ａは一方の冷却器４２Ａと連通し、一方の冷却器４２Ａは一方のディスプレーサピストン２０Ａの圧縮空間２３Ａと連通している。
　また、他方のガス通路５１Ｂは他方の再生器４１Ｂと連通し、他方の再生器４１Ｂは他方の冷却器４２Ｂと連通し、他方の冷却器４２Ｂは他方のディスプレーサピストン２０Ｂの圧縮空間２３Ｂと連通している。
　ロッドの一端側は大径ロッド２４Ａ、２４Ｂ、ロッドの他端側は小径ロッド２５Ａ、２５Ｂで構成され、大径ロッド２４Ａ、２４Ｂはディスプレーサピストン２０Ａ、２０Ｂに固定され、小径ロッド２５Ａ、２５Ｂは板バネ２６Ａ、２６Ｂに連結されている。
　容器端部１２Ａ、１２Ｂは、パワーピストン２１Ａ、２１Ｂ、リニア発電機３０Ａ、３０Ｂを内部に収容する。
　以上のように、一方のスターリングエンジンは、ディスプレーサピストン２０Ａ、パワーピストン２１Ａ、加熱部である熱交換器５０、再生器４１Ａ、及び冷却器４２Ａによって構成され、他方のスターリングエンジンは、ディスプレーサピストン２０Ｂ、パワーピストン２１Ｂ、加熱部である熱交換器５０、再生器４１Ｂ、及び冷却器４２Ｂによって構成されている。 One gas passage 51A communicates with one regenerator 41A, one regenerator 41A communicates with one cooler 42A, and one cooler 42A communicates with the compression space 23A of one displacer piston 20A. .
The other gas passage 51B communicates with the other regenerator 41B, the other regenerator 41B communicates with the other cooler 42B, and the other cooler 42B communicates with the compression space 23B of the other displacer piston 20B. ing.
One end of the rod is composed of large- diameter rods 24A and 24B, and the other end of the rod is composed of small- diameter rods 25A and 25B. The large- diameter rods 24A and 24B are fixed to the displacer pistons 20A and 20B. The springs 26A and 26B are connected.
Container edge part 12A, 12B accommodates power piston 21A, 21B and linear generator 30A, 30B inside.
As described above, one Stirling engine is configured by the displacer piston 20A, the power piston 21A, the heat exchanger 50 as a heating unit, the regenerator 41A, and the cooler 42A, and the other Stirling engine is the displacer piston 20B, The power piston 21B, the heat exchanger 50 as a heating unit, a regenerator 41B, and a cooler 42B are included.
　上記構成において、熱交換器５０での加熱によって、封入されている気体が膨張してディスプレーサピストン２０Ａ、２０Ｂを端板１８から離間する方向（端部方向）へ移動させる。ディスプレーサピストン２０Ａ、２０Ｂの端部方向への移動によって、圧縮空間２３Ａ、２３Ｂにあるガスが圧縮されてパワーピストン２１Ａ、２１Ｂを端部方向へ移動させる。パワーピストン２１Ａ、２１Ｂの端部方向への移動によって、気体はディスプレーサピストン２０Ａ、２０Ｂの膨張空間２２Ａ、２２Ｂから、熱交換器５０、再生器４１Ａ、４１Ｂ、及び冷却器４２Ａ、４２Ｂを通過してディスプレーサピストン２０Ａ、２０Ｂとパワーピストン２１Ａ、２１Ｂとの間の圧縮空間２３Ａ、２３Ｂに移動する。そしてディスプレーサピストン２０Ａ、２０Ｂの端板１８に近接する方向（中心方向）への移動によって圧縮空間２３Ａ、２３Ｂが低圧になることで、パワーピストン２１Ａ、２１Ｂは中心方向へ移動する。パワーピストン２１Ａ、２１Ｂの中心方向への移動によって、圧縮空間２３Ａ、２３Ｂの気体は、冷却器４２Ａ、４２Ｂ、再生器４１Ａ、４１Ｂ、及び熱交換器５０を通過して、膨張空間２２Ａ、２２Ｂに移動する。
　このように、熱交換器５０での加熱と冷却器４２Ａ、４２Ｂでの冷却によって、気体は膨張収縮を行いながら膨張空間２２Ａ、２２Ｂと圧縮空間２３Ａ、２３Ｂを往復することで、ディスプレーサピストン２０Ａ、２０Ｂを移動させるとともに、パワーピストン２１Ａ、２１Ｂを移動させる。そして、パワーピストン２１Ａ、２１Ｂの移動によって発電を行うことができる。
　なお、本実施例による一対のスターリングエンジンは、同期運転させることが好ましい。 In the above-described configuration, the enclosed gas expands by heating in the heat exchanger 50 and moves the displacer pistons 20A and 20B away from the end plate 18 (end portion direction). By the movement of the displacer pistons 20A and 20B in the end direction, the gas in the compression spaces 23A and 23B is compressed, and the power pistons 21A and 21B are moved in the end direction. Due to the movement of the power pistons 21A and 21B in the end direction, the gas passes from the expansion spaces 22A and 22B of the displacer pistons 20A and 20B through the heat exchanger 50, the regenerators 41A and 41B, and the coolers 42A and 42B. It moves to the compression spaces 23A and 23B between the displacer pistons 20A and 20B and the power pistons 21A and 21B. The power pistons 21A and 21B move in the central direction when the compression spaces 23A and 23B become low pressure due to the movement of the displacer pistons 20A and 20B in the direction close to the end plate 18 (center direction). Due to the movement of the power pistons 21A and 21B toward the center, the gas in the compression spaces 23A and 23B passes through the coolers 42A and 42B, the regenerators 41A and 41B, and the heat exchanger 50, and enters the expansion spaces 22A and 22B. Moving.
As described above, by heating in the heat exchanger 50 and cooling in the coolers 42A and 42B, the gas reciprocates between the expansion spaces 22A and 22B and the compression spaces 23A and 23B while performing expansion and contraction, thereby displacer piston 20A, While moving 20B, power piston 21A, 21B is moved. And electric power generation can be performed by movement of power piston 21A, 21B.
The pair of Stirling engines according to the present embodiment are preferably operated synchronously.
　次に、本実施例による電気回収エンジンの吸熱用熱交換器について、図４及び図５を用いて説明する。
　吸熱用熱交換器６０は排熱ガスダクト７１の煙道中に設けられる。吸熱用熱交換器６０は二重管シェルで構成され、二重管シェル内には排ガスを流す複数のチューブ６１が設けられている。チューブ６１の外周空間６２が熱媒体の通路となり、この熱媒体の通路は、導入口６３と導出口６４を備えている。二重管シェルの外径は排熱ガスダクト７１よりも大きく、チューブ６１の総断面積を排熱ガスダクト７１の断面積よりも大きくすることで、吸熱用熱交換器６０を通過する排ガスの流通抵抗を小さくしている。また、導入口６３を排ガス流れの下流側に、導出口６４を排ガス流れの上流側に配置することで、熱媒体の流れと排ガス流れが対向流となるように構成されている。
　なお、導入口６３は図１から図３に示す熱媒体導出口１４と配管で接続され、導出口６４は図１から図３に示す熱媒体導入口１３と配管で接続されており、熱媒体であるオイルは、吸熱用熱交換器６０と熱交換器５０とを循環する。 Next, the heat exchanger for heat absorption of the electricity recovery engine according to the present embodiment will be described with reference to FIGS.
The heat absorption heat exchanger 60 is provided in the flue of the exhaust heat gas duct 71. The heat-absorbing heat exchanger 60 is constituted by a double pipe shell, and a plurality of tubes 61 for flowing exhaust gas are provided in the double pipe shell. The outer circumferential space 62 of the tube 61 serves as a heat medium passage, and the heat medium passage includes an inlet 63 and an outlet 64. The outer diameter of the double pipe shell is larger than that of the exhaust heat gas duct 71, and the total cross sectional area of the tube 61 is larger than the cross sectional area of the exhaust heat gas duct 71. Is made smaller. Further, the introduction port 63 is arranged on the downstream side of the exhaust gas flow, and the outlet port 64 is arranged on the upstream side of the exhaust gas flow, so that the flow of the heat medium and the exhaust gas flow are opposed to each other.
The inlet 63 is connected to the heat medium outlet 14 shown in FIGS. 1 to 3 by piping, and the outlet 64 is connected to the heat medium inlet 13 shown in FIGS. 1 to 3 by piping. Is circulated through the heat-absorbing heat exchanger 60 and the heat exchanger 50.
　次に、本実施例による電気回収エンジンの他の吸熱用熱交換器について、図６及び図７を用いて説明する。
　図６は同電気回収エンジンの他の吸熱用熱交換器を示す断面図、図７は図６におけるＸ－Ｘ線による断面図である。
　吸熱用熱交換器８０は排熱ガスダクト７１の煙道中に設けられる。吸熱用熱交換器８０は二重管シェルで構成され、二重管シェル内の内周部には排ガスの流路空間が形成され、この排ガスの流路空間にフィン８１が設けられている。フィン８１は、複数の平板で構成され、それぞれの平板は、二重管シェルの管軸方向を長手方向として、内管に放射状に立設されている。二重管シェル内の外周部には、螺旋状の熱媒体通路８２が形成されている。排ガスの流路空間における伝熱面積が十分である場合は、フィン８１を設けることなく、排ガスの流路空間を貫通穴で構成してもよい。熱媒体通路８２は、導入口８３と導出口８４を備えている。二重管シェルの外径は排熱ガスダクト７１よりも大きく、フィン８１間の排ガス流路の総断面積を排熱ガスダクト７１の断面積よりも大きくすることで、吸熱用熱交換器８０を通過する排ガスの流通抵抗を小さくしている。また、導入口８３を排ガス流れの下流側に、導出口８４を排ガス流れの上流側に配置することで、熱媒体の流れと排ガス流れが対向流となるように構成されている。
　なお、導入口８３は図１から図３に示す熱媒体導出口１４と配管で接続され、導出口８４は図１から図３に示す熱媒体導入口１３と配管で接続されており、熱媒体であるオイルは、吸熱用熱交換器８０と熱交換器５０とを循環する。 Next, another heat absorption heat exchanger according to the present embodiment will be described with reference to FIGS.
6 is a cross-sectional view showing another heat absorption heat exchanger of the same electricity recovery engine, and FIG. 7 is a cross-sectional view taken along line XX in FIG.
The heat absorption heat exchanger 80 is provided in the flue of the exhaust heat gas duct 71. The heat-absorbing heat exchanger 80 is constituted by a double pipe shell, and an exhaust gas passage space is formed in the inner periphery of the double pipe shell, and fins 81 are provided in the exhaust gas passage space. The fins 81 are constituted by a plurality of flat plates, and each flat plate is erected radially on the inner pipe with the pipe axis direction of the double pipe shell as the longitudinal direction. A spiral heat medium passage 82 is formed on the outer periphery of the double tube shell. If the heat transfer area in the exhaust gas passage space is sufficient, the exhaust gas passage space may be formed by through holes without providing the fins 81. The heat medium passage 82 includes an inlet 83 and an outlet 84. The outer diameter of the double pipe shell is larger than that of the exhaust heat gas duct 71, and the total cross-sectional area of the exhaust gas flow path between the fins 81 is larger than the cross-sectional area of the exhaust heat gas duct 71, thereby passing through the heat absorption heat exchanger 80. The flow resistance of exhaust gas is reduced. Further, the introduction port 83 is disposed on the downstream side of the exhaust gas flow, and the outlet port 84 is disposed on the upstream side of the exhaust gas flow, so that the flow of the heat medium and the exhaust gas flow are opposed to each other.
The inlet 83 is connected to the heat medium outlet 14 shown in FIGS. 1 to 3 through a pipe, and the outlet 84 is connected to the heat medium inlet 13 shown in FIGS. 1 to 3 through a pipe. Is circulated through the heat-absorbing heat exchanger 80 and the heat exchanger 50.
　以下本発明の他の実施例による電気回収エンジンについて図面とともに詳細に説明する。
　図８は本実施例による電気回収エンジンの概念構成図、図９は同電気回収エンジンの外観要部斜視図である。
　本実施例による電気回収エンジンについても、一方のスターリングエンジンのディスプレーサピストン１２０Ａと、他方のスターリングエンジンのディスプレーサピストン１２０Ｂとを対向させて配置し、ディスプレーサピストン１２０Ａ、１２０Ｂの軸方向にはパワーピストン１２１Ａ、１２１Ｂが同軸上に配置されている。
　ディスプレーサピストン１２０Ａ、１２０Ｂは、シリンダ部１１９Ａ、１１９Ｂ内に配置されている。
　パワーピストン１２１Ａ、１２１Ｂには、リニア発電機１３０Ａ、１３０Ｂを取り付けている。
　ディスプレーサピストン１２０Ａ、１２０Ｂの外周部には、再生器１４１Ａ、１４１Ｂ及び冷却器１４２Ａ、１４２Ｂを備えている。再生器１４１Ａ、１４１Ｂ及び冷却器１４２Ａ、１４２Ｂは、リング状に構成されている。冷却器１４２Ａ、１４２Ｂには、冷却水導入口１１５Ａ、１１５Ｂと冷却水導出口１１６Ａ、１１６Ｂが接続されている。
　ディスプレーサピストン１２０Ａの膨脹空間１２２Ａは、シリンダ部１１９Ａ、端板１１８Ａ、及びディスプレーサピストン１２０Ａのピストンヘッドによって形成している。また、ディスプレーサピストン１２０Ｂの膨脹空間１２２Ｂは、シリンダ部１１９Ｂ、端板１１８Ｂ、及びディスプレーサピストン１２０Ｂのピストンヘッドによって形成している。 Hereinafter, an electricity recovery engine according to another embodiment of the present invention will be described in detail with reference to the drawings.
FIG. 8 is a conceptual configuration diagram of the electricity recovery engine according to the present embodiment, and FIG. 9 is a perspective view of the main part of the electricity recovery engine.
Also in the electricity recovery engine according to the present embodiment, the displacer piston 120A of one Stirling engine and the displacer piston 120B of the other Stirling engine are arranged to face each other, and in the axial direction of the displacer pistons 120A, 120B, a power piston 121A, 121B is arranged on the same axis.
Displacer pistons 120A and 120B are arranged in cylinder portions 119A and 119B.
Linear power generators 130A and 130B are attached to the power pistons 121A and 121B.
Regenerators 141A and 141B and coolers 142A and 142B are provided on the outer periphery of the displacer pistons 120A and 120B. The regenerators 141A and 141B and the coolers 142A and 142B are configured in a ring shape. Cooling water inlets 115A and 115B and cooling water outlets 116A and 116B are connected to the coolers 142A and 142B.
The expansion space 122A of the displacer piston 120A is formed by the cylinder portion 119A, the end plate 118A, and the piston head of the displacer piston 120A. The expansion space 122B of the displacer piston 120B is formed by the cylinder portion 119B, the end plate 118B, and the piston head of the displacer piston 120B.
　熱交換器１５０は、一方のディスプレーサピストン１２０Ａの端板１１８Ａと、他方のディスプレーサピストン１２０Ｂの端板１１８Ｂとの間に配置している。冷却器１４２Ａ、１４２Ｂは、シリンダ部１１９Ａ、１１９Ｂの端部に配置し、再生器１４１Ａ、１４１Ｂは熱交換器１５０と冷却器１４２Ａ、１４２Ｂとの間に配置している。
　熱交換器１５０は、一方のディスプレーサピストン１２０Ａの膨張空間１２２Ａと連通する一方のガス通路１５１Ａと、他方のディスプレーサピストン１２０Ｂの膨張空間１２２Ｂと連通する他方のガス通路１５１Ｂと、一方のガス通路１５１Ａ及び他方のガス通路１５１Ｂを加熱する熱媒体通路１５２とを形成している。このように熱交換器１５０は、一方のガス通路１５１Ａと他方のガス通路１５１Ｂとを一体に構成することで、一方のスターリングエンジンと他方のスターリングエンジンとを連結しており、ユニット化されている。なお、熱媒体通路１５２は、工場に設置され、又は車輌が搭載している排気ガス通路や排熱ダクトを直接利用するものであってもよく、熱媒体通路１５２には排気ガスが熱媒体として流れる。
　熱交換器１５０は、ガス通路１５１Ａ、１５１Ｂを、対向する一対のディスプレーサピストン１２０Ａ、１２０Ｂの間に配置し、熱媒体通路１５２を流れるガスの流れ方向を、ディスプレーサピストン１２０Ａ、１２０Ｂの軸に直交する方向としている。
　本実施例では、ガス通路１５１Ａ、１５１Ｂを排熱ガスダクト１７１内に配置している。ガス通路１５１Ａ、１５１Ｂは、複数の直管で構成し、それぞれの直管を円弧状に配置している。
　本実施例による熱交換器１５０は、一方のガス通路１５１Ａは他方の再生器１４１Ｂと連通し、他方の再生器１４１Ｂは他方の冷却器１４２Ｂと連通し、他方の冷却器１４２Ｂは他方のディスプレーサピストン１２０Ｂの圧縮空間１２３Ｂと連通している。
　また、他方のガス通路１５１Ｂは一方の再生器１４１Ａと連通し、一方の再生器１４１Ａは一方の冷却器１４２Ａと連通し、一方の冷却器１４２Ａは一方のディスプレーサピストン１２０Ａの圧縮空間１２３Ａと連通している。
　本実施例による電気回収エンジンは、それぞれのディスプレーサピストン１２０Ａ、１２０Ｂにはそれぞれ制御モータ１８０Ａ、１８０Ｂを取り付け、それぞれの制御モータ１８０Ａ、１８０Ｂによって、一対のスターリングエンジンを０度の位相で同期運転させる。 The heat exchanger 150 is disposed between the end plate 118A of one displacer piston 120A and the end plate 118B of the other displacer piston 120B. The coolers 142A and 142B are disposed at the ends of the cylinder portions 119A and 119B, and the regenerators 141A and 141B are disposed between the heat exchanger 150 and the coolers 142A and 142B.
The heat exchanger 150 includes one gas passage 151A communicating with the expansion space 122A of one displacer piston 120A, the other gas passage 151B communicating with the expansion space 122B of the other displacer piston 120B, one gas passage 151A, and A heat medium passage 152 for heating the other gas passage 151B is formed. As described above, the heat exchanger 150 is configured as a unit by connecting the one Stirling engine and the other Stirling engine by integrally configuring the one gas passage 151A and the other gas passage 151B. . The heat medium passage 152 may be installed in a factory, or may directly use an exhaust gas passage or a heat exhaust duct mounted on a vehicle. The heat medium passage 152 has exhaust gas as a heat medium. Flowing.
In the heat exchanger 150, the gas passages 151A and 151B are disposed between a pair of opposing displacer pistons 120A and 120B, and the flow direction of the gas flowing through the heat medium passage 152 is orthogonal to the axis of the displacer pistons 120A and 120B. The direction.
In the present embodiment, the gas passages 151 </ b> A and 151 </ b> B are disposed in the exhaust heat gas duct 171. The gas passages 151A and 151B are constituted by a plurality of straight pipes, and the respective straight pipes are arranged in an arc shape.
In the heat exchanger 150 according to the present embodiment, one gas passage 151A communicates with the other regenerator 141B, the other regenerator 141B communicates with the other cooler 142B, and the other cooler 142B is the other displacer piston. It communicates with the 120B compression space 123B.
The other gas passage 151B communicates with one regenerator 141A, one regenerator 141A communicates with one cooler 142A, and one cooler 142A communicates with the compression space 123A of one displacer piston 120A. ing.
In the electricity recovery engine according to the present embodiment, control motors 180A and 180B are attached to the displacer pistons 120A and 120B, respectively, and the pair of Stirling engines are synchronously operated with a phase of 0 degrees by the control motors 180A and 180B.
　上記構成において、熱交換器１５０での加熱によって、封入されている気体が膨張してディスプレーサピストン１２０Ａ、１２０Ｂを端板１１８Ａ、１１８Ｂから離間する方向（端部方向）へ移動させる。
　ここで、一方のディスプレーサピストン１２０Ａの端部方向への移動によって、圧縮空間１２３Ａにあるガスが圧縮されてパワーピストン１２１Ａを端部方向へ移動させる。パワーピストン１２１Ａの端部方向への移動によって、他方のディスプレーサピストン１２０Ｂの膨張空間１２２Ｂにある気体が、熱交換器１５０、再生器１４１Ａ、及び冷却器１４２Ａを通過してディスプレーサピストン１２０Ａとパワーピストン１２１Ａとの間の圧縮空間１２３Ａに移動する。そしてディスプレーサピストン１２０Ａの端板１１８Ａに近接する方向（中心方向）への移動によって圧縮空間１２３Ａが低圧になることで、パワーピストン１２１Ａは中心方向へ移動する。パワーピストン１２１Ａの中心方向への移動によって、一方の圧縮空間１２３Ａの気体は、冷却器１４２Ａ、再生器１４１Ａ、及び熱交換器１５０を通過して、他方のディスプレーサピストン１２０Ｂの膨張空間１２２Ｂに移動する。
　また、他方のディスプレーサピストン１２０Ｂの端部方向への移動によって、圧縮空間１２３Ｂにあるガスが圧縮されてパワーピストン１２１Ｂを端部方向へ移動させる。パワーピストン１２１Ｂの端部方向への移動によって、一方のディスプレーサピストン１２０Ａの膨張空間１２２Ａにある気体は、熱交換器１５０、再生器１４１Ｂ、及び冷却器１４２Ｂを通過してディスプレーサピストン１２０Ｂとパワーピストン１２１Ｂとの間の圧縮空間１２３Ｂに移動する。そしてディスプレーサピストン１２０Ｂの中心方向への移動によって圧縮空間１２３Ｂが低圧になることで、パワーピストン１２１Ｂは中心方向へ移動する。パワーピストン１２１Ｂの中心方向への移動によって、他方の圧縮空間１２３Ｂの気体は、冷却器１４２Ｂ、再生器１４１Ｂ、及び熱交換器１５０を通過して、一方のディスプレーサピストン１２０Ａの膨張空間１２２Ａに移動する。 In the above-described configuration, the enclosed gas expands by heating in the heat exchanger 150 and moves the displacer pistons 120A and 120B away from the end plates 118A and 118B (end direction).
Here, by the movement of one displacer piston 120A in the end direction, the gas in the compression space 123A is compressed, and the power piston 121A is moved in the end direction. Due to the movement of the power piston 121A toward the end, the gas in the expansion space 122B of the other displacer piston 120B passes through the heat exchanger 150, the regenerator 141A, and the cooler 142A, and the displacer piston 120A and the power piston 121A. It moves to the compression space 123A between. Then, the displacement of the compression space 123A by the movement of the displacer piston 120A in the direction (center direction) close to the end plate 118A causes the power piston 121A to move in the center direction. By the movement of the power piston 121A toward the center, the gas in one compression space 123A passes through the cooler 142A, the regenerator 141A, and the heat exchanger 150 and moves to the expansion space 122B of the other displacer piston 120B. .
Further, the gas in the compression space 123B is compressed by the movement of the other displacer piston 120B in the end direction, and the power piston 121B is moved in the end direction. Due to the movement of the power piston 121B in the end direction, the gas in the expansion space 122A of one displacer piston 120A passes through the heat exchanger 150, the regenerator 141B, and the cooler 142B, and the displacer piston 120B and the power piston 121B. It moves to the compression space 123B between. Then, the displacement of the compression space 123B due to the movement of the displacer piston 120B in the center direction causes the power piston 121B to move in the center direction. By the movement of the power piston 121B toward the center, the gas in the other compression space 123B passes through the cooler 142B, the regenerator 141B, and the heat exchanger 150, and moves to the expansion space 122A of the one displacer piston 120A. .
　このように、熱交換器５０での加熱と冷却器４２Ａ、４２Ｂでの冷却によって、気体は膨張収縮を行いながら膨張空間２２Ａ、２２Ｂと圧縮空間２３Ａ、２３Ｂを往復することで、ディスプレーサピストン２０Ａ、２０Ｂを移動させるとともに、パワーピストン２１Ａ、２１Ｂを移動させる。そして、パワーピストン２１Ａ、２１Ｂの移動によって発電を行うことができる。
　特に、本実施例では、一方のスターリングエンジンの膨張空間１２２Ａから導出させたガスを同じスターリングエンジンの圧縮空間１２３Ａに戻すことなく、対向する他方のスターリングエンジンの圧縮空間１２３Ｂに導き、他方のスターリングエンジンの膨張空間１２２Ｂから導出させたガスを同じスターリングエンジンの圧縮空間１２３Ｂに戻すことなく、対向する一方のスターリングエンジンの圧縮空間１２３Ａに導くため、ガス通路１５１Ａ、１５１ＢをＵ字状に曲げる必要が無く、流路抵抗の少ないガス通路とすることができ、効率が高まるとともに、ガス通路１５１Ａ、１５１Ｂを直管で構成できるため、Ｕ字部のような曲げ部分がある場合と比較して耐久性を向上させることができる。 As described above, by heating in the heat exchanger 50 and cooling in the coolers 42A and 42B, the gas reciprocates between the expansion spaces 22A and 22B and the compression spaces 23A and 23B while performing expansion and contraction, thereby displacer piston 20A, While moving 20B, power piston 21A, 21B is moved. And electric power generation can be performed by movement of power piston 21A, 21B.
In particular, in this embodiment, the gas led out from the expansion space 122A of one Stirling engine is led to the compression space 123B of the other Stirling engine facing the other Stirling engine without returning to the compression space 123A of the same Stirling engine. Since the gas led out from the expansion space 122B is guided to the compression space 123A of the opposite Stirling engine without returning to the compression space 123B of the same Stirling engine, there is no need to bend the gas passages 151A and 151B in a U-shape. The gas passage can have a low flow resistance, and the efficiency can be increased and the gas passages 151A and 151B can be configured by straight pipes. Therefore, the durability can be improved as compared with the case where there is a bent portion such as a U-shaped portion. Can be improved.
　以下本発明の更に他の実施例による電気回収エンジンについて図面とともに説明する。
　図１０から図１２は、それぞれ異なる実施例による電気回収エンジンの概念構成図である。下記の説明においては、図８と同一機能を有する構成には同一符号を付して説明を省略する。
　図１０に示す実施例は、図８に示す実施例における制御モータ１８０Ａ、１８０Ｂの代わりに、ディスプレーサピストン１２０Ａ、１２０Ｂの往復運動をリニア発電機１３０Ａ、１３０Ｂに取り付けたパワーピストン１２１Ａ、１２１Ｂから電気的に制御するものであり、リニア発電機１３０Ａ、１３０Ｂの負荷制御を行う同期制御部１９０を設けている。
　図１１に示す実施例は、図８に示す実施例におけるリニア発電機１３０Ａ、１３０Ｂの代わりに、クランク機構２０１Ａ、２０１Ｂを介して回転式発電機２００Ａ、２００Ｂを設けたものである。
　図１２に示す実施例は、図１１に示す実施例における制御モータ１８０Ａ、１８０Ｂの代わりに、クランク機構２０１Ａ、２０１Ｂを介してディスプレーサピストン１２０Ａ、１２０Ｂを回転式発電機２００Ａ、２００Ｂに接続し、更に、回転式発電機２００Ａ、２００Ｂの負荷制御を行う同期制御部１９０を設けたものである。
　図１０から図１２に示す実施例による電気回収エンジンは、それぞれの構成によって一対のスターリングエンジンを０度の位相で同期運転させる。
　なお、図８及び図９に示した同期運転のための構成、及び図１０から図１２に示した同期運転のための構成は、図１から図３に示した実施例に適用することができる。 Hereinafter, an electricity recovery engine according to still another embodiment of the present invention will be described with reference to the drawings.
10 to 12 are conceptual configuration diagrams of an electricity recovery engine according to different embodiments. In the following description, components having the same functions as those in FIG.
In the embodiment shown in FIG. 10, instead of the control motors 180A and 180B in the embodiment shown in FIG. 8, the reciprocating motion of the displacer pistons 120A and 120B is electrically generated from the power pistons 121A and 121B attached to the linear generators 130A and 130B. The synchronous control part 190 which performs load control of the linear generators 130A and 130B is provided.
In the embodiment shown in FIG. 11, rotary generators 200A and 200B are provided via crank mechanisms 201A and 201B instead of the linear generators 130A and 130B in the embodiment shown in FIG.
In the embodiment shown in FIG. 12, displacer pistons 120A and 120B are connected to rotary generators 200A and 200B via crank mechanisms 201A and 201B instead of the control motors 180A and 180B in the embodiment shown in FIG. A synchronous control unit 190 that performs load control of the rotary generators 200A and 200B is provided.
The electricity recovery engine according to the embodiment shown in FIG. 10 to FIG. 12 causes a pair of Stirling engines to operate synchronously at a phase of 0 degrees depending on the respective configurations.
The configuration for synchronous operation shown in FIGS. 8 and 9 and the configuration for synchronous operation shown in FIGS. 10 to 12 can be applied to the embodiments shown in FIGS. .
　本実施例による電気回収エンジンは、一方のディスプレーサピストン２０Ａ、１２０Ａの膨張空間２２Ａ、１２２Ａと連通する一方のガス通路５１Ａ、１５１Ａと、他方のディスプレーサピストン２０Ｂ、１２０Ｂの膨張空間２２Ｂ、１２２Ｂと連通する他方のガス通路５１Ｂ、１５１Ｂと、一方のガス通路５１Ａ、１５１Ａ及び他方のガス通路５１Ｂ、１５１Ｂを加熱する熱媒体通路５２、１５２とを形成する熱交換器５０、１５０によって、一方のスターリングエンジンと他方のスターリングエンジンとを連結してユニット化したことで、２つの別々のスターリングエンジンと比較してシンプルな構成とすることができる。また、熱交換器５０、１５０の両側にスターリングエンジンが配置されるため、例えば、熱交換器５０、１５０を煙道中に配置してスターリングエンジンを煙道から突出させて施工できるため、排熱ガスダクトなどの煙道への施工性が良い。
　本実施例による電気回収エンジンは、熱媒体通路５２に流れる熱媒体としてオイル又は溶融塩を用いたことで、特に低温排熱を利用する場合に、伝熱面積が小さくても十分な熱回収を行うことができ、熱交換器のデッドスペースを少なくすることができる。
　本実施例による電気回収エンジンは、熱交換器５０を、一方のディスプレーサピストン２０Ａのピストンヘッド側の外周部と、他方のディスプレーサピストン２０Ｂのピストンヘッド側の外周部とに、リング状に配置したことで、ディスプレーサピストン２０Ａ、２０Ｂの膨張空間２３Ａ、２３Ｂの外周を加熱できるので熱効率を高めることができる。
　本実施例による電気回収エンジンは、熱媒体通路５２を、対向する一対のディスプレーサピストン２０Ａ、２０Ｂの間には配置せず、熱媒体通路５２に熱媒体を導入する導入口１３と、熱媒体通路５２から熱媒体を導出する導出口１４とを熱交換器５０の外周面に配置したことで、ディスプレーサピストン２０Ａ、２０Ｂの軸方向の長さを短くできる。
　本実施例による電気回収エンジンは、排熱ガスダクト７１に設けた吸熱用熱交換器６０、８０と、吸熱用熱交換器６０、８０と熱交換器５０とを熱媒体が循環する配管とを設けたことで、高い熱効率で排熱を利用することができるとともに、スターリングエンジンを排熱ガスダクトの配置に影響されずに施工できるために、施工性が良い。
　本実施例による電気回収エンジンは、一方のガス通路１５１Ａを、他方のスターリングエンジンの再生器１４１Ｂと連通させ、他方のガス通路１５１Ｂを、一方のスターリングエンジンの再生器１４１Ａと連通させたことで、ガス通路１５１Ａ、１５１ＢをＵ字状に曲げる必要が無く、流路抵抗の少ないガス通路１５１Ａ、１５１Ｂとすることができ、効率が高まるとともに、Ｕ字部のような曲げ部分がある場合と比較して耐久性を向上させることができる。
　本実施例による電気回収エンジンは、ガス通路１５０を、対向する一対のディスプレーサピストン１２０Ａ、１２０Ｂの間に配置し、熱媒体通路１５２を流れるガスの流れ方向を、ディスプレーサピストン１２０Ａ、１２０Ｂの軸に直交する方向としたことで、排熱ガスダクト１７１のような煙道に施工した場合に、煙道を流れるガスの排熱を効率よく回収することができる。
　本実施例による電気回収エンジンは、ガス通路１５１Ａ、１５１Ｂを複数の直管で構成し、それぞれの直管をリング状に配置したことで、排熱ガスダクト１７１のような煙道を流れるガス流に対する抵抗を小さくでき、効率よく熱回収を行うことができる。
　本実施例による電気回収エンジンは、一対のスターリングエンジンを０度の位相で同期運転させることで、一対のスターリングエンジンの同期運転によって低振動化を図ることができる。
　本実施例による電気回収エンジンは、それぞれのパワーピストン１２０Ａ、１２０Ｂにはそれぞれリニア発電機１３０Ａ、１３０Ｂを取り付け、それぞれのディスプレーサピストン１２０Ａ、１２０Ｂにはそれぞれ制御モータ１８０Ａ、１８０Ｂを取り付けたことで、回転式発電機２００Ａ、２００Ｂと比較して伝達ロスが少なく高効率な電気回収が行えるとともに、それぞれの制御モータによって同期を容易に行うことができる。
　本実施による電気回収エンジンは、一方のパワーピストン１２１Ａ及び一方のディスプレーサピストン１２０Ａには一方のリニア発電機１３０Ａを取り付け、他方のパワーピストン１２１Ｂ及び他方のディスプレーサピストン１２０Ｂには他方のリニア発電機１３０Ｂを取り付けたことで、リニア発電機１３０Ａ、１３０Ｂを用いることで回転式発電機２００Ａ、２００Ｂと比較して伝達ロスが少なく高効率な電気回収が行えるとともに、それぞれのリニア発電機の負荷を一定に保つことで同期を容易に行うことができる。
　本実施による電気回収エンジンは、それぞれのパワーピストン１２１Ａ、１２１Ｂにはそれぞれ回転式発電機２００Ａ、２００Ｂを取り付け、それぞれのディスプレーサピストン１２０Ａ、１２０Ｂにはそれぞれ制御モータ１８０Ａ、１８０Ｂを取り付けたことで、パワーピストン１２１Ａ、１２１Ｂとディスプレーサピストン１２０Ａ、１２０Ｂとの位相が固定されているので同期を容易に行うことができる。
　本実施例による電気回収エンジンは、一方のパワーピストン１２１Ａ及び一方のディスプレーサピストン１２０Ａには一方の回転式発電機２００Ａを取り付け、他方のパワーピストン１２１Ｂ及び他方のディスプレーサピストン１２０Ｂには他方の回転式発電機２００Ｂを取り付けたものである。本実施の形態によれば、パワーピストン１２１Ａ、１２１Ｂとディスプレーサピストン１２０Ａ、１２０Ｂとの位相が固定されているので同期を容易に行うことができる。 The electricity recovery engine according to the present embodiment communicates with one gas passage 51A, 151A communicating with the expansion spaces 22A, 122A of one displacer piston 20A, 120A and with expansion spaces 22B, 122B of the other displacer pistons 20B, 120B. The heat exchangers 50 and 150 that form the other gas passages 51B and 151B, the one gas passages 51A and 151A, and the heat medium passages 52 and 152 that heat the other gas passages 51B and 151B are combined with one Stirling engine. Since the other Stirling engine is connected and unitized, a simple configuration can be obtained as compared with two separate Stirling engines. Further, since the Stirling engines are arranged on both sides of the heat exchangers 50 and 150, for example, the heat exchangers 50 and 150 can be arranged in the flue and the Stirling engine can be projected from the flue, so that the exhaust heat gas duct Good workability in flues.
The electricity recovery engine according to the present embodiment uses oil or molten salt as the heat medium flowing in the heat medium passage 52, so that sufficient heat recovery is possible even when the heat transfer area is small, particularly when using low-temperature exhaust heat. This can be done and the dead space of the heat exchanger can be reduced.
In the electricity recovery engine according to the present embodiment, the heat exchanger 50 is arranged in a ring shape on the outer periphery of the one displacer piston 20A on the piston head side and on the outer periphery of the other displacer piston 20B on the piston head side. Thus, since the outer circumferences of the expansion spaces 23A and 23B of the displacer pistons 20A and 20B can be heated, the thermal efficiency can be increased.
In the electricity recovery engine according to the present embodiment, the heat medium passage 52 is not disposed between the pair of opposing displacer pistons 20A and 20B, and the introduction port 13 for introducing the heat medium into the heat medium passage 52, and the heat medium passage. By disposing the outlet 14 through which the heat medium is led out from 52 on the outer peripheral surface of the heat exchanger 50, the axial length of the displacer pistons 20A and 20B can be shortened.
The electricity recovery engine according to the present embodiment includes heat absorption heat exchangers 60 and 80 provided in the exhaust heat gas duct 71, and a pipe through which a heat medium circulates between the heat absorption heat exchangers 60 and 80 and the heat exchanger 50. As a result, exhaust heat can be used with high thermal efficiency, and the Stirling engine can be constructed without being affected by the arrangement of the exhaust heat gas duct, so that the workability is good.
In the electricity recovery engine according to the present embodiment, one gas passage 151A is communicated with the regenerator 141B of the other Stirling engine, and the other gas passage 151B is communicated with the regenerator 141A of one Stirling engine. There is no need to bend gas passages 151A and 151B in a U shape, and gas passages 151A and 151B with low flow resistance can be obtained, which increases efficiency and is compared to the case where there is a bent portion such as a U portion. And durability can be improved.
In the electricity recovery engine according to the present embodiment, the gas passage 150 is disposed between a pair of opposing displacer pistons 120A and 120B, and the flow direction of the gas flowing through the heat medium passage 152 is orthogonal to the axis of the displacer pistons 120A and 120B. By adopting the direction, the exhaust heat of the gas flowing through the flue can be efficiently recovered when it is constructed in a flue such as the exhaust heat gas duct 171.
In the electricity recovery engine according to the present embodiment, the gas passages 151A and 151B are constituted by a plurality of straight pipes, and the respective straight pipes are arranged in a ring shape, so that the gas flow flowing through the flue such as the exhaust heat gas duct 171 can be prevented. Resistance can be reduced and heat recovery can be performed efficiently.
In the electricity recovery engine according to the present embodiment, the pair of Stirling engines can be operated synchronously with a phase of 0 degrees, so that the vibration can be reduced by the synchronous operation of the pair of Stirling engines.
The electricity recovery engine according to the present embodiment is rotated by attaching linear generators 130A and 130B to the power pistons 120A and 120B, respectively, and attaching control motors 180A and 180B to the displacer pistons 120A and 120B, respectively. Compared with the electric power generators 200A and 200B, there is less transmission loss and highly efficient electricity recovery can be performed, and synchronization can be easily performed by the respective control motors.
In the electricity recovery engine according to the present embodiment, one power generator 121A and one displacer piston 120A have one linear generator 130A attached, and the other power piston 121B and the other displacer piston 120B have the other linear generator 130B. By attaching the linear generators 130A and 130B, it is possible to perform highly efficient electricity recovery with less transmission loss compared to the rotary generators 200A and 200B, and keep the load of each linear generator constant. Thus, synchronization can be easily performed.
In the electricity recovery engine according to this embodiment, rotary power generators 200A and 200B are attached to the power pistons 121A and 121B, respectively, and control motors 180A and 180B are attached to the displacer pistons 120A and 120B, respectively. Since the phases of the pistons 121A and 121B and the displacer pistons 120A and 120B are fixed, synchronization can be easily performed.
In the electricity recovery engine according to the present embodiment, one rotary generator 200A is attached to one power piston 121A and one displacer piston 120A, and the other rotary power generator is attached to the other power piston 121B and the other displacer piston 120B. The machine 200B is attached. According to the present embodiment, since the phases of power pistons 121A and 121B and displacer pistons 120A and 120B are fixed, synchronization can be easily performed.
　本発明の電気回収エンジンは、工場排熱のみならず、自動車や船舶等のエンジンの排熱にも適用できる。 The electricity recovery engine of the present invention can be applied not only to factory exhaust heat but also to exhaust heat of engines such as automobiles and ships.

Claims (13)

  1. 　ディスプレーサピストンとパワーピストンとを同軸上に配置した一対のスターリングエンジンを備え、前記スターリングエンジンはそれぞれが再生器と冷却器とを有し、
    一方の前記スターリングエンジンの前記ディスプレーサピストンと、他方の前記スターリングエンジンの前記ディスプレーサピストンとを対向させて配置した電気回収エンジンであって、
    一方の前記ディスプレーサピストンの膨張空間と連通する一方のガス通路と、他方の前記ディスプレーサピストンの膨張空間と連通する他方のガス通路と、一方の前記ガス通路及び他方の前記ガス通路を加熱する熱媒体通路とを形成する熱交換器によって、一方の前記スターリングエンジンと他方の前記スターリングエンジンとを連結してユニット化したことを特徴とする電気回収エンジン。     It includes a pair of Stirling engines in which a displacer piston and a power piston are coaxially arranged, each of the Stirling engines having a regenerator and a cooler,
    An electric recovery engine in which the displacer piston of one of the Stirling engines and the displacer piston of the other Stirling engine are arranged to face each other,
    One gas passage communicating with the expansion space of the one displacer piston, the other gas passage communicating with the expansion space of the other displacer piston, and the heat medium for heating the one gas passage and the other gas passage. An electric recovery engine characterized in that one Stirling engine and the other Stirling engine are connected and unitized by a heat exchanger that forms a passage.
  2. 　前記熱媒体通路を流れる熱媒体としてオイル又は溶融塩を用いたことを特徴とする請求項１に記載の電気回収エンジン。 The oil recovery engine according to claim 1, wherein oil or molten salt is used as a heat medium flowing through the heat medium passage.
  3. 　前記熱交換器を、一方の前記ディスプレーサピストンのピストンヘッド側の外周部と、他方の前記ディスプレーサピストンのピストンヘッド側の外周部とに、リング状に配置したことを特徴とする請求項２に記載の電気回収エンジン。 The said heat exchanger is arrange | positioned at the outer peripheral part by the side of the piston head of one said displacer piston, and the outer peripheral part by the side of the piston head of the said other displacer piston. Electricity recovery engine.
  4. 　前記熱媒体通路に前記熱媒体を導入する導入口と、前記熱媒体通路から前記熱媒体を導出する導出口とを前記熱交換器の外周面に配置し、前記熱媒体通路を、対向する一対の前記ディスプレーサピストンの間には配置しないことを特徴とする請求項３に記載の電気回収エンジン。 An inlet for introducing the heat medium into the heat medium passage and an outlet for deriving the heat medium from the heat medium passage are arranged on the outer peripheral surface of the heat exchanger, and the heat medium passage is opposed to a pair The electric recovery engine according to claim 3, wherein the electric recovery engine is not disposed between the displacer pistons.
  5. 　排熱ガスダクトに設けた吸熱用熱交換器と、前記吸熱用熱交換器と前記熱交換器とを前記熱媒体が循環する配管とを設けたことを特徴とする請求項２に記載の電気回収エンジン。 The heat recovery according to claim 2, further comprising: a heat exchanger for heat absorption provided in an exhaust heat gas duct; and a pipe through which the heat medium circulates through the heat exchanger for heat absorption and the heat exchanger. engine.
  6. 　一方の前記ガス通路を、他方の前記スターリングエンジンの前記再生器と連通させ、他方の前記ガス通路を、一方の前記スターリングエンジンの前記再生器と連通させたことを特徴とする請求項１に記載の電気回収エンジン。 The one gas passage is communicated with the regenerator of the other Stirling engine, and the other gas passage is communicated with the regenerator of one Stirling engine. Electricity recovery engine.
  7. 　前記ガス通路を、対向する一対の前記ディスプレーサピストンの間に配置し、前記熱媒体通路を流れるガスの流れ方向を、前記ディスプレーサピストンの軸に直交する方向としたことを特徴とする請求項６に記載の電気回収エンジン。 The gas passage is disposed between a pair of the displacer pistons facing each other, and a flow direction of the gas flowing through the heat medium passage is set to a direction orthogonal to an axis of the displacer piston. The described electricity recovery engine.
  8. 　前記ガス通路を、複数の直管で構成し、それぞれの前記直管を円弧状に配置したことを特徴とする請求項６に記載の電気回収エンジン。 The electric recovery engine according to claim 6, wherein the gas passage is constituted by a plurality of straight pipes, and each of the straight pipes is arranged in an arc shape.
  9. 　一対の前記スターリングエンジンを０度の位相で同期運転させることを特徴とする請求項１に記載の電気回収エンジン。 The electric recovery engine according to claim 1, wherein the pair of Stirling engines are operated synchronously with a phase of 0 degrees.
  10. 　それぞれの前記パワーピストンにはそれぞれリニア発電機を取り付け、それぞれの前記ディスプレーサピストンにはそれぞれ制御モータを取り付けたことを特徴とする請求項９に記載の電気回収エンジン。 10. The electric recovery engine according to claim 9, wherein a linear generator is attached to each of the power pistons, and a control motor is attached to each of the displacer pistons.
  11. 　一方の前記パワーピストン及び一方の前記ディスプレーサピストンには一方のリニア発電機を取り付け、他方の前記パワーピストン及び他方の前記ディスプレーサピストンには他方のリニア発電機を取り付けたことを特徴とする請求項９に記載の電気回収エンジン。 10. One linear generator is attached to one power piston and one displacer piston, and the other linear generator is attached to the other power piston and the other displacer piston. The electricity recovery engine described in 1.
  12. 　それぞれの前記パワーピストンにはそれぞれ回転式発電機を取り付け、それぞれの前記ディスプレーサピストンにはそれぞれ制御モータを取り付けたことを特徴とする請求項９に記載の電気回収エンジン。 10. The electric recovery engine according to claim 9, wherein a rotary generator is attached to each of the power pistons, and a control motor is attached to each of the displacer pistons.
  13. 　一方の前記パワーピストン及び一方の前記ディスプレーサピストンには一方の回転式発電機を取り付け、他方の前記パワーピストン及び他方の前記ディスプレーサピストンには他方の回転式発電機を取り付けたことを特徴とする請求項９に記載の電気回収エンジン。 One rotary generator is attached to one power piston and one displacer piston, and the other rotary generator is attached to the other power piston and the other displacer piston. Item 10. The electricity recovery engine according to Item 9.
PCT/JP2010/003816 2009-06-08 2010-06-08 Engine for electrical recovery WO2010143418A1 (en)

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JP3188818U (en) * 2013-09-12 2014-02-13 志村　征男 Stirling engine
CN114320656A (en) * 2021-12-10 2022-04-12 兰州空间技术物理研究所 Heater assembly applied to Stirling generator

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JP2014031726A (en) * 2012-08-01 2014-02-20 Hidemi Kurita Drive control method for stirling engine

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CN114320656A (en) * 2021-12-10 2022-04-12 兰州空间技术物理研究所 Heater assembly applied to Stirling generator

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