EP1717413A1 - Brayton cycle device and exhaust heat energy recovery device for internal combustion engine - Google Patents
Brayton cycle device and exhaust heat energy recovery device for internal combustion engine Download PDFInfo
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- EP1717413A1 EP1717413A1 EP05704295A EP05704295A EP1717413A1 EP 1717413 A1 EP1717413 A1 EP 1717413A1 EP 05704295 A EP05704295 A EP 05704295A EP 05704295 A EP05704295 A EP 05704295A EP 1717413 A1 EP1717413 A1 EP 1717413A1
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- Prior art keywords
- scroll
- expander
- compressor
- orbital
- working fluid
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C1/00—Rotary-piston machines or engines
- F01C1/02—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F01C1/0207—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F01C1/0215—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
- F01C1/0223—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving with symmetrical double wraps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C11/00—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type
- F01C11/002—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of similar working principle
- F01C11/004—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of similar working principle and of complementary function, e.g. internal combustion engine with supercharger
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C11/00—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type
- F01C11/006—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of dissimilar working principle
- F01C11/008—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of dissimilar working principle and of complementary function, e.g. internal combustion engine with supercharger
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
Definitions
- the present invention relates to an apparatus realizing a Brayton cycle and an apparatus for recovering exhaust heat energy of an internal combustion engine using a Brayton cycle.
- a Rankine cycle apparatus is mounted on a vehicle together with an internal combustion engine.
- a vaporizer arranged in the Rankine cycle apparatus generates high-temperature high-pressure vapor by heating water, which is contained in the apparatus, using exhaust heat energy.
- An expander generates power using the vapor (refer for example to Japanese Laid-Open Patent Publication No. 2003-120281 ).
- Japanese Laid-Open Patent Publication No. 2003-138933 describes a technique for drawing exhaust into a scroll expander. This inevitably increases the exhaust back pressure of the internal combustion engine and lowers the engine output. In this case, there may be no improvement in the engine fuel efficiency as a whole.
- the present invention provides a Brayton cycle apparatus.
- the Brayton cycle apparatus includes a scroll compressor, a scroll expander that operates in cooperation with an orbiting action of the scroll compressor, and a heating device for heating a compressed working fluid that is fed from the scroll compressor to the scroll expander.
- this Brayton cycle apparatus uses the scroll compressor and the scroll expander and simplifies its structure.
- the simplified structure downsizes the apparatus.
- the working fluid is moved, compressed, and expanded inside the compressor and the expander in partitioned and sealed spaces.
- the efficiency of conversion from heat energy to kinetic energy is high.
- the heating device heats the working fluid by heat transfer to drive the Brayton cycle apparatus of the present invention.
- the pressure of the energy source itself causes no problem, and the back pressure of the energy source including the exhaust is unaffected.
- the Brayton cycle apparatus of the present invention efficiently converts heat energy to kinetic energy without increasing the back pressure of the energy source.
- the apparatus recovers the exhaust heat energy efficiently without increasing the exhaust back pressure.
- an orbital compression scroll of the scroll compressor and an orbital expansion scroll of the scroll expander are arranged at opposite sides of an orbital partitioning wall.
- the orbital compression scroll of the orbital partitioning wall comes in contact with a compressor case in which a fixed compression scroll is formed in a slidable manner or faces the compressor case with a narrow space between them.
- the orbital compression scroll is combined with the fixed compression scroll to form the scroll compressor.
- the orbital expansion scroll on the orbital partitioning wall comes in contact with an expander case in which a fixed expansion scroll is formed in a slidable manner or faces the expander case with a narrow space between them.
- the orbital expansion scroll is combined with the fixed expansion scroll to form the scroll expander.
- the scroll compressor and the scroll expander are formed in this manner so that the Brayton cycle apparatus is further simplified and downsized.
- the scroll compressor releases heat transferred from the scroll expander to the orbital partitioning wall into the atmosphere via the compressor case.
- the scroll compressor comes in contact with the scroll expander through the orbital partitioning wall.
- the compressor case at a low-temperature side receives heat of the orbital partitioning wall transferred from the scroll expander at a high-temperature side and releases the heat into the atmosphere.
- the heat releasing effect of the compressor case prevents the orbital partitioning wall from being heated to a high temperature.
- the orbital partitioning wall is prevented from being deformed by heat, and the dimensional accuracy of the orbital partitioning wall is maintained. This prevents the working fluid from leaking, and prevents the friction coefficient during orbiting of the orbital partitioning wall from becoming large. This maintains high energy conversion efficiency.
- the orbital partitioning wall or the compressor case in particular may be made of a lightweight material with a low heat resistance. This contributes to further decreasing the weight of the apparatus.
- the scroll expander guides the working fluid introduced into a heat absorption chamber defined in the expander case before the introduced working fluid expands so that the working fluid that is being expanded is heated by a wall of the heat absorption chamber.
- the scroll expander with this structure enables the working fluid that is being expanded in the scroll expander to be heated by the heat of the working fluid prior to compression. This enables the Brayton cycle apparatus to convert heat energy to kinetic energy more efficiently without complicating the structure of the apparatus.
- the scroll compressor uses atmospheric gas as the working fluid and compresses the atmospheric gas, and the scroll expander releases the expanded working fluid into the atmosphere.
- the atmospheric gas is used as the working fluid in this manner and eliminates the need for an apparatus for releasing heat of the working fluid. This further simplifies and downsizes the structure of the apparatus.
- the heating device is formed as a heat exchanger for transferring external heat to the working fluid by heat exchange.
- the heating device is formed as a heat exchanger so that the apparatus is further simplified and downsized. Further, even when the Brayton cycle apparatus is used to collect exhaust heat energy of, for example, an internal combustion engine, the apparatus does not increase the exhaust back pressure.
- the present invention further provides a Brayton cycle apparatus including a positive-displacement compressor, a scroll expander for performing orbiting action in cooperation with the compression action of the positive-displacement compressor, and a heating device for heating the compressed working fluid that is fed from the positive-displacement compressor to the scroll expander.
- the Brayton cycle apparatus uses the positive-displacement compressor and the scroll expander.
- this Brayton cycle apparatus has a simple structure.
- the simple structure downsizes the apparatus.
- the working fluid is moved, compressed, and expanded inside the compressor and the expander in partitioned and sealed spaces.
- the efficiency of conversion from heat energy to kinetic energy of the Brayton cycle apparatus is high.
- the heating device heats the working fluid by heat transfer to drive the Brayton cycle apparatus of the present invention.
- the pressure of the energy source itself causes no problem, and the back pressure of the energy source including the exhaust is unaffected.
- the Brayton cycle apparatus of the present invention converts heat energy to kinetic energy without increasing the back pressure of the energy source.
- the apparatus recovers the exhaust heat energy efficiently without increasing the exhaust back pressure.
- a wall surface of the expander in the Brayton cycle apparatus is kept warm.
- the wall surface of the expander is kept warm in this manner so that heat energy is prevented from leaking from the expander. As a result, the expander converts heat energy to kinetic energy further efficiently.
- the present invention further provides an exhaust heat energy recovery apparatus for an internal combustion engine.
- the energy recovery apparatus uses a Brayton cycle apparatus for heating a compressed working fluid that is fed from a compressor to an expander by heat transferred from a flow passage wall of an exhaust passage of the internal combustion engine. As a result, the heat energy recovery apparatus recovers the exhaust heat energy as kinetic energy.
- the exhaust heat energy recovery apparatus of the present invention uses the Brayton cycle apparatus to heat the working fluid by heat transfer to collect exhaust heat energy of the internal combustion engine.
- the exhaust heat energy recovery apparatus of the present invention recovers the exhaust heat energy efficiently without increasing the exhaust back pressure of the internal combustion engine.
- a heating device included in the Brayton cycle apparatus of the heat energy recovery apparatus is formed as a heat exchanger for transferring external heat to the working fluid by heat exchange.
- This heat exchanger is arranged to come in contact with the exhaust of the internal combustion engine.
- This structure simplifies and downsizes the exhaust heat energy recovery apparatus and enables the exhaust heat energy recovery apparatus to be easily mounted on a vehicle etc.
- This exhaust heat energy recovery apparatus recovers the exhaust heat energy efficiently without increasing the exhaust back pressure of the internal combustion engine.
- the exhaust flow passage is formed as a double pipe having an inner passage and an outer passage. Heat exchange is performed between the exhaust flowing through one of the inner passage and the outer passage of the double pipe and the working fluid flowing through the other one of the passages.
- the exhaust flow passage is formed as a double pipe to enable such heat exchange so that the compressed working fluid is easily heated using the exhaust heat energy.
- the simple and compact structure enables the exhaust heat energy to be recovered efficiently without increasing the exhaust back pressure of the internal combustion engine.
- the Brayton cycle apparatus includes a scroll compressor and a scroll expander that are arranged at opposite sides of an orbital partitioning wall.
- the orbital partitioning wall and the compressor case are made of a high heat-conductive material, and the expander case is made of a heat-resistant material.
- the compressor case made of a high heat-conductive material is at a low temperature side in the Brayton cycle apparatus.
- the orbital partitioning wall is also made of a high heat-conductive material.
- the compressor case of the Brayton cycle apparatus is cooled first. This eliminates the need for using a heat-resistant material for the orbital partitioning wall and the compressor case.
- the expander case that directly comes in contact with the high-temperature working fluid is made of a heat-resistant material so that the exhaust heat energy recovery apparatus of the internal combustion engine is formed.
- an aluminum alloy is used as the high heat-conductive material, and an iron alloy is used as the heat-resistant material.
- a wall surface of the expander is kept warm.
- the use of the Brayton cycle apparatus in which the wall surface of the expander is kept warm enables heat energy to be converted to kinetic energy more efficiently, and enables the exhaust hest energy to be recovered efficiently.
- the present invention further provides a Brayton cycle apparatus including a scroll expander formed by combining an orbital expansion scroll with a fixed expansion scroll, a compressor for operating in cooperation with the orbiting action of the orbital expansion scroll to compress a working fluid, a compressed working fluid flow passage for supplying the working fluid from the compressor to the scroll expander, and a heat source for heating the working fluid in the scroll expander by heat transfer.
- the Brayton cycle apparatus is not limited to a structure in which the working fluid is heated by a compressed working fluid passage for supplying the working fluid from the compressor to the scroll expander and may have a structure for heating the working fluid in the scroll expander using heat transferred from the heat source.
- heating the working fluid in the scroll expander using heat transferred from the heat source drives the Brayton cycle apparatus of the present invention.
- the pressure of the heat source itself causes no problem, the back pressure of the heat source is unaffected, and heat energy is efficiently converted to kinetic energy.
- the apparatus recovers the exhaust heat energy efficiently without increasing the exhaust back pressure.
- the working fluid is not heated by the compressed working fluid passage. This simplifies the structure of the compressed working fluid passage itself. This further enables the working fluid to be heated by heat transfer using the structure of the scroll expander so that the Brayton cycle apparatus is further simplified and downsized.
- the compressor is a positive-displacement compressor.
- the present invention further provides a Brayton cycle apparatus including an orbital partitioning wall having a first surface on which an orbital compression scroll is formed and a second surface on which an orbital expansion scroll is formed, a scroll compressor formed by combining the orbital compression scroll with a fixed compression scroll, a scroll expander formed by combining the orbital expansion scroll with a fixed expansion scroll, a compressed working fluid passage for supplying working fluid from the scroll compressor to the scroll expander, and a heat source for heating the working fluid in the scroll expander by heat transfer.
- a Brayton cycle apparatus including an orbital partitioning wall having a first surface on which an orbital compression scroll is formed and a second surface on which an orbital expansion scroll is formed, a scroll compressor formed by combining the orbital compression scroll with a fixed compression scroll, a scroll expander formed by combining the orbital expansion scroll with a fixed expansion scroll, a compressed working fluid passage for supplying working fluid from the scroll compressor to the scroll expander, and a heat source for heating the working fluid in the scroll expander by heat transfer.
- the Brayton cycle apparatus is not be limited to the structure in which the working fluid is heated on the compressed working fluid passage for supplying the working fluid from the scroll compressor to the scroll expander and may have a structure for heating the working fluid in the scroll expander by heat transfer from the heat source.
- the Brayton cycle apparatus uses the scroll compressor and the scroll expander and simplifies the structure.
- the simplified structure downsizes the apparatus.
- the working fluid is moved, compressed, and expanded inside the compressor and the expander in partitioned spaces.
- the efficiency of conversion from heat energy to kinetic energy is high.
- heating the working fluid by heat transferred from the heat source drives the Brayton cycle apparatus of the present invention.
- the pressure of the heat source itself causes no problem, and the back pressure of the heat source is unaffected.
- the Brayton cycle apparatus of the present invention converts heat energy to kinetic energy efficiently without increasing the back pressure of the heat source. As a result, even when the Brayton cycle apparatus is applied to, for example, an internal combustion engine, the apparatus recovers the exhaust heat energy efficiently without increasing the exhaust back pressure.
- the working fluid is not heated in the compressed working fluid passage. This simplifies the structure of the compressed working fluid passage itself and further enables the working fluid to be heated by heat transfer using the structure of the scroll expander so that the Brayton cycle apparatus is further simplified and downsized.
- the compressed working fluid passage is a through-hole formed in the orbital partitioning wall.
- the through-hole communicates an internal space of the case of the scroll compressor with an internal space of the case of the scroll expander that is formed to sandwich the orbital partitioning wall together with the scroll compressor.
- the through-hole of the orbital partitioning wall also functions as the compressed working fluid passage.
- the compressed working fluid passage has an extremely simple structure. As a result, the entire Brayton cycle apparatus is further simplified and downsized.
- the heat source comes in contact with the case of the scroll expander.
- the heat source heats the working fluid in the scroll expander through the case of the scroll expander or the fixed expansion scroll fixed to the case.
- the fixed expansion scroll is used to heat the working fluid through heat transfer.
- the Brayton cycle apparatus is further simplified and downsized.
- the present invention provides an exhaust heat energy recovery apparatus that uses a Brayton cycle apparatus for heating a working fluid fed to an expander by heat transferred from a flow passage wall of an exhaust flow passage of an internal combustion engine.
- the Brayton cycle apparatus is used to heat the working fluid by heat transfer to collect exhaust heat energy of the internal combustion engine.
- the apparatus recovers the exhaust heat energy efficiently without increasing the exhaust back pressure of the internal combustion engine.
- the exhaust heat energy recovery apparatus heats the working fluid fed to the expander by heat transferred from the flow passage wall of the exhaust flow passage of the internal combustion engine. As a result, the entire exhaust heat energy recovery apparatus is simplified and downsized.
- the exhaust heat energy recovery apparatus includes a scroll expander and a heat source for heating the working fluid in the scroll expander through heat transfer.
- the exhaust of the internal combustion engine is used as the heat source.
- the entire exhaust heat energy recovery apparatus is further simplified and downsized.
- Fig. 1 shows a schematic structure of a Brayton cycle apparatus 1.
- a heat insulation apparatus 2 included in the Brayton cycle apparatus 1 is shown in Figs. 2 and 3.
- Fig. 2(A) is a front view showing the heat insulation apparatus 2
- Fig. 2(B) is a rear view
- Fig. 3(A) is a right side view
- Fig. 3(B) is a left side view of the same.
- the heat insulation apparatus 2 includes a scroll compressor 4 and a scroll expander 6.
- the scroll compressor 4 includes a compressor case 8 shown in the plan view of Fig. 4.
- a fixed compression scroll 10 is formed in an internal space 9 of the compressor case 8.
- a compressed working fluid outlet port 9a is arranged in the compressor case 8 at a location corresponding to a central portion of the fixed compression scroll 10.
- a working fluid inlet port 9b is arranged at peripheral portion of the fixed compression scroll 10.
- Fig. 6 is a perspective view showing the compressor case 8.
- the scroll expander 6 includes an expander case 12 shown in the plan view of Fig. 5.
- a fixed expansion scroll 14 is formed in an internal space 13 of the expander case 12.
- a compressed working fluid inlet port 13a is arranged in the expander case 12 at a location corresponding to a central portion of the fixed expansion scroll 14.
- a working fluid outlet port 13b is arranged at a peripheral portion of the fixed expansion scroll 14.
- Fig. 7 is a perspective view showing the expander case 12.
- a circular orbital recession 8b is arranged inside a contact surface 8a of the compressor case 8.
- a circular orbital recession 12b is arranged inside a contact surface 12a of the expander case 12.
- the two orbital recessions 8b and 12b define an accommodating chamber inside the heat insulation apparatus 2.
- the accommodating chamber accommodates an orbital partitioning wall 18.
- the orbital partitioning wall 18, which is shown in Fig. 8, in the accommodating chamber orbits while sliding in the accommodating chamber or orbits in a narrow gap formed between the orbital partitioning wall 18 and the cases.
- An orbital compression scroll 20 is formed to project from a compressor-side surface 18a of the orbital partitioning wall 18 shown in Fig. 8(A).
- An orbital expansion scroll 22 is formed to project from an expander-side surface 18b of the orbital partitioning wall 18 shown in Fig. 8 (B).
- Fig. 9 is a perspective view of the orbital partitioning wall 18.
- crank mechanisms 24 each of which is formed in to be disk-shaped are rotatably attached to the peripheral portion of the orbital partitioning wall 18 by crank pins 24b.
- the three crank mechanisms 24 are respectively accommodated in three crank accommodating units 8c, which are arranged in the compressor case 8.
- Each crank mechanism 24 has a crankshaft 24a arranged in its central portion.
- the crankshaft 24a is inserted in a crankshaft reception hole 8d arranged in the center of the crank accommodating unit 8c and is supported on the compressor case 8 in a rotatable manner. With the crank mechanisms 24 being supported on the compressor case 8 in this manner, the entire orbital partitioning wall 18 is supported on the compressor case 8 in a manner enabling orbiting.
- crankshafts 24a In the assembled state for the heat insulation apparatus 2, two of the three crankshafts 24a project outside the heat insulation apparatus 2 as shown in Figs. 1 and 2.
- the first crankshaft 24a receives a cranking torque when activating the Brayton cycle apparatus 1 from outside the heat insulation apparatus 2.
- the second crankshaft 24a outputs a torque generated by the Brayton cycle apparatus 1 out of the heat insulation apparatus 2.
- the number of crankshafts 24a projecting outside the heat insulation apparatus 2 may be changed from one to two. In this case, the single crankshaft 24a may function to both input the cranking torque and output the generated torque.
- the orbital compression scroll 20 arranged on one surface (the compressor-side surface 18a (front surface)) of the orbital partitioning wall 18 with the above-described structure is combined with the fixed compression scroll 10 of the compressor case 8 (Fig. 4 and Fig. 6), and the orbital expansion scroll 22 arranged on the other surface (the expander-side surface 18b (rear surface)) is combined with the fixed expansion scroll 14 of the expander case 12 (Fig. 5 and Fig. 7).
- the compressor case 8, the expander case 12, and the orbital partitioning wall 18 are then fastened together by the bolts Bt to form the heat insulation apparatus 2.
- Fig. 10 shows the internal structure of the scroll compressor 4 included in the heat insulation apparatus 2 with this structure.
- Fig. 10 shows the orbital compression scroll 20 arranged on the compressor-side surface 18a (front surface) of the orbital partitioning wall 18 and the compressor case 8 that is combined with the orbital compression scroll 20.
- the scroll compressor 4 is arranged so that the compressor case 8 (the orbital compression scroll 20) is located at the upper side and the expander case 12 (the orbital expansion scroll 22) is located at the lower side, the part of the compressor case 8 located above the orbital partitioning wall 18 is indicated by single-dashed lines.
- the orbital compression scroll 20 is shown in black.
- Fig. 11 shows the internal structure of the scroll expander 6 included in the heat insulation apparatus 2.
- Fig. 11 shows the orbital expansion scroll 22 arranged on the expander-side surface 18b (rear surface) of the orbital partitioning wall 18 and the expander case 12 that is combined with the orbital expansion scroll 22 as viewed through the orbital partitioning wall 18 from the side of the scroll compressor 4.
- the parts of the fixed expansion scroll 14 and the orbital expansion scroll 22 located below the orbital partitioning wall 18 are indicated by broken lines.
- the crankshafts 24a rotate clockwise as viewed in the drawings from the side of the compressor case 8 so that the orbital partitioning wall 18 orbits clockwise.
- the scroll compressor 4 realizes a heat-insulation compression stroke in the PV (pressure-volume) diagram of a Brayton cycle of Fig. 12 and the scroll expander 6 realizes a heat-insulation expansion stroke in the PV diagram.
- Fig. 13 shows the orbital partitioning wall 18 viewed from the side of the compressor case 8 and the part of the compressor case 8 located above the orbital partitioning wall 18 in an overlapped state to show the positional relationship between the fixed compression scroll 10 and the orbital compression scroll 20.
- Fig. 14 shows the orbital partitioning wall 18 viewed from the side of the compressor case 8 and the part of the expander case 12 located below the orbital partitioning wall 18 in an overlapped manner to show the positional relationship between the fixed expansion scroll 14 and the orbital expansion scroll 22.
- the orbital compression scroll 20 and the orbital expansion scroll 22, which are positioned on the front and rear surfaces of the orbital partitioning wall 18 produces the same orbiting action.
- the orbiting shown in Fig. 13 and the orbiting shown in Fig. 14 occur simultaneously at the front and rear surfaces of the orbital partitioning wall 18.
- the orbital partitioning wall 18 orbits clockwise as viewed from the side of the scroll compressor 4 as described above.
- the position of the orbital compression scroll 20 with respect to the fixed compression scroll 10 changes sequentially from the states (1) to (8) shown in Fig. 13.
- an initial volume Va1 of a working fluid (atmospheric gas in this case) is introduced into the internal space 9 of the compressor case 8 through the working fluid inlet port 9b, and the working fluid flows toward the center of the compressor case 8 while gradually reducing its volume.
- the compressed working fluid outlet port 9a opens so that the compressed working fluid is fed from the compressed working fluid outlet port 9a to the heating device 30 (Fig. 1).
- the dimensions of the fixed expansion scroll 14 and the orbital expansion scroll 22 in the axial direction are greater than the dimensions of the fixed compression scroll 10 and the orbital compression scroll 20 in the axial direction, and the scrolls are designed to satisfy the relationship Va1 ⁇ Vb1 and Va2 ⁇ Vb2.
- the heat insulation apparatus 2 and the heating device 30 with the above-described structures are combined together to complete the Brayton cycle apparatus 1 shown in Fig. 1.
- the heating device 30 uses a double pipe and includes a heat source flow passage 30a, which functions as an inner passage, and an outer passage 30b, which is arranged to surround the flow passage 30a.
- the heating device 30 has the working fluid flow through the outer passage 30b.
- the working fluid flowing through the outer passage 30b exchanges heat with fluid flowing through the heat source flow passage 30a through the pipe wall (flow passage wall) of the heat source flow passage 30a.
- an exhaust pipe of an internal combustion engine is used as the heat source flow passage 30a, exhaust heat energy of the internal combustion engine is recovered. In this case, the exhaust flows through the heat source flow passage 30a and the heat of the exhaust is transferred to the working fluid (air) flowing through the outer passage 30b.
- the values of the volumes Va1, Va2, Vb1, and Vb2 above are designed to maximize the heat conversion efficiency of the Brayton cycle apparatus 1 by considering the working fluid temperature at the working fluid inlet port 9b, the heat exchanger efficiency in the heating device 30, the working fluid temperature at the compressed working fluid inlet port 13a, and the heat insulation efficiency in the scroll compressor 4 and the scroll expander 6.
- the first embodiment has the advantages described below.
- a Brayton cycle apparatus 51 with the structure shown in Fig. 15 is used to collect exhaust heat energy of an internal combustion engine Eng that is mounted on a vehicle.
- a heat insulation apparatus 52 is formed by a scroll compressor 54 and a scroll expander 56.
- the internal structures of the scroll compressor 54 and the scroll expander 56 are the same as the structures of the scroll compressor 4 and the scroll expander 6 described in the first embodiment.
- the present embodiment differs from the first embodiment in the following points. More specifically, a large number of heat releasing fins 58b, which are formed as projections, are arranged on an end surface 58a of a compressor case 58 as shown in Fig 15 and Fig. 16.
- the heat releasing fins 58b are used to discharge from the compressor case 58 heat, which is transferred from the internal orbital partitioning wall 18 to the compressor case 58. More specifically, the heat releasing fins 58b improve the releasing efficiency of the heat received from the high-temperature scroll expander 56 by the orbital partitioning wall 18 through the compressor case 58.
- a large number of heat absorbing fins 62b which are formed as projections, are also arranged on an end surface 62a of an expander case 62 as shown in Fig 15 and Fig. 17.
- a cover 62c is arranged on the end surface 62a of the expander case 62.
- the cover 62c covers a compressed working fluid inlet port 63a and the heat absorbing fins 62b to define a heat absorption chamber 62d.
- the working fluid heated by a heating device 80 is introduced into the heat absorption chamber 62d.
- the compressed working fluid inlet port 63a that opens into the heat absorption chamber 62d absorbs the heated working fluid.
- the working fluid introduced into the heat absorption chamber 62d heats the working fluid inside the expander case 62 through the end surface 62a of the wall of the heat absorption chamber 62d.
- a pressure decrease caused by expansion of the working fluid in the scroll expander 56 is small.
- the working fluid can be set in an atmospheric pressure state and discharged from the working fluid outlet port 63b. This enables the Brayton cycle apparatus 51 to collect the exhaust heat energy more efficiently.
- the heating device 80 includes two passages, namely, a passage 80c for having the working fluid pass through the entire length of a double pipe 80b and a passage 80d for having the working fluid pass through only part of the double pipe 80b.
- the passage distribution state of the compressed working fluid supplied from the scroll compressor 54 is adjustable using a distribution valve 80e.
- the distribution ratio of the passages 80c and 80d in the present embodiment is adjusted in a manner that the working fluid supplying temperature detected by a temperature sensor 81 arranged at an opening of the compressed working fluid inlet port 63a becomes equal to a predetermined reference temperature.
- the distribution ratio of the distribution valve 80e is adjusted in a manner that the temperature of the working fluid becomes equal to a reference temperature that is appropriate for starting expansion in the scroll expander 56 when the working fluid reaches the compressed working fluid inlet port 63a after heat is absorbed by the heat absorbing fins 62b.
- crankshafts 74a of the Brayton cycle apparatus 51 are rotated when the internal combustion engine Eng starts driving the Brayton cycle apparatus 51.
- the crankshafts 74a rotate independently of the output of the internal combustion engine Eng by using heat energy of the exhaust that passes through the heating device 80.
- the crankshafts 74a need to be disconnected from the internal combustion engine Eng.
- an electromagnetic clutch 92 is arranged between an output shaft 64 of the internal combustion engine Eng and the crankshafts 74a of the Brayton cycle apparatus 51.
- the distribution ratio control of the distribution valve 80e and the engagement/disengagement control of the electromagnetic clutch 92 are executed by an electronic control unit (ECU) 94 based on the driving state of the internal combustion engine Eng.
- ECU electronice control unit
- the electromagnetic clutch 92 is set in a disengaged state before the internal combustion engine Eng is started. At the timing when the internal combustion engine exhaust temperature reaches a sufficiently high temperature after the internal combustion engine Eng is started, the electromagnetic clutch 92 is engaged so that the crankshafts 74a of the Brayton cycle apparatus 51 are rotated based on an output of the internal combustion engine Eng.
- the ECU 94 drives a valve actuator 80f and adjusts the distribution valve 80e in a manner that the working fluid temperature detected by the temperature sensor 81 is adjusted to, for example, 350°C.
- the ECU 94 disengages the electromagnetic clutch 92.
- the crankshafts 74a of the Brayton cycle apparatus 51 rotate independently to rotate an apparatus for recovering the exhaust heat energy, or a generator 96 in this case.
- the exhaust heat energy is recovered as electric energy and used as a vehicle power supply or stored in a battery.
- the expander case 62 which directly comes in contact with the high-temperature working fluid, is made of a heat-resistant material (e.g. an iron alloy such as cast iron).
- the compressor case 58 through which the working fluid flows with a relatively low temperature, is made of a high heat-conductive material (particularly a light alloy such as an aluminum alloy).
- the orbital partitioning wall 18 is made of a high heat-conductive material so that the orbital partitioning wall 18 is cooled by transferring heat to the compressor case 58.
- the second embodiment described above has the advantages described below.
- Fig. 18 is a schematic diagram showing the structure of a Brayton cycle apparatus 101.
- a heat insulation apparatus 102 included in the Brayton cycle apparatus 101 is shown in Figs. 19 and 20.
- Fig. 19(A) is a front view showing the heat insulation apparatus 102
- Fig. 19(B) is a rear view
- Fig. 20(A) is a right side view
- Fig. 20(B) is a left side view of the same.
- a working fluid inlet port 109b projects from a peripheral portion of a scroll compressor 104 and a working fluid outlet port 113b projects from a peripheral portion of a scroll expander 106.
- a compressed working fluid outlet port 9a is not arranged in a compressor case 108 and a compressed working fluid inlet port 13a is not arranged in an expander case 112 as shown in Figs. 21 to 24.
- Fig. 21 is a plan view showing the compressor case 108
- Fig. 22 is a plan view showing the expander case 112
- Fig. 23 is a perspective view showing the compressor case 108
- Fig. 24 is a perspective view showing the expander case 112.
- a through-hole 118c is formed in a central portion of an orbital partitioning wall 118 as shown in Figs. 25 and 26.
- Fig. 25 is a perspective view showing the orbital partitioning wall 118
- Fig. 26(A) is a plan view of the orbital partitioning wall 118 showing a compressor-side surface 118a of the orbital partitioning wall 118
- Fig. 26(B) is a rear view of the orbital partitioning wall 118 showing an expander-side surface 118b of the orbital partitioning wall 118.
- the orbital partitioning wall 118 orbits as shown in the states (1) to (8) in Fig. 27.
- An orbital compression scroll 120 of the orbital partitioning wall 118 moves relative to a fixed compression scroll 110 of the compressor case 108 so that the working fluid introduced from the working fluid inlet port 109b into the scroll compressor 104 is compressed and reaches the through-hole 118c formed in the central portion of the orbital partitioning wall 118.
- Fig. 27 shows the orbital partitioning wall 118 viewed from the side of the compressor case 108 and the compressor case 108 located above the orbital partitioning wall 118 in an overlapped manner to describe the positional relationship between the fixed compression scroll 110 and the orbital compression scroll 120. Accordingly, the left and right sides shown in Fig. 27 are reversed from the state shown in Fig. 21.
- the working fluid in a compressed state passes through the through-hole 118c so that the working fluid is immediately introduced into the scroll expander 106 from the scroll compressor 104 as indicated by a broken line Ap in Fig. 18.
- the orbital partitioning wall 118 orbits as shown in (1) to (8) in Fig. 28.
- An orbital expansion scroll 122 of the orbital partitioning wall 118 moves relative to a fixed expansion scroll 114 of the expander case 112 so that the working fluid introduced through the through-hole 118c into the scroll expander 106 expands and reaches the working fluid outlet port 113b.
- Fig. 28 shows the orbital partitioning wall 118 viewed from the side of the compressor case 108 and the part of the expander case 112 located below the orbital partitioning wall 118 in an overlapped manner to show the positional relationship between the fixed expansion scroll 114 and the orbital expansion scroll 122.
- the expander case 112 comes in contact with or is joined with a flow passage 130a (Fig. 18) as a heat source.
- the expander case 112 exchanges heat with a fluid flowing through the flow passage 130a through a pipe wall (flow passage wall) of the flow passage 130a.
- the working fluid expands while being heated by the heat transferred to the working fluid that comes in contact with the expander case 112 or the fixed expansion scroll 114.
- the orbital partitioning wall 118 with this structure orbits clockwise in Fig. 27 and 28 to realize a heat-insulation compression stroke, an isobaric heating stroke, and a heat-insulation expansion stroke in the PV diagram of the Brayton cycle shown in Fig. 12.
- the expander case 112 comes in contact with the high-temperature flow passage 130a and is heated to a high temperature by the heat transfer from the flow passage 130a.
- the working fluid is heated by the expander case 112 and the fixed expansion scroll 114.
- the expander case 112 and the fixed expansion scroll 114 are made of a heat-resistant material (e.g. an iron alloy such as cast iron).
- the expander case 112 and the fixed expansion scroll 114 may be made of a light alloy such as an aluminum alloy. Because the temperature of the working fluid in the compressor case 108 is relatively low, the compressor case 108 is made of a high heat-conductive material (particularly a light alloy such as an aluminum alloy).
- the orbital partitioning wall 118 is made of a high heat-conductive material so that the orbital partitioning wall 18 may be cooled by transferring heat to the compressor case 58.
- Fig. 29 shows a graph comparing the heat energy conversion efficiency experiments in the present embodiment case, in which the expander case 112 is heated, with the heat energy conversion efficiency experiments in the first embodiment case, in which the expander case 112 is not heated and the working fluid is introduced into the scroll expander 106 after the working fluid is heated separately.
- this graph compares the output torque of the crankshafts 124a when the expander case 112 is heated with an output torque of the crankshafts 124a when the working fluid introduced into the expander case 112 is heated in the state in which the scroll expander 106 is disconnected from the Brayton cycle apparatus 101.
- the horizontal axis of the graph indicates a temperate increase difference ⁇ T, which is the difference between a temperature increase of the expander case 112 and a temperature increase of the working fluid occurring via heating.
- the vertical axis of the graph indicates a torque gain (Nm).
- the heat energy conversion efficiency is higher when the expander case 112 made of an aluminum alloy is heated than when the working fluid is heated.
- the expander case 112 is made of cast iron, clearance for the mechanism of the scroll expander 106 may be reduced and the heat energy conversion efficiency is further increased.
- the third embodiment has the advantages described below.
- the compressed working fluid passage has a simple structure.
- the compressed working fluid passage is actually realized by the through-hole 118c formed in the orbital partitioning wall 118.
- the expander case 112 and the fixed expansion scroll 114 which are the components of the scroll expander 106, are used to transfer heat to the working fluid and heat the working fluid.
- the Brayton cycle apparatus 101 is further simplified and downsized.
- a Brayton cycle apparatus 201 of the present embodiment differs from the structure of the first embodiment shown in Fig. 1 in that a heat insulator 201a is arranged to cover the expander case 12 in the heat insulation apparatus 2 and keep the expander case 12 warm.
- the other parts of the Brayton cycle apparatus 201 are the same as the structure in the first embodiment.
- the components of the Brayton cycle apparatus 201 that are the same as the components in the first embodiment are denoted by the same reference numerals.
- the fourth embodiment has the advantages described below.
- the wall surface of the expander case 12 is kept warm to prevent heat energy from leaking from the scroll expander 6.
- the heat energy is converted to kinetic energy more efficiently.
Abstract
Description
- The present invention relates to an apparatus realizing a Brayton cycle and an apparatus for recovering exhaust heat energy of an internal combustion engine using a Brayton cycle.
- To improve the fuel efficiency of an internal combustion engine, an apparatus for recovering exhaust energy that is discharged from the engine after fuel is burned has been used. For example, a Rankine cycle apparatus is mounted on a vehicle together with an internal combustion engine. A vaporizer arranged in the Rankine cycle apparatus generates high-temperature high-pressure vapor by heating water, which is contained in the apparatus, using exhaust heat energy. An expander generates power using the vapor (refer for example to
Japanese Laid-Open Patent Publication No. 2003-120281 - As other techniques for recovering exhaust energy, combining an engine that uses heat, such as a Stirling engine, with an internal combustion engine (refer for example to
Japanese Laid-Open Patent Publication No. 2001- 99003 Japanese Laid-Open Patent Publication No. 2003-138933 - However, the apparatus described in
Japanese Laid-Open Patent Publication No. 2003-120281 Japanese Laid-Open Patent Publication No. 2001-99003 - Further,
Japanese Laid-Open Patent Publication No. 2003-138933 - It is an object of the present invention to provide an exhaust heat energy recovery apparatus for an internal combustion engine for recovering the exhaust heat energy efficiently without increasing the exhaust back pressure of the internal combustion engine. It is another object to provide a Brayton cycle apparatus applicable to such an exhaust heat energy recovery apparatus.
- The means for achieving the above objects and its advantages will now be described.
- The present invention provides a Brayton cycle apparatus. The Brayton cycle apparatus includes a scroll compressor, a scroll expander that operates in cooperation with an orbiting action of the scroll compressor, and a heating device for heating a compressed working fluid that is fed from the scroll compressor to the scroll expander.
- Unlike a gas turbine Brayton cycle apparatus of the prior art, this Brayton cycle apparatus uses the scroll compressor and the scroll expander and simplifies its structure. The simplified structure downsizes the apparatus. In the Brayton cycle apparatus, the working fluid is moved, compressed, and expanded inside the compressor and the expander in partitioned and sealed spaces. Thus, the efficiency of conversion from heat energy to kinetic energy is high.
- Further, the heating device heats the working fluid by heat transfer to drive the Brayton cycle apparatus of the present invention. Thus, the pressure of the energy source itself causes no problem, and the back pressure of the energy source including the exhaust is unaffected.
- In this manner, the Brayton cycle apparatus of the present invention efficiently converts heat energy to kinetic energy without increasing the back pressure of the energy source. Thus, even when the Brayton cycle apparatus of the present invention is applied to, for example, an internal combustion engine, the apparatus recovers the exhaust heat energy efficiently without increasing the exhaust back pressure.
- Preferably, an orbital compression scroll of the scroll compressor and an orbital expansion scroll of the scroll expander are arranged at opposite sides of an orbital partitioning wall. The orbital compression scroll of the orbital partitioning wall comes in contact with a compressor case in which a fixed compression scroll is formed in a slidable manner or faces the compressor case with a narrow space between them. As a result, the orbital compression scroll is combined with the fixed compression scroll to form the scroll compressor. The orbital expansion scroll on the orbital partitioning wall comes in contact with an expander case in which a fixed expansion scroll is formed in a slidable manner or faces the expander case with a narrow space between them. As a result, the orbital expansion scroll is combined with the fixed expansion scroll to form the scroll expander.
- The scroll compressor and the scroll expander are formed in this manner so that the Brayton cycle apparatus is further simplified and downsized.
- Preferably, the scroll compressor releases heat transferred from the scroll expander to the orbital partitioning wall into the atmosphere via the compressor case.
- The scroll compressor comes in contact with the scroll expander through the orbital partitioning wall. Thus, the compressor case at a low-temperature side receives heat of the orbital partitioning wall transferred from the scroll expander at a high-temperature side and releases the heat into the atmosphere. The heat releasing effect of the compressor case prevents the orbital partitioning wall from being heated to a high temperature. As a result, the orbital partitioning wall is prevented from being deformed by heat, and the dimensional accuracy of the orbital partitioning wall is maintained. This prevents the working fluid from leaking, and prevents the friction coefficient during orbiting of the orbital partitioning wall from becoming large. This maintains high energy conversion efficiency.
- As a result, the orbital partitioning wall or the compressor case in particular may be made of a lightweight material with a low heat resistance. This contributes to further decreasing the weight of the apparatus.
- Preferably, the scroll expander guides the working fluid introduced into a heat absorption chamber defined in the expander case before the introduced working fluid expands so that the working fluid that is being expanded is heated by a wall of the heat absorption chamber.
- The scroll expander with this structure enables the working fluid that is being expanded in the scroll expander to be heated by the heat of the working fluid prior to compression. This enables the Brayton cycle apparatus to convert heat energy to kinetic energy more efficiently without complicating the structure of the apparatus.
- Preferably, the scroll compressor uses atmospheric gas as the working fluid and compresses the atmospheric gas, and the scroll expander releases the expanded working fluid into the atmosphere.
- The atmospheric gas is used as the working fluid in this manner and eliminates the need for an apparatus for releasing heat of the working fluid. This further simplifies and downsizes the structure of the apparatus.
- Preferably, the heating device is formed as a heat exchanger for transferring external heat to the working fluid by heat exchange.
- In this manner, the heating device is formed as a heat exchanger so that the apparatus is further simplified and downsized. Further, even when the Brayton cycle apparatus is used to collect exhaust heat energy of, for example, an internal combustion engine, the apparatus does not increase the exhaust back pressure.
- The present invention further provides a Brayton cycle apparatus including a positive-displacement compressor, a scroll expander for performing orbiting action in cooperation with the compression action of the positive-displacement compressor, and a heating device for heating the compressed working fluid that is fed from the positive-displacement compressor to the scroll expander.
- Unlike a conventional gas turbine Brayton cycle apparatus, the Brayton cycle apparatus uses the positive-displacement compressor and the scroll expander. Thus, this Brayton cycle apparatus has a simple structure. The simple structure downsizes the apparatus. Further, in the Brayton cycle apparatus, the working fluid is moved, compressed, and expanded inside the compressor and the expander in partitioned and sealed spaces. Thus, the efficiency of conversion from heat energy to kinetic energy of the Brayton cycle apparatus is high.
- Further, the heating device heats the working fluid by heat transfer to drive the Brayton cycle apparatus of the present invention. Thus, the pressure of the energy source itself causes no problem, and the back pressure of the energy source including the exhaust is unaffected.
- In this manner, the Brayton cycle apparatus of the present invention converts heat energy to kinetic energy without increasing the back pressure of the energy source. Thus, when the Brayton cycle apparatus of the present invention is applied to, for example, an internal combustion engine, the apparatus recovers the exhaust heat energy efficiently without increasing the exhaust back pressure.
- Preferably, a wall surface of the expander in the Brayton cycle apparatus is kept warm.
- The wall surface of the expander is kept warm in this manner so that heat energy is prevented from leaking from the expander. As a result, the expander converts heat energy to kinetic energy further efficiently.
- The present invention further provides an exhaust heat energy recovery apparatus for an internal combustion engine. The energy recovery apparatus uses a Brayton cycle apparatus for heating a compressed working fluid that is fed from a compressor to an expander by heat transferred from a flow passage wall of an exhaust passage of the internal combustion engine. As a result, the heat energy recovery apparatus recovers the exhaust heat energy as kinetic energy.
- In this manner, the exhaust heat energy recovery apparatus of the present invention uses the Brayton cycle apparatus to heat the working fluid by heat transfer to collect exhaust heat energy of the internal combustion engine. Thus, the exhaust heat energy recovery apparatus of the present invention recovers the exhaust heat energy efficiently without increasing the exhaust back pressure of the internal combustion engine.
- Preferably, a heating device included in the Brayton cycle apparatus of the heat energy recovery apparatus is formed as a heat exchanger for transferring external heat to the working fluid by heat exchange. This heat exchanger is arranged to come in contact with the exhaust of the internal combustion engine.
- This structure simplifies and downsizes the exhaust heat energy recovery apparatus and enables the exhaust heat energy recovery apparatus to be easily mounted on a vehicle etc. This exhaust heat energy recovery apparatus recovers the exhaust heat energy efficiently without increasing the exhaust back pressure of the internal combustion engine.
- Preferably, the exhaust flow passage is formed as a double pipe having an inner passage and an outer passage. Heat exchange is performed between the exhaust flowing through one of the inner passage and the outer passage of the double pipe and the working fluid flowing through the other one of the passages.
- In this manner, the exhaust flow passage is formed as a double pipe to enable such heat exchange so that the compressed working fluid is easily heated using the exhaust heat energy.
- Thus, the simple and compact structure enables the exhaust heat energy to be recovered efficiently without increasing the exhaust back pressure of the internal combustion engine.
- Preferably, the Brayton cycle apparatus includes a scroll compressor and a scroll expander that are arranged at opposite sides of an orbital partitioning wall. The orbital partitioning wall and the compressor case are made of a high heat-conductive material, and the expander case is made of a heat-resistant material.
- The compressor case made of a high heat-conductive material is at a low temperature side in the Brayton cycle apparatus. The orbital partitioning wall is also made of a high heat-conductive material. Thus, the compressor case of the Brayton cycle apparatus is cooled first. This eliminates the need for using a heat-resistant material for the orbital partitioning wall and the compressor case. The expander case that directly comes in contact with the high-temperature working fluid is made of a heat-resistant material so that the exhaust heat energy recovery apparatus of the internal combustion engine is formed.
- Preferably, an aluminum alloy is used as the high heat-conductive material, and an iron alloy is used as the heat-resistant material.
- In this manner, the use of an aluminum alloy as the high heat-conductive material contributes to further decreasing the weight of the exhaust heat energy recovery apparatus.
- Preferably, a wall surface of the expander is kept warm.
- In this manner, the use of the Brayton cycle apparatus in which the wall surface of the expander is kept warm enables heat energy to be converted to kinetic energy more efficiently, and enables the exhaust hest energy to be recovered efficiently.
- The present invention further provides a Brayton cycle apparatus including a scroll expander formed by combining an orbital expansion scroll with a fixed expansion scroll, a compressor for operating in cooperation with the orbiting action of the orbital expansion scroll to compress a working fluid, a compressed working fluid flow passage for supplying the working fluid from the compressor to the scroll expander, and a heat source for heating the working fluid in the scroll expander by heat transfer.
- More specifically, the Brayton cycle apparatus is not limited to a structure in which the working fluid is heated by a compressed working fluid passage for supplying the working fluid from the compressor to the scroll expander and may have a structure for heating the working fluid in the scroll expander using heat transferred from the heat source.
- In this case, heating the working fluid in the scroll expander using heat transferred from the heat source drives the Brayton cycle apparatus of the present invention. As a result, the pressure of the heat source itself causes no problem, the back pressure of the heat source is unaffected, and heat energy is efficiently converted to kinetic energy. As a result, even when the Brayton cycle apparatus of the present invention is applied to, for example, an internal combustion engine, the apparatus recovers the exhaust heat energy efficiently without increasing the exhaust back pressure.
- Further, the working fluid is not heated by the compressed working fluid passage. This simplifies the structure of the compressed working fluid passage itself. This further enables the working fluid to be heated by heat transfer using the structure of the scroll expander so that the Brayton cycle apparatus is further simplified and downsized.
- Preferably, the compressor is a positive-displacement compressor.
- When the positive-displacement compressor is used in this manner, the working fluid in the scroll expander is heated in the manner described above. As a result, even when the Brayton cycle apparatus of the present invention is applied to, for example, an internal combustion engine, the apparatus recovers the exhaust heat energy efficiently without increasing the exhaust back pressure.
- The present invention further provides a Brayton cycle apparatus including an orbital partitioning wall having a first surface on which an orbital compression scroll is formed and a second surface on which an orbital expansion scroll is formed, a scroll compressor formed by combining the orbital compression scroll with a fixed compression scroll, a scroll expander formed by combining the orbital expansion scroll with a fixed expansion scroll, a compressed working fluid passage for supplying working fluid from the scroll compressor to the scroll expander, and a heat source for heating the working fluid in the scroll expander by heat transfer.
- More specifically, the Brayton cycle apparatus is not be limited to the structure in which the working fluid is heated on the compressed working fluid passage for supplying the working fluid from the scroll compressor to the scroll expander and may have a structure for heating the working fluid in the scroll expander by heat transfer from the heat source.
- Unlike a conventional gas turbine Brayton cycle apparatus in the prior art, the Brayton cycle apparatus uses the scroll compressor and the scroll expander and simplifies the structure. The simplified structure downsizes the apparatus. In the Brayton cycle apparatus, the working fluid is moved, compressed, and expanded inside the compressor and the expander in partitioned spaces. Thus, the efficiency of conversion from heat energy to kinetic energy is high.
- Further, heating the working fluid by heat transferred from the heat source drives the Brayton cycle apparatus of the present invention. As a result, the pressure of the heat source itself causes no problem, and the back pressure of the heat source is unaffected.
- The Brayton cycle apparatus of the present invention converts heat energy to kinetic energy efficiently without increasing the back pressure of the heat source. As a result, even when the Brayton cycle apparatus is applied to, for example, an internal combustion engine, the apparatus recovers the exhaust heat energy efficiently without increasing the exhaust back pressure.
- Further, the working fluid is not heated in the compressed working fluid passage. This simplifies the structure of the compressed working fluid passage itself and further enables the working fluid to be heated by heat transfer using the structure of the scroll expander so that the Brayton cycle apparatus is further simplified and downsized.
- Preferably, the compressed working fluid passage is a through-hole formed in the orbital partitioning wall. The through-hole communicates an internal space of the case of the scroll compressor with an internal space of the case of the scroll expander that is formed to sandwich the orbital partitioning wall together with the scroll compressor.
- The through-hole of the orbital partitioning wall also functions as the compressed working fluid passage. Thus, the compressed working fluid passage has an extremely simple structure. As a result, the entire Brayton cycle apparatus is further simplified and downsized.
- Preferably, the heat source comes in contact with the case of the scroll expander. The heat source heats the working fluid in the scroll expander through the case of the scroll expander or the fixed expansion scroll fixed to the case.
- In this case, the fixed expansion scroll is used to heat the working fluid through heat transfer. As a result, the Brayton cycle apparatus is further simplified and downsized.
- The present invention provides an exhaust heat energy recovery apparatus that uses a Brayton cycle apparatus for heating a working fluid fed to an expander by heat transferred from a flow passage wall of an exhaust flow passage of an internal combustion engine.
- In this case, the Brayton cycle apparatus is used to heat the working fluid by heat transfer to collect exhaust heat energy of the internal combustion engine. Thus, the apparatus recovers the exhaust heat energy efficiently without increasing the exhaust back pressure of the internal combustion engine.
- Further, the exhaust heat energy recovery apparatus heats the working fluid fed to the expander by heat transferred from the flow passage wall of the exhaust flow passage of the internal combustion engine. As a result, the entire exhaust heat energy recovery apparatus is simplified and downsized.
- Preferably, the exhaust heat energy recovery apparatus includes a scroll expander and a heat source for heating the working fluid in the scroll expander through heat transfer. The exhaust of the internal combustion engine is used as the heat source. Thus, the entire exhaust heat energy recovery apparatus is further simplified and downsized.
-
- Fig. 1 is a schematic view showing the structure of a Brayton cycle apparatus according to a first embodiment of the present invention;
- Fig. 2 is a diagram showing the appearance of a heat insulation apparatus included in the Brayton cycle apparatus of Fig. 1;
- Fig. 3 is a diagram showing the appearance of the heat insulation apparatus of Fig. 2;
- Fig. 4 is a plan view showing a compressor case included in the apparatus of Fig. 1;
- Fig. 5 is a plan view showing an expander case included in the apparatus of Fig. 1;
- Fig. 6 is a perspective view showing the compressor case of Fig. 4;
- Fig. 7 is a perspective view showing the expander case of Fig. 5;
- Fig. 8 is a diagram showing the structure of an orbital partitioning wall included in the apparatus of Fig. 1;
- Fig. 9 is a perspective view showing the orbital partitioning wall of Fig. 8;
- Fig. 10 is a diagram describing an internal structure of a scroll compressor included in the apparatus of Fig. 1;
- Fig. 11 is a diagram showing an internal structure of a scroll expander included in the apparatus of Fig. 1;
- Fig. 12 is a PV (pressure-volume) diagram of a Brayton cycle of the apparatus of Fig. 1;
- Fig. 13 is a diagram showing the positional relationship between a fixed compression scroll and an orbital compression scroll during driving of the Brayton cycle apparatus of Fig. 1;
- Fig. 14 is a diagram showing the positional relationship between a fixed expansion scroll and an orbital expansion scroll during driving of the Brayton cycle apparatus of Fig. 1;
- Fig. 15 is a schematic diagram showing the structure of a Brayton cycle apparatus and an exhaust heat energy recovery apparatus according to a second embodiment of the present invention;
- Fig. 16 is a schematic diagram showing the structure of heat releasing fins of a compressor case included in the apparatus of Fig. 15;
- Fig. 17 is a schematic diagram showing the structure of heat absorbing fins of an expander case included in the apparatus of Fig. 15;
- Fig. 18 is a schematic diagram showing the structure of a Brayton cycle apparatus according to a third embodiment of the present invention;
- Fig. 19 is a diagram showing the appearance of a heat insulation apparatus included in the Brayton cycle apparatus of Fig. 18;
- Fig. 20 is a diagram describing the appearance of the heat insulation apparatus of Fig. 19;
- Fig. 21 is a plan view showing a compressor case included in the apparatus of Fig. 18;
- Fig. 22 is a plan view showing an expander case included in the apparatus of Fig. 18;
- Fig. 23 is a perspective view showing the compressor case of Fig. 21;
- Fig. 24 is a perspective view showing the expander case of Fig. 22;
- Fig. 25 is a perspective view of an orbital partitioning wall included in the apparatus of Fig. 18;
- Fig. 26 is a diagram showing the structure of the orbital partitioning wall of Fig. 25;
- Fig. 27 is a diagram showing the positional relationship between a fixed compression scroll and an orbital compression scroll during driving of the Brayton cycle apparatus of Fig. 18;
- Fig. 28 is a diagram showing the positional relationship between a fixed expansion scroll and an orbital expansion scroll during driving of the Brayton cycle apparatus of Fig. 18;
- Fig. 29 is a graph comparing heat energy conversion efficiency between different heating methods used in the apparatus of Fig. 18;
- Fig. 30 is a schematic diagram showing the structure of a Brayton cycle apparatus according to a fourth embodiment of the present invention; and
- Fig. 31 is a diagram describing the structure of crank mechanisms according to another example of the present invention.
- A first embodiment of the present invention will now be described. Fig. 1 shows a schematic structure of a
Brayton cycle apparatus 1. Aheat insulation apparatus 2 included in theBrayton cycle apparatus 1 is shown in Figs. 2 and 3. Fig. 2(A) is a front view showing theheat insulation apparatus 2, Fig. 2(B) is a rear view, Fig. 3(A) is a right side view, and Fig. 3(B) is a left side view of the same. - The
heat insulation apparatus 2 includes ascroll compressor 4 and ascroll expander 6. Thescroll compressor 4 includes acompressor case 8 shown in the plan view of Fig. 4. A fixedcompression scroll 10 is formed in aninternal space 9 of thecompressor case 8. A compressed workingfluid outlet port 9a is arranged in thecompressor case 8 at a location corresponding to a central portion of the fixedcompression scroll 10. A workingfluid inlet port 9b is arranged at peripheral portion of the fixedcompression scroll 10. Fig. 6 is a perspective view showing thecompressor case 8. - The
scroll expander 6 includes anexpander case 12 shown in the plan view of Fig. 5. A fixedexpansion scroll 14 is formed in aninternal space 13 of theexpander case 12. A compressed workingfluid inlet port 13a is arranged in theexpander case 12 at a location corresponding to a central portion of the fixedexpansion scroll 14. A workingfluid outlet port 13b is arranged at a peripheral portion of the fixedexpansion scroll 14. Fig. 7 is a perspective view showing theexpander case 12. - A circular
orbital recession 8b is arranged inside acontact surface 8a of thecompressor case 8. In the same manner, a circularorbital recession 12b is arranged inside acontact surface 12a of theexpander case 12. When the contact surfaces 8a and 12a come in contact with each other as shown in Fig. 2, thecompressor case 8 is fastened with theexpander case 12 by bolts Bt. The twoorbital recessions heat insulation apparatus 2. The accommodating chamber accommodates anorbital partitioning wall 18. Theorbital partitioning wall 18, which is shown in Fig. 8, in the accommodating chamber orbits while sliding in the accommodating chamber or orbits in a narrow gap formed between theorbital partitioning wall 18 and the cases. - An
orbital compression scroll 20 is formed to project from a compressor-side surface 18a of theorbital partitioning wall 18 shown in Fig. 8(A). Anorbital expansion scroll 22 is formed to project from an expander-side surface 18b of theorbital partitioning wall 18 shown in Fig. 8 (B). Fig. 9 is a perspective view of theorbital partitioning wall 18. - Three crank
mechanisms 24, each of which is formed in to be disk-shaped are rotatably attached to the peripheral portion of theorbital partitioning wall 18 by crankpins 24b. The three crankmechanisms 24 are respectively accommodated in three crankaccommodating units 8c, which are arranged in thecompressor case 8. Each crankmechanism 24 has acrankshaft 24a arranged in its central portion. Thecrankshaft 24a is inserted in acrankshaft reception hole 8d arranged in the center of thecrank accommodating unit 8c and is supported on thecompressor case 8 in a rotatable manner. With thecrank mechanisms 24 being supported on thecompressor case 8 in this manner, the entireorbital partitioning wall 18 is supported on thecompressor case 8 in a manner enabling orbiting. - In the assembled state for the
heat insulation apparatus 2, two of the threecrankshafts 24a project outside theheat insulation apparatus 2 as shown in Figs. 1 and 2. Thefirst crankshaft 24a receives a cranking torque when activating theBrayton cycle apparatus 1 from outside theheat insulation apparatus 2. Thesecond crankshaft 24a outputs a torque generated by theBrayton cycle apparatus 1 out of theheat insulation apparatus 2. The number ofcrankshafts 24a projecting outside theheat insulation apparatus 2 may be changed from one to two. In this case, thesingle crankshaft 24a may function to both input the cranking torque and output the generated torque. - The
orbital compression scroll 20 arranged on one surface (the compressor-side surface 18a (front surface)) of theorbital partitioning wall 18 with the above-described structure is combined with the fixedcompression scroll 10 of the compressor case 8 (Fig. 4 and Fig. 6), and theorbital expansion scroll 22 arranged on the other surface (the expander-side surface 18b (rear surface)) is combined with the fixedexpansion scroll 14 of the expander case 12 (Fig. 5 and Fig. 7). Thecompressor case 8, theexpander case 12, and theorbital partitioning wall 18 are then fastened together by the bolts Bt to form theheat insulation apparatus 2. - Fig. 10 shows the internal structure of the
scroll compressor 4 included in theheat insulation apparatus 2 with this structure. Fig. 10 shows theorbital compression scroll 20 arranged on the compressor-side surface 18a (front surface) of theorbital partitioning wall 18 and thecompressor case 8 that is combined with theorbital compression scroll 20. When thescroll compressor 4 is arranged so that the compressor case 8 (the orbital compression scroll 20) is located at the upper side and the expander case 12 (the orbital expansion scroll 22) is located at the lower side, the part of thecompressor case 8 located above theorbital partitioning wall 18 is indicated by single-dashed lines. Theorbital compression scroll 20 is shown in black. - Fig. 11 shows the internal structure of the
scroll expander 6 included in theheat insulation apparatus 2. Fig. 11 shows theorbital expansion scroll 22 arranged on the expander-side surface 18b (rear surface) of theorbital partitioning wall 18 and theexpander case 12 that is combined with theorbital expansion scroll 22 as viewed through theorbital partitioning wall 18 from the side of thescroll compressor 4. The parts of the fixedexpansion scroll 14 and theorbital expansion scroll 22 located below theorbital partitioning wall 18 are indicated by broken lines. - Referring to Figs. 10 and 11, the
crankshafts 24a rotate clockwise as viewed in the drawings from the side of thecompressor case 8 so that theorbital partitioning wall 18 orbits clockwise. As a result, thescroll compressor 4 realizes a heat-insulation compression stroke in the PV (pressure-volume) diagram of a Brayton cycle of Fig. 12 and thescroll expander 6 realizes a heat-insulation expansion stroke in the PV diagram. - The orbital state will now be described with reference to Fig. 13 and Fig. 14. Fig. 13 shows the
orbital partitioning wall 18 viewed from the side of thecompressor case 8 and the part of thecompressor case 8 located above theorbital partitioning wall 18 in an overlapped state to show the positional relationship between the fixedcompression scroll 10 and theorbital compression scroll 20. In the same manner, Fig. 14 shows theorbital partitioning wall 18 viewed from the side of thecompressor case 8 and the part of theexpander case 12 located below theorbital partitioning wall 18 in an overlapped manner to show the positional relationship between the fixedexpansion scroll 14 and theorbital expansion scroll 22. Theorbital compression scroll 20 and theorbital expansion scroll 22, which are positioned on the front and rear surfaces of theorbital partitioning wall 18 produces the same orbiting action. Thus, the orbiting shown in Fig. 13 and the orbiting shown in Fig. 14 occur simultaneously at the front and rear surfaces of theorbital partitioning wall 18. - The
orbital partitioning wall 18 orbits clockwise as viewed from the side of thescroll compressor 4 as described above. Thus, the position of theorbital compression scroll 20 with respect to the fixedcompression scroll 10 changes sequentially from the states (1) to (8) shown in Fig. 13. As a result, an initial volume Va1 of a working fluid (atmospheric gas in this case) is introduced into theinternal space 9 of thecompressor case 8 through the workingfluid inlet port 9b, and the working fluid flows toward the center of thecompressor case 8 while gradually reducing its volume. When the volume of the working fluid reaches a final volume Va2 (Val > Val) at the central portion of thecompressor case 8, the compressed workingfluid outlet port 9a opens so that the compressed working fluid is fed from the compressed workingfluid outlet port 9a to the heating device 30 (Fig. 1). - During the orbiting of the
orbital compression scroll 20, orbiting simultaneously occurs in thescroll expander 6. The position of theorbital expansion scroll 22 with respect to the fixedexpansion scroll 14 changes sequentially from the states (1) to (8) shown in Fig. 14. As a result, an initial volume Vb2 of the working fluid heated in theheating device 30 is introduced from the compressed workingfluid inlet port 13a into theinternal space 13 of theexpander case 12, and flows toward the peripheral side of theexpander case 12 while gradually increasing its volume. When the volume of the working fluid reaches a final volume Vb1 (Vb1 > Vb2) at the peripheral portion of theexpander case 12, the working fluid is released from restriction imposed by the fixedexpansion scroll 14 and theorbital expansion scroll 22, and is discharged outside theexpander case 12 from the workingfluid outlet port 13b. - The dimensions of the fixed
expansion scroll 14 and theorbital expansion scroll 22 in the axial direction are greater than the dimensions of the fixedcompression scroll 10 and theorbital compression scroll 20 in the axial direction, and the scrolls are designed to satisfy the relationship Va1 < Vb1 and Va2 < Vb2. - The
heat insulation apparatus 2 and theheating device 30 with the above-described structures are combined together to complete theBrayton cycle apparatus 1 shown in Fig. 1. Theheating device 30 uses a double pipe and includes a heatsource flow passage 30a, which functions as an inner passage, and anouter passage 30b, which is arranged to surround theflow passage 30a. Theheating device 30 has the working fluid flow through theouter passage 30b. The working fluid flowing through theouter passage 30b exchanges heat with fluid flowing through the heatsource flow passage 30a through the pipe wall (flow passage wall) of the heatsource flow passage 30a. When an exhaust pipe of an internal combustion engine is used as the heatsource flow passage 30a, exhaust heat energy of the internal combustion engine is recovered. In this case, the exhaust flows through the heatsource flow passage 30a and the heat of the exhaust is transferred to the working fluid (air) flowing through theouter passage 30b. - The values of the volumes Va1, Va2, Vb1, and Vb2 above are designed to maximize the heat conversion efficiency of the
Brayton cycle apparatus 1 by considering the working fluid temperature at the workingfluid inlet port 9b, the heat exchanger efficiency in theheating device 30, the working fluid temperature at the compressed workingfluid inlet port 13a, and the heat insulation efficiency in thescroll compressor 4 and thescroll expander 6. - The first embodiment has the advantages described below.
- (1) Unlike the gas turbine Brayton cycle apparatus of the prior art, the
Brayton cycle apparatus 1 of the preferred embodiment uses thescroll compressor 4 and thescroll expander 6. This simplifies and downsizes the structure.
In particular, in theheat insulation apparatus 2, the working fluid is moved, compressed, and expanded inside thescroll compressor 4 and thescroll expander 6 in spaces partitioned and sealed by the combination of the fixed scrolls 10 and 14 and theorbital scrolls
The external energy source is only required to transfer heat to the working fluid via the pipe wall of theflow passage 30a and exchange heat with the working fluid. This downsizes the external energy source. Further, the pressure of the energy source itself causes no problem, and the back pressure of the energy source including the exhaust is unaffected.
As a result, theBrayton cycle apparatus 1 of the present embodiment converts heat energy to kinetic energy efficiently without increasing the back pressure of the energy source. Thus, when theBrayton cycle apparatus 1 of the present embodiment is applied to an internal combustion engine, the apparatus recovers the exhaust heat energy efficiently without increasing the exhaust back pressure of the internal combustion engine. - (2) The
orbital compression scroll 20 of thescroll compressor 4 and theorbital expansion scroll 22 of thescroll expander 6 are respectively arranged at opposite sides of theorbital partitioning wall 18, which is orbited by thecrankshafts 24a. Thecompressor case 8, in which the fixedcompression scroll 10 is formed, is set on theorbital compression scroll 20 side of theorbital partitioning wall 18 to come in contact with theorbital partitioning wall 18 in a slidable manner or to face theorbital partitioning wall 18 with a narrow gap therebetween. Theorbital compression scroll 20 and the fixedcompression scroll 10 are combined to form thescroll compressor 4. Theexpander case 12, in which the fixedexpansion scroll 14 is formed, is set on theorbital expansion scroll 22 side of theorbital partitioning wall 18 to come in contact with theorbital partitioning wall 18 in a slidable manner or to face theorbital partitioning wall 18 with a narrow gap therebetween. Theorbital expansion scroll 22 and the fixedexpansion scroll 14 are combined to form thescroll expander 6.
Thescroll compressor 4 and thescroll expander 6 are formed in this manner so that theBrayton cycle apparatus 1 is further simplified and downsized. - (3) As described above, the
orbital partitioning wall 18 covers theexpander case 12. Thus, theorbital partitioning wall 18 is exposed to the high-temperature working fluid that is introduced into thescroll expander 6. However, thecompressor case 8 is enabled to contact theorbital partitioning wall 18 from the side opposite to theexpander case 12. As a result, heat transferred from thescroll expander 6 to theorbital partitioning wall 18 is removed by thecompressor case 8 and released into the atmosphere.
The heat releasing effect of thecompressor case 8 prevents theorbital partitioning wall 18 from being heated to a high temperature. As a result, theorbital partitioning wall 18 is prevented from being deformed by heat, and the dimensional accuracy of theorbital partitioning wall 18 is maintained. This prevents the working fluid from leaking from theheat insulation apparatus 2 and prevents the friction coefficient during orbiting of theorbital partitioning wall 18 from becoming large. As a result, high energy conversion efficiency is maintained.
Thus, theorbital partitioning wall 18 and thescroll compressor 4 in particular may be made of a light alloy with a low heat resistance. This contributes to further decreasing the weight of theBrayton cycle apparatus 1. - (4) The
scroll compressor 4 uses the atmospheric gas (air) drawn through the workingfluid inlet port 9b as the working fluid, and thescroll expander 6 releases the expanded working fluid from the workingfluid outlet port 13b into the atmosphere. In this manner, the atmospheric gas is used as the working fluid. This eliminates the need for an apparatus for releasing heat of the working fluid and further simplifies and downsizes the structure of theBrayton cycle apparatus 1. - A second embodiment of the present invention will now be described. In the present embodiment, a
Brayton cycle apparatus 51 with the structure shown in Fig. 15 is used to collect exhaust heat energy of an internal combustion engine Eng that is mounted on a vehicle. Aheat insulation apparatus 52 is formed by ascroll compressor 54 and ascroll expander 56. The internal structures of thescroll compressor 54 and thescroll expander 56 are the same as the structures of thescroll compressor 4 and thescroll expander 6 described in the first embodiment. - The present embodiment differs from the first embodiment in the following points. More specifically, a large number of
heat releasing fins 58b, which are formed as projections, are arranged on anend surface 58a of acompressor case 58 as shown in Fig 15 and Fig. 16. Theheat releasing fins 58b are used to discharge from thecompressor case 58 heat, which is transferred from the internalorbital partitioning wall 18 to thecompressor case 58. More specifically, theheat releasing fins 58b improve the releasing efficiency of the heat received from the high-temperature scroll expander 56 by theorbital partitioning wall 18 through thecompressor case 58. - Further, a large number of
heat absorbing fins 62b, which are formed as projections, are also arranged on anend surface 62a of anexpander case 62 as shown in Fig 15 and Fig. 17. Acover 62c is arranged on theend surface 62a of theexpander case 62. Thecover 62c covers a compressed workingfluid inlet port 63a and theheat absorbing fins 62b to define aheat absorption chamber 62d. The working fluid heated by aheating device 80 is introduced into theheat absorption chamber 62d. Thus, the working fluid introduced into theheat absorption chamber 62d heats theheat absorbing fins 62b. The compressed workingfluid inlet port 63a that opens into theheat absorption chamber 62d absorbs the heated working fluid. The working fluid introduced into theheat absorption chamber 62d heats the working fluid inside theexpander case 62 through theend surface 62a of the wall of theheat absorption chamber 62d. Thus, a pressure decrease caused by expansion of the working fluid in thescroll expander 56 is small. As a result, even when the expansion coefficient of thescroll expander 56 is high, the working fluid can be set in an atmospheric pressure state and discharged from the workingfluid outlet port 63b. This enables theBrayton cycle apparatus 51 to collect the exhaust heat energy more efficiently. - The
heating device 80 includes two passages, namely, apassage 80c for having the working fluid pass through the entire length of adouble pipe 80b and apassage 80d for having the working fluid pass through only part of thedouble pipe 80b. The passage distribution state of the compressed working fluid supplied from thescroll compressor 54 is adjustable using adistribution valve 80e. The distribution ratio of thepassages temperature sensor 81 arranged at an opening of the compressed workingfluid inlet port 63a becomes equal to a predetermined reference temperature. More specifically, the distribution ratio of thedistribution valve 80e is adjusted in a manner that the temperature of the working fluid becomes equal to a reference temperature that is appropriate for starting expansion in thescroll expander 56 when the working fluid reaches the compressed workingfluid inlet port 63a after heat is absorbed by theheat absorbing fins 62b. -
Crankshafts 74a of theBrayton cycle apparatus 51 are rotated when the internal combustion engine Eng starts driving theBrayton cycle apparatus 51. However, after the driving of theBrayton cycle apparatus 51 starts, thecrankshafts 74a rotate independently of the output of the internal combustion engine Eng by using heat energy of the exhaust that passes through theheating device 80. Thus, thecrankshafts 74a need to be disconnected from the internal combustion engine Eng. For this purpose, anelectromagnetic clutch 92 is arranged between anoutput shaft 64 of the internal combustion engine Eng and thecrankshafts 74a of theBrayton cycle apparatus 51. - The distribution ratio control of the
distribution valve 80e and the engagement/disengagement control of the electromagnetic clutch 92 are executed by an electronic control unit (ECU) 94 based on the driving state of the internal combustion engine Eng. - For example, the
electromagnetic clutch 92 is set in a disengaged state before the internal combustion engine Eng is started. At the timing when the internal combustion engine exhaust temperature reaches a sufficiently high temperature after the internal combustion engine Eng is started, theelectromagnetic clutch 92 is engaged so that thecrankshafts 74a of theBrayton cycle apparatus 51 are rotated based on an output of the internal combustion engine Eng. TheECU 94 drives avalve actuator 80f and adjusts thedistribution valve 80e in a manner that the working fluid temperature detected by thetemperature sensor 81 is adjusted to, for example, 350°C. - Afterwards, the
ECU 94 disengages theelectromagnetic clutch 92. As a result, thecrankshafts 74a of theBrayton cycle apparatus 51 rotate independently to rotate an apparatus for recovering the exhaust heat energy, or agenerator 96 in this case. As a result, the exhaust heat energy is recovered as electric energy and used as a vehicle power supply or stored in a battery. - With the above-described structure, the
expander case 62, which directly comes in contact with the high-temperature working fluid, is made of a heat-resistant material (e.g. an iron alloy such as cast iron). Thecompressor case 58, through which the working fluid flows with a relatively low temperature, is made of a high heat-conductive material (particularly a light alloy such as an aluminum alloy). Theorbital partitioning wall 18 is made of a high heat-conductive material so that theorbital partitioning wall 18 is cooled by transferring heat to thecompressor case 58. - The second embodiment described above has the advantages described below.
- (1) The
heat releasing fins 58b are formed on thecompressor case 58. Thus, thecompressor case 58 can easily release heat into the atmosphere. This strengthens advantage (3) described in the first embodiment. - (2) The
cover 62c covers theend surface 62a of theexpander case 62 and defines theheat absorption chamber 62d. As described above, the working fluid expanded in thescroll expander 56 is heated by the wall of theexpander case 62 having theend surface 62a. Further, theheat absorbing fins 62b are formed on theend surface 62a. Theheat absorbing fins 62b enhance heat conductivity of theend surface 62a, and enable theBrayton cycle apparatus 51 to convert heat energy to kinetic energy further efficiently without complicating the structure of theBrayton cycle apparatus 51. - (3) The exhaust pipe is formed by the
double pipe 80b. Theheating device 80 is formed as a heat exchanger for exchanging heat between the high-temperature gas (the exhaust of the internal combustion engine Eng in this case) and the working fluid. TheBrayton cycle apparatus 51 recovers the exhaust heat energy as kinetic energy. Thus, theBrayton cycle apparatus 51 converts the exhaust heat energy to kinetic energy more efficiently without increasing the exhaust back pressure of the internal combustion engine Eng. - (4) A light alloy may be used as a material for the
compressor case 58 and theorbital partitioning wall 18 as described above. This reduces the weight of the entireBrayton cycle apparatus 51. When theBrayton cycle apparatus 51 is applied to an internal combustion engine that is mounted on a vehicle, theBrayton cycle apparatus 51 improves fuel efficiency of the engine. - (5) Advantages (1), (2), and (4) of the first embodiment are obtained.
- A third embodiment of the present invention will now be described. Fig. 18 is a schematic diagram showing the structure of a
Brayton cycle apparatus 101. Aheat insulation apparatus 102 included in theBrayton cycle apparatus 101 is shown in Figs. 19 and 20. Fig. 19(A) is a front view showing theheat insulation apparatus 102, Fig. 19(B) is a rear view, Fig. 20(A) is a right side view, and Fig. 20(B) is a left side view of the same. - In the same manner as the first embodiment, a working
fluid inlet port 109b projects from a peripheral portion of ascroll compressor 104 and a workingfluid outlet port 113b projects from a peripheral portion of ascroll expander 106. - Unlike the first embodiment, a compressed working
fluid outlet port 9a is not arranged in acompressor case 108 and a compressed workingfluid inlet port 13a is not arranged in anexpander case 112 as shown in Figs. 21 to 24. Fig. 21 is a plan view showing thecompressor case 108, Fig. 22 is a plan view showing theexpander case 112, Fig. 23 is a perspective view showing thecompressor case 108, and Fig. 24 is a perspective view showing theexpander case 112. - Instead of the compressed working
fluid outlet port 9a and the compressed workingfluid inlet port 13a, a through-hole 118c is formed in a central portion of anorbital partitioning wall 118 as shown in Figs. 25 and 26. Fig. 25 is a perspective view showing theorbital partitioning wall 118, Fig. 26(A) is a plan view of theorbital partitioning wall 118 showing a compressor-side surface 118a of theorbital partitioning wall 118, and Fig. 26(B) is a rear view of theorbital partitioning wall 118 showing an expander-side surface 118b of theorbital partitioning wall 118. - In the
scroll compressor 104, theorbital partitioning wall 118 orbits as shown in the states (1) to (8) in Fig. 27. Anorbital compression scroll 120 of theorbital partitioning wall 118 moves relative to a fixedcompression scroll 110 of thecompressor case 108 so that the working fluid introduced from the workingfluid inlet port 109b into thescroll compressor 104 is compressed and reaches the through-hole 118c formed in the central portion of theorbital partitioning wall 118. Fig. 27 shows theorbital partitioning wall 118 viewed from the side of thecompressor case 108 and thecompressor case 108 located above theorbital partitioning wall 118 in an overlapped manner to describe the positional relationship between the fixedcompression scroll 110 and theorbital compression scroll 120. Accordingly, the left and right sides shown in Fig. 27 are reversed from the state shown in Fig. 21. - The working fluid in a compressed state passes through the through-
hole 118c so that the working fluid is immediately introduced into thescroll expander 106 from thescroll compressor 104 as indicated by a broken line Ap in Fig. 18. - In the
scroll expander 106, theorbital partitioning wall 118 orbits as shown in (1) to (8) in Fig. 28. Anorbital expansion scroll 122 of theorbital partitioning wall 118 moves relative to a fixedexpansion scroll 114 of theexpander case 112 so that the working fluid introduced through the through-hole 118c into thescroll expander 106 expands and reaches the workingfluid outlet port 113b. - Fig. 28 shows the
orbital partitioning wall 118 viewed from the side of thecompressor case 108 and the part of theexpander case 112 located below theorbital partitioning wall 118 in an overlapped manner to show the positional relationship between the fixedexpansion scroll 114 and theorbital expansion scroll 122. - The
expander case 112 comes in contact with or is joined with aflow passage 130a (Fig. 18) as a heat source. Theexpander case 112 exchanges heat with a fluid flowing through theflow passage 130a through a pipe wall (flow passage wall) of theflow passage 130a. Thus, the working fluid expands while being heated by the heat transferred to the working fluid that comes in contact with theexpander case 112 or the fixedexpansion scroll 114. - The
orbital partitioning wall 118 with this structure orbits clockwise in Fig. 27 and 28 to realize a heat-insulation compression stroke, an isobaric heating stroke, and a heat-insulation expansion stroke in the PV diagram of the Brayton cycle shown in Fig. 12. - In the above-described structure, the
expander case 112 comes in contact with the high-temperature flow passage 130a and is heated to a high temperature by the heat transfer from theflow passage 130a. As a result, the working fluid is heated by theexpander case 112 and the fixedexpansion scroll 114. Thus, theexpander case 112 and the fixedexpansion scroll 114 are made of a heat-resistant material (e.g. an iron alloy such as cast iron). Theexpander case 112 and the fixedexpansion scroll 114 may be made of a light alloy such as an aluminum alloy. Because the temperature of the working fluid in thecompressor case 108 is relatively low, thecompressor case 108 is made of a high heat-conductive material (particularly a light alloy such as an aluminum alloy). Theorbital partitioning wall 118 is made of a high heat-conductive material so that theorbital partitioning wall 18 may be cooled by transferring heat to thecompressor case 58. - With the above-described structure, heat energy transferred from the
flow passage 130a to theexpander case 112 is converted to rotation energy ofcrankshafts 124a. - Fig. 29 shows a graph comparing the heat energy conversion efficiency experiments in the present embodiment case, in which the
expander case 112 is heated, with the heat energy conversion efficiency experiments in the first embodiment case, in which theexpander case 112 is not heated and the working fluid is introduced into thescroll expander 106 after the working fluid is heated separately. To correctly indicate the difference in the torque gain in thescroll expander 106 between the different heating methods, this graph compares the output torque of thecrankshafts 124a when theexpander case 112 is heated with an output torque of thecrankshafts 124a when the working fluid introduced into theexpander case 112 is heated in the state in which thescroll expander 106 is disconnected from theBrayton cycle apparatus 101. The horizontal axis of the graph indicates a temperate increase difference ΔT, which is the difference between a temperature increase of theexpander case 112 and a temperature increase of the working fluid occurring via heating. The vertical axis of the graph indicates a torque gain (Nm). - As shown in the graph, the heat energy conversion efficiency is higher when the
expander case 112 made of an aluminum alloy is heated than when the working fluid is heated. When theexpander case 112 is made of cast iron, clearance for the mechanism of thescroll expander 106 may be reduced and the heat energy conversion efficiency is further increased. - The third embodiment has the advantages described below.
- (1) Advantages (1) to (4) of the first embodiment are obtained.
- (2) The
Brayton cycle apparatus 101 of the present embodiment heats the working fluid in thescroll expander 106 using the heat transferred from the heat source (theflow passage 130a) without using a heating device for separately heating the working fluid. - Thus, the compressed working fluid passage has a simple structure. The compressed working fluid passage is actually realized by the through-
hole 118c formed in theorbital partitioning wall 118. - Further, the
expander case 112 and the fixedexpansion scroll 114, which are the components of thescroll expander 106, are used to transfer heat to the working fluid and heat the working fluid. As a result, theBrayton cycle apparatus 101 is further simplified and downsized. - A fourth embodiment of the present invention will now be described. As shown in Fig. 30, a
Brayton cycle apparatus 201 of the present embodiment differs from the structure of the first embodiment shown in Fig. 1 in that aheat insulator 201a is arranged to cover theexpander case 12 in theheat insulation apparatus 2 and keep theexpander case 12 warm. The other parts of theBrayton cycle apparatus 201 are the same as the structure in the first embodiment. Thus, the components of theBrayton cycle apparatus 201 that are the same as the components in the first embodiment are denoted by the same reference numerals. - The fourth embodiment has the advantages described below.
- (1) Advantages (1) to (4) of the first embodiment are obtained.
- (2) The
heat insulator 201a keeps the wall surface of theexpander case 12 warm. This prevents heat from being released from theexpander case 12 outside through heat transfer from theexpander case 12 when the working fluid is expanded in thescroll expander 6 in a heat-insulated state. - In this manner, the wall surface of the
expander case 12 is kept warm to prevent heat energy from leaking from thescroll expander 6. As a result, the heat energy is converted to kinetic energy more efficiently. - The above embodiments may be modified in the following forms.
- (a) The Brayton cycle apparatus shown in Fig. 1, Fig. 18, or Fig. 30 may be used as an exhaust heat energy recovery apparatus for an internal combustion engine instead of the Brayton cycle apparatus used in the second embodiment.
In the above embodiments, the Brayton cycle apparatus used to collect exhaust heat energy from an internal combustion engine uses the scroll compressor and the scroll expander. Another compressor, such as a screw compressor, a vane compressor, or a turbo compressor, may be used instead of the scroll compressor. A turbine compressor may be used instead of the scroll expander.
A positive-displacement compressor and a positive-displacement expander may be used instead of the scroll compressor and the scroll expander. The Brayton cycle apparatus may be formed by combining a positive-displacement compressor for compressing a working fluid and a scroll expander. In this case, the scroll expander may operate in cooperation with the operation of the positive-displacement compressor. - (b) The
orbital partitioning wall 18 is supported by the three crankmechanisms 24 as shown in Fig. 8. However, the present invention should not be limited to this structure. Theorbital partitioning wall 18 may be supported by two crankmechanisms 24 or may be supported by four or more crankmechanisms 24. Although each crankmechanism 24 is circular, each crankmechanism 24 may include abalancer 100 as shown in Fig. 31 to improve the vibration reducing effect during driving of the Brayton cycle apparatus. The same applies to theorbital partitioning wall 118 in the third embodiment. - (c) Although the
heat releasing fins 58b and theheat absorbing fins 62b are formed as projections as shown in Figs. 16 and 17, theheat releasing fins 58b and theheat absorbing fins 62b may be formed as flat plates or bent plates. - (d) The
heat releasing fins 58b shown in Figs. 15 and 16 may be arranged on thecompressor case 108 in the third embodiment. This structure enables the heat of thecompressor case 108 to be easily released into the atmosphere and strengthens advantage (3) described in the first embodiment.
In the third embodiment, theexpander case 112 comes in contact with or joined together with theflow passage 130a, which functions as a heat source, as shown in Fig. 18 to exchange heat through the pipe wall (flow passage wall) of theflow passage 130a. However, theexpander case 112 may be formed to have a flow passage through which the exhaust flows, and the exhaust may be guided to this flow passage.
In the third embodiment, a peripheral portion of theexpander case 112 excluding parts that are in contact with or joined with theflow passage 130a may be covered by a heat insulator to keep theexpander case 112 warm. - (e) In the above embodiments, the working fluid inlet port and the working fluid outlet port are open to the atmosphere and the atmospheric gas is used as the working fluid. However, the passage of the working fluid may be closed, and a gas other than the atmospheric gas may be used as the working fluid. In this case, it is preferable that a heat releasing apparatus be arranged.
- (f) In the above embodiments, the orbital compression scroll and the orbital expansion scroll are formed to sandwich the orbital partitioning wall to operate the expander in cooperation with movement of the compressor.
The synchronous movement intends to mean that the compressor is linked to the expander in a manner that the compressor and the expander move in a unified manner. Thus, operating the expander in cooperation with the movement of the compressor is equivalent to operating the compressor in cooperation with the operation of the expander. Unlike the above embodiments, this compressor does not have to be directly connected to the expander. Particularly in the first, second, and fourth embodiments, a shaft or a gear may be arranged between the compressor and the expander to operate the expander in cooperation with the operation of the compressor.
Claims (23)
- A Brayton cycle apparatus, being characterized by:a scroll compressor for compressing a working fluid;a scroll expander for operating in cooperation with an orbiting action of the scroll compressor, wherein the working fluid compressed by the scroll compressor is fed to the scroll expander; anda heating device for heating the compressed working fluid fed from the scroll compressor to the scroll expander.
- The Brayton cycle apparatus according to claim 1, characterized in that:the scroll compressor includes a compressor case, a fixed compression scroll formed in the compressor case, and an orbital compression scroll combined with the fixed compression scroll to come in contact with the compressor case in a slidable manner or to face the compressor case with a narrow gap therebetween; andthe scroll expander includes an expander case, a fixed expansion scroll formed in the expander case, and an orbital expansion scroll combined with the fixed expansion scroll to come in contact with the expander case in a slidable manner or to face the expander case with a narrow gap therebetween, the Brayton cycle apparatus further being characterized by:an orbital partitioning wall for generating an orbiting action, wherein the orbital compression scroll and the orbital expansion scroll are arranged on the orbital partitioning wall in a manner that the orbital compression scroll and the orbital expansion scroll are located at opposite sides of the orbital partition.
- The Brayton cycle apparatus according to claim 2, characterized in that the scroll compressor releases heat transferred from the scroll expander to the orbital partitioning wall in the atmosphere through the compressor case.
- The Brayton cycle apparatus according to claim 2 or 3, characterized in that the expander case includes a heat absorption chamber into which the working liquid introduced into the scroll expander prior to expansion is introduced, the heat absorption chamber being partitioned by a wall for heating the working liquid when the working liquid is expanding.
- The Brayton cycle apparatus according to any one of claims 1 to 4, characterized in that the scroll compressor uses atmospheric gas as the working fluid, compresses the atmospheric gas, and releases the expanded working fluid into the atmosphere.
- The Brayton cycle apparatus according to any one of claims 1 to 5, characterized in that the heating device is a heat exchanger for transferring external heat to the working fluid through heat exchange.
- The Brayton cycle apparatus according to any one of claims 1 to 6, characterized in that a wall surface of the expander is kept warm.
- A Brayton cycle apparatus being characterized by:a positive-displacement compressor for compressing a working fluid;a scroll expander for generating an orbiting action in cooperation with a compression action of the positive-displacement compressor, wherein the working fluid compressed by the positive-displacement compressor is fed to the scroll expander; anda heating device for heating the compressed working fluid fed from the positive-displacement compressor to the scroll expander.
- The Brayton cycle apparatus according to claim 8, characterized in that a wall surface of the expander is kept warm.
- An exhaust heat energy recovery apparatus for an internal combustion engine for recovering exhaust heat energy of the internal combustion engine as kinetic energy, wherein the exhaust heat energy recovery apparatus incorporates a Brayton cycle apparatus, the exhaust heat energy recovery apparatus being characterized in that the Brayton cycle apparatus includes:a compressor for compressing a working fluid; andan expander to which the working fluid compressed by the compressor is fed, wherein the compressed working fluid fed from the compressor to the expander is heated by heat transferred from a flow passage wall of an exhaust flow passage of the internal combustion engine.
- The exhaust heat energy recovery apparatus according to claim 10, characterized in that:the compressor is a scroll compressor and the expander is a scroll expander; andthe Brayton cycle apparatus includes a heating device for heating the compressed working fluid that is fed from the scroll compressor to the scroll expander, and the heating device is a heat exchanger that is arranged to contact exhaust of the internal combustion engine to transfer heat from the flow passage wall to the working fluid.
- The exhaust heat energy recovery apparatus according to claim 10 or 11, wherein the exhaust flow passage is formed as a double pipe having an inner passage and an outer passage, and exhaust flowing through one of the inner passage and the outer passage exchanges heat with the working fluid flowing through the other one of the inner passage and the outer passage.
- The exhaust heat energy recovery apparatus according to claim 10, characterized in that:the compressor is a scroll compressor including a compressor case, a fixed compression scroll formed in the compressor case, and an orbital compression scroll combined with the fixed compression scroll to come in contact with the compressor case in a slidable manner or to face the compressor case with a narrow gap therebetween;the expander is a scroll expander including an expander case, a fixed expansion scroll formed in the expander case, and an orbital expansion scroll combined with the fixed expansion scroll to come in contact with the expander case in a slidable manner or to face the expander case with a narrow space therebetween, the Brayton cycle apparatus further being characterized by:a heating device, for heating the compressed working fluid fed from the scroll compressor to the scroll expander with heat from the flow passage wall, and an orbital partitioning wall for generating an orbiting action, wherein the orbital compression scroll and the orbital expansion scroll are arranged on the orbital partitioning wall in a manner that the orbital compression scroll and the orbital expansion scroll are located at opposite sides of the orbital partition; andwherein the orbital partitioning wall and the compressor case are made of a high heat-conductive material, and the expander case is made of a heat-resistant material.
- The exhaust heat energy recovery apparatus according to claim 13, characterized in that an aluminum alloy is used as the high heat-conductive material, and an iron alloy is used as the heat-resistant material.
- The exhaust heat energy recovery apparatus according to any one of claims 10 to 14, characterized in that a wall surface of the expander is kept warm.
- A Brayton cycle apparatus being characterized by:a scroll expander including an orbital expansion scroll and a fixed expansion scroll combined with the orbital expansion scroll;a compressor for compressing a working fluid in cooperation with an orbiting action of the orbital expansion scroll;a compressed working fluid flow passage for supplying the compressed working fluid from the compressor to the scroll expander; anda heat source for heating the working fluid in the scroll expander through heat transfer.
- The Brayton cycle apparatus according to claim 16, characterized in that the compressor is a positive-displacement compressor.
- The Brayton cycle apparatus according to claim 16 or 17, characterized in that:the scroll expander has a case fixed to the fixed expansion scroll; andthe heat source comes in contact with the case and thereby heating the working fluid in the scroll expander through the case or the fixed expansion scroll.
- A Brayton cycle apparatus being characterized by:an orbital partitioning wall having a first surface on which an orbital compression scroll is formed and a second surface on which an orbital expansion scroll is formed;a scroll compressor including the orbital compression scroll and a fixed compression scroll combined with the orbital compression scroll;a scroll expander including the orbital expansion scroll and a fixed expansion scroll combined with the fixed expansion scroll;a compressed working fluid passage for supplying a compressed working fluid from the scroll compressor to the scroll expander; anda heat source for heating the working fluid in the scroll expander through heat transfer.
- The Brayton cycle apparatus according to claim 19, characterized in that the scroll compressor has a compressor case arranged on the first surface, the scroll expander has an expander case arranged on the second surface, the compressed working fluid passage has a through-hole formed in the orbital partition, and the through-hole communicates the interior of the compressor case with the interior of the expander case.
- The Brayton cycle apparatus according to claim 19, characterized in that:the scroll expander has a case fixed to the fixed expansion scroll; andthe heat source comes in contact with the case thereby heating the working fluid in the scroll expander through the case or the fixed expansion scroll.
- An exhaust heat energy recovery apparatus for recovering exhaust heat energy discharged from an internal combustion engine through an exhaust flow passage as kinetic energy, the exhaust heat energy recovery apparatus being
characterized by:a Brayton cycle apparatus including an expander to which a working fluid is fed, wherein the working fluid fed to the expander is heated by heat transferred from a flow passage wall of the exhaust flow passage. - The exhaust heat energy recovery apparatus according to claim 22, characterized in that:the expander is a scroll expander including an orbital expansion scroll and a fixed expansion scroll combined with the orbital expansion scroll, the Brayton cycle apparatus further including:a compressor operated in cooperation with an orbiting action of the orbital expansion scroll to compress the working fluid;a compressed working fluid passage for supplying the working fluid from the compressor to the scroll expander; anda heat source for heating the working fluid in the scroll expander through heat transfer, wherein an exhaust of the internal combustion engine is used as the heat source.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2004044967 | 2004-02-20 | ||
PCT/JP2005/001299 WO2005080756A1 (en) | 2004-02-20 | 2005-01-25 | Brayton cycle device and exhaust heat energy recovery device for internal combustion engine |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1717413A1 true EP1717413A1 (en) | 2006-11-02 |
EP1717413A4 EP1717413A4 (en) | 2008-04-23 |
Family
ID=34879366
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP05704295A Withdrawn EP1717413A4 (en) | 2004-02-20 | 2005-01-25 | Brayton cycle device and exhaust heat energy recovery device for internal combustion engine |
Country Status (4)
Country | Link |
---|---|
US (1) | US20070277522A1 (en) |
EP (1) | EP1717413A4 (en) |
JP (1) | JPWO2005080756A1 (en) |
WO (1) | WO2005080756A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102012019040A1 (en) * | 2012-09-28 | 2014-04-03 | Harald Teinzer | Scroll motor for e.g. aircraft engine, has heating chamber arranged between scroll compressor and scroll expander, where flow of gas is converted into kinetic energy in scroll expander and supplied to drive shaft |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2096026B1 (en) * | 2006-12-09 | 2014-10-29 | National University Corporation Yokohama National University | Ship buoyancy control system |
JP6023507B2 (en) * | 2012-08-09 | 2016-11-09 | 日野自動車株式会社 | Brayton cycle engine |
JP6125216B2 (en) * | 2012-12-14 | 2017-05-10 | サンデンホールディングス株式会社 | Scroll type fluid machinery |
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WO1979001071A1 (en) * | 1978-05-15 | 1979-12-13 | Purification Sciences Inc | Engine |
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- 2005-01-25 EP EP05704295A patent/EP1717413A4/en not_active Withdrawn
- 2005-01-25 JP JP2006510176A patent/JPWO2005080756A1/en active Pending
- 2005-01-25 US US10/589,333 patent/US20070277522A1/en not_active Abandoned
- 2005-01-25 WO PCT/JP2005/001299 patent/WO2005080756A1/en active Application Filing
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JP2001271765A (en) * | 2000-03-29 | 2001-10-05 | Seiko Instruments Inc | Scroll type fluid machine |
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Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102012019040A1 (en) * | 2012-09-28 | 2014-04-03 | Harald Teinzer | Scroll motor for e.g. aircraft engine, has heating chamber arranged between scroll compressor and scroll expander, where flow of gas is converted into kinetic energy in scroll expander and supplied to drive shaft |
DE102012019040B4 (en) * | 2012-09-28 | 2014-08-14 | Harald Teinzer | Scroll engine |
Also Published As
Publication number | Publication date |
---|---|
WO2005080756A1 (en) | 2005-09-01 |
EP1717413A4 (en) | 2008-04-23 |
JPWO2005080756A1 (en) | 2009-05-07 |
US20070277522A1 (en) | 2007-12-06 |
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