JPWO2005080756A1 - Brayton cycle device and exhaust heat energy recovery device for internal combustion engine - Google Patents

Abstract

An exhaust heat energy recovery device for an internal combustion engine that can efficiently recover exhaust heat energy without increasing the exhaust back pressure of the internal combustion engine, and a Brayton cycle device that can be used for such an exhaust heat energy recovery device . The Brayton cycle apparatus 1 uses a scroll compressor 4 and a scroll expander 6. Therefore, the structure of the Brayton cycle apparatus 1 is simple and can be miniaturized. The working fluid is compressed by the scroll compressor 4 and expanded by the scroll expander 6 in a state of being divided and sealed by a combination of the fixed scroll and the orbiting scroll. For this reason, the conversion efficiency from thermal energy to kinetic energy is also excellent. Further, heat is transferred from the exhaust to the working fluid through the tube wall of the flow path 30a and the expander case 12 of the scroll expander 6, and heat exchange is performed. Therefore, the Brayton cycle apparatus 1 can be further reduced in size and does not affect the back pressure of an energy source such as exhaust.

Description

  The present invention relates to an apparatus for realizing a Brayton cycle and an exhaust heat energy recovery apparatus for an internal combustion engine using the Brayton cycle.

In order to improve the fuel consumption of an internal combustion engine, a device for recovering exhaust energy discharged from the engine after fuel combustion is known. For example, a Rankine cycle device is mounted on a vehicle together with an internal combustion engine. The evaporator disposed in the Rankine cycle apparatus heats water inside the apparatus by exhaust heat energy to generate high-temperature and high-pressure steam. Power is generated by an expander using this steam (see, for example, Japanese Patent Application Laid-Open No. 2003-120281).
In addition to this, a heat-utilizing engine such as a Stirling engine is combined with an internal combustion engine (for example, see Japanese Patent Laid-Open No. 2001-99003), or exhaust is directly introduced into a scroll type expander (for example, Japanese Patent Laid-Open No. 2003-138933). For example, it has been proposed to recover exhaust energy.
However, an apparatus such as the aforementioned Japanese Patent Application Laid-Open No. 2003-120281 requires an evaporator, an expander, a condenser, a pump, and water as a working fluid, so that the volume and weight of the apparatus must be increased. Absent. Therefore, even if exhaust heat energy can be recovered efficiently, the driving energy of the device and the vehicle weight may be excessive, and the fuel efficiency may hardly be improved. The same applies to the case of using a heat-utilizing engine such as a Stirling engine as described in JP-A-2001-99003.
Further, in Japanese Patent Application Laid-Open No. 2003-138933, exhaust is introduced into the scroll expander, and therefore, the exhaust back pressure of the internal combustion engine is inevitably increased and the engine output is decreased.
SUMMARY OF THE INVENTION An object of the present invention is to provide an exhaust thermal energy recovery device for an internal combustion engine that can efficiently recover exhaust thermal energy without increasing the exhaust back pressure of the internal combustion engine, and such an exhaust thermal energy recovery device. An object of the present invention is to provide a Brayton cycle apparatus that can be used in the future.
The means for achieving the above object and its advantages will be described below.
The present invention provides a Brayton cycle apparatus. This Brayton cycle apparatus heats a scroll type compressor, a scroll type expander interlocking with the turning motion of the scroll type compressor, and a compressed working fluid sent from the scroll type compressor to the scroll type expander. Heating device.
Unlike the conventional gas turbine type Brayton cycle device, this Brayton cycle device has a scroll and a compressor and an expander, so that the structure is simple and can be miniaturized. Moreover, in the Brayton cycle apparatus, the working fluid is divided and sealed, moves inside the compressor and the expander, and is compressed and expanded. Therefore, the conversion efficiency from thermal energy to kinetic energy is also excellent.
Furthermore, the heating device can drive the Brayton cycle device of the present invention by heating the working fluid by heat transfer. Therefore, the pressure of the energy source itself does not matter and does not affect the back pressure of the energy source such as exhaust.
Thus, the Brayton cycle device of the present invention can efficiently convert thermal energy into kinetic energy without increasing the back pressure of the energy source. Therefore, even when the Brayton cycle device of the present invention is applied to an internal combustion engine or the like, the exhaust heat energy can be efficiently recovered without increasing the exhaust back pressure.
Preferably, the compression orbiting scroll of the scroll type compressor and the expansion orbiting scroll of the scroll type expander are provided on both sides of the orbiting partition so as to be opposite to each other across the orbiting partition. The compression orbiting scroll of the orbiting partition faces a compressor case having a compression-fixed scroll formed therein and is slidably in contact with or sandwiching a narrow gap. Therefore, the compression orbiting scroll is combined with the compression fixed scroll to form the scroll compressor. The inflatable orbiting scroll of the orbiting partition faces the expander case in which an inflatable fixed scroll is formed, and slidably contacts or sandwiches a narrow gap. Therefore, the expansion orbiting scroll is combined with the expansion fixed scroll to form the scroll type expander.
By forming the scroll compressor and the scroll expander in this way, the Brayton cycle apparatus can be further simplified and miniaturized.
Preferably, the scroll type compressor releases heat transferred from the scroll type expander to the orbiting partition wall to the outside through the compressor case.
The scroll type compressor is in contact with the scroll type expander through the rotating partition. Therefore, the compressor case on the low temperature side can receive the heat of the swirling partition wall transmitted from the scroll expander on the high temperature side and release the heat to the outside. Due to the heat radiation effect of such a compressor case, it is possible to suppress the high temperature of the swirling partition wall. Therefore, the thermal deformation of the swirl partition can be suppressed and the dimensional accuracy of the swirl partition can be maintained. Accordingly, the leakage of the working fluid is prevented, the friction coefficient is prevented from being increased when the swirling partition wall is swung, and high energy conversion efficiency can be maintained.
This makes it possible to use a lightweight material with low heat resistance, particularly for the swirling partition wall and the compressor case, which can contribute to further weight reduction of the apparatus.
Preferably, the scroll-type expander introduces the working fluid into the heat absorption chamber provided in the expander case before the introduced working fluid expands, and through the wall portion of the heat absorption chamber, Heat the working fluid during expansion.
By configuring the scroll expander in this way, the working fluid being expanded in the scroll expander can be heated by the heat of the working fluid before compression. Therefore, heat energy can be converted into kinetic energy more efficiently in the Brayton cycle apparatus without complicating the configuration.
Preferably, the scroll compressor takes air as working fluid and compresses it, and the scroll expander releases the expanded working fluid to the atmosphere.
Since the atmosphere is used as the working fluid in this way, a heat radiating device for the working fluid is unnecessary. Therefore, the configuration of the apparatus is further simplified and reduced in size.
Preferably, the heating device is formed as a heat exchanger that transfers external heat to the working fluid by heat exchange.
By forming the heating device as a heat exchanger in this way, the device can be simplified and miniaturized. Furthermore, even if the Brayton cycle device of the present invention is used for exhaust heat energy recovery of an internal combustion engine or the like, the exhaust back pressure does not increase.
The present invention further relates to a positive displacement compressor, a scroll expander that orbits in conjunction with a compression motion of the positive displacement compressor, and a compressed operation that is sent from the positive displacement compressor to the scroll expander. There is provided a Brayton cycle device including a heating device for heating a fluid.
In this Brayton cycle device, unlike the conventional gas turbine type Brayton cycle device, the compressor is a positive displacement type and the expander is a scroll type. Therefore, the structure of the Brayton cycle device is simplified and the size can be reduced. Moreover, in this Brayton cycle apparatus, the working fluid is divided and sealed, moves inside the compressor and the expander, and is compressed and expanded. Therefore, this Brayton cycle apparatus is also excellent in conversion efficiency from thermal energy to kinetic energy.
Furthermore, the heating device can drive the Brayton cycle device of the present invention by heating the working fluid by heat transfer. Therefore, the pressure of the energy source itself does not matter and does not affect the back pressure of the energy source such as exhaust.
Thus, the Brayton cycle device of the present invention can efficiently convert thermal energy into kinetic energy without increasing the back pressure of the energy source. Therefore, even when the Brayton cycle device of the present invention is applied to an internal combustion engine or the like, the exhaust heat energy can be efficiently recovered without increasing the exhaust back pressure.
Preferably, in the Brayton cycle apparatus, the wall surface of the expander is kept warm.
Since the wall surface of the expander is thus kept warm, leakage of heat energy from the expander is prevented. Therefore, the expander can convert thermal energy into kinetic energy more efficiently.
Furthermore, the present invention provides an exhaust heat energy recovery device for an internal combustion engine. This energy recovery device uses a Brayton cycle device that heats the compressed working fluid sent from the compressor to the expander by heat transmitted from the flow path wall of the exhaust flow path of the internal combustion engine. Therefore, the thermal energy recovery device can recover the exhaust heat energy as kinetic energy.
As described above, the exhaust heat energy recovery device of the present invention uses the Brayton cycle device to heat the working fluid by heat transfer in order to recover the exhaust heat energy of the internal combustion engine. Therefore, the exhaust heat energy recovery device of the present invention can efficiently recover the exhaust heat energy without increasing the exhaust back pressure of the internal combustion engine.
Preferably, in the thermal energy recovery device, the heating device included in the Brayton cycle device is formed as a heat exchanger that transfers external heat to the working fluid by heat exchange. This heat exchanger is arranged so as to contact the exhaust gas of the internal combustion engine.
With this configuration, the exhaust heat energy recovery device can be simplified and downsized, and can be easily mounted on a vehicle or the like. This exhaust heat energy recovery device can efficiently recover exhaust heat energy without increasing the exhaust back pressure of the internal combustion engine.
Preferably, the exhaust flow path is configured as a double pipe having an inner passage and an outer passage. Heat exchange takes place between the exhaust passing through one of the inner and outer passages of the double pipe and the working fluid passing through the other.
By forming the exhaust passage as a double pipe and exchanging heat in this way, the compressed working fluid can be easily heated with exhaust heat energy.
Therefore, exhaust heat energy can be efficiently recovered with a simple and small configuration without increasing the exhaust back pressure of the internal combustion engine.
Preferably, the Brayton cycle apparatus includes a scroll compressor and a scroll expander disposed on opposite sides with respect to the orbiting partition. The swirling partition and the compressor case are made of a highly heat conductive material, and the expander case is made of a heat resistant material.
The compressor case of the high thermal conductivity material is on the low temperature side in the Brayton cycle apparatus, and the swirl partition is also formed of the high thermal conductivity material. Thus, the Brayton cycle device is cooled from the compressor case. As a result, the swirling partition wall and the compressor case need not be made of a heat resistant material. Therefore, an exhaust heat energy recovery device for an internal combustion engine can be formed by forming the expander case in direct contact with the high temperature working fluid with a heat resistant material.
Preferably, an aluminum alloy is used as the high thermal conductivity material, and an iron alloy is used as the heat resistant material.
Thus, by using an aluminum alloy as a highly heat conductive material, it can contribute to weight reduction of an exhaust thermal energy recovery apparatus.
Preferably, the wall surface of the expander is kept warm.
Thus, by using the Brayton cycle device in which the wall surface of the expander is kept warm, it is possible to more efficiently convert heat energy into kinetic energy and to recover exhaust heat energy with high efficiency.
Furthermore, the present invention relates to a scroll type expander formed by combining an expanded orbiting scroll with an expanded fixed scroll, a compressor that is linked to the orbiting motion of the expanded orbiting scroll to compress working fluid, and the scroll from the compressor to the scroll. There is provided a Brayton cycle apparatus comprising a compressed working fluid path for supplying a working fluid to a type expander and a heat source for heating the working fluid in the scroll type expander by heat transfer.
That is, the Brayton cycle device is not limited to a configuration in which the working fluid is heated in the compressed working fluid path that supplies the working fluid from the compressor to the scroll type expander, but the working fluid in the scroll type expander is converted into heat transmitted from the heat source. It may be configured to be heated.
In this case, it becomes possible to drive the Brayton cycle device of the present invention by heating the working fluid in the scroll expander with the heat transmitted from the heat source. Therefore, the pressure of the heat source itself does not matter, and heat energy can be efficiently converted into kinetic energy without affecting the back pressure of the heat source. Therefore, even when the Brayton cycle device of the present invention is applied to an internal combustion engine or the like, the exhaust heat energy can be efficiently recovered without increasing the exhaust back pressure.
Further, since the working fluid is not heated in the compressed working fluid path, the compressed working fluid path itself can have a simple configuration. Since the working fluid can be heated by heat transfer using the configuration of the scroll expander, the Brayton cycle apparatus is further simplified and miniaturized.
Preferably, the compressor is a positive displacement compressor.
Even when a positive displacement compressor is used in this manner, the working fluid in the scroll expander is heated as described above. Therefore, even when the Brayton cycle device in this case is applied to an internal combustion engine or the like, the exhaust heat energy can be efficiently recovered without increasing the exhaust back pressure.
Furthermore, the present invention provides a rotating partition in which a compression orbiting scroll is formed on one side and an expansion orbiting scroll is formed on the other side, and a scroll compressor formed by combining a compression fixed scroll with the compression orbiting scroll, A scroll type expander formed by combining an expansion fixed scroll with an expansion fixed scroll, a compression working fluid path for supplying a working fluid from the scroll type compressor to the scroll type expander, and an operation in the scroll type expander A Brayton cycle apparatus is provided that includes a heat source that heats a fluid by heat transfer.
That is, the Brayton cycle device is not limited to a configuration in which the working fluid is heated in the compression working fluid path for supplying the working fluid from the scroll compressor to the scroll expander, but the working fluid in the scroll expander is transferred from the heat source. The structure which heats by may be sufficient.
Unlike the conventional gas turbine type Brayton cycle device, this Brayton cycle device has a scroll and a compressor and an expander, so that the structure is simple and can be miniaturized. Moreover, in the Brayton cycle apparatus, the working fluid moves in the divided state inside the compressor and the expander, and is compressed and expanded. Therefore, the conversion efficiency from thermal energy to kinetic energy is also excellent.
Furthermore, the Brayton cycle device of the present invention is driven by heating the working fluid by the heat transferred from the heat source. Therefore, the pressure of the heat source itself does not matter and does not affect the back pressure of the heat source such as exhaust.
Thus, the Brayton cycle device of the present invention can efficiently convert thermal energy into kinetic energy without increasing the back pressure of the heat source. Therefore, even when this Brayton cycle device is applied to an internal combustion engine or the like, exhaust heat energy can be efficiently recovered without increasing the exhaust back pressure.
Further, since the working fluid is not heated in the compressed working fluid path, the compressed working fluid path itself has a simple configuration. Furthermore, since the configuration of heating the working fluid by heat transfer using the configuration of the scroll expander is possible, the Brayton cycle apparatus is further simplified and miniaturized.
Preferably, the compressed working fluid path is a through hole formed in the swirling partition wall. The through-hole communicates with the inside of the case of the scroll type compressor and the inside of the case of the scroll type expander formed with the orbiting partition wall interposed between the scroll type compressor and the scroll type compressor.
The through hole of the swirling partition wall can serve as a compressed working fluid path. Therefore, the compressed working fluid path has a very simple configuration, and the Brayton cycle apparatus as a whole is further simplified and downsized.
Preferably, the heat source contacts a case of the scroll expander. Thus, the heat source heats the working fluid in the scroll expander via the case of the scroll expander or the expansion fixed scroll fixed to the case.
In this case, the working fluid can be heated by heat transfer using the expansion fixed scroll. Therefore, the Brayton cycle apparatus is further simplified and miniaturized.
The present invention provides an exhaust heat energy recovery device for an internal combustion engine using a Brayton cycle device that heats the working fluid sent to the expander by heat transmitted from the flow passage wall of the exhaust flow passage of the internal combustion engine.
In this case, in order to recover the exhaust heat energy of the internal combustion engine, the working fluid is heated by heat transfer using the Brayton cycle device. Therefore, exhaust heat energy can be efficiently recovered without increasing the exhaust back pressure of the internal combustion engine.
Further, the exhaust heat energy recovery device heats the working fluid sent to the expander by heat transmitted from the flow path wall of the exhaust flow path of the internal combustion engine. Therefore, the exhaust heat energy recovery apparatus as a whole is simplified and downsized.
Preferably, the exhaust heat energy recovery device includes a scroll type expander and a heat source that heats the working fluid in the scroll type expander by heat transfer. An exhaust gas from an internal combustion engine is used as the heat source. Therefore, the exhaust heat energy recovery apparatus as a whole is further simplified and downsized.

FIG. 1 is a schematic configuration diagram of a Brayton cycle apparatus according to a first embodiment embodying the present invention.
FIG. 2 is an external explanatory view of a heat treatment apparatus in the Brayton cycle apparatus of FIG.
FIG. 3 is an external explanatory diagram of the heat treatment apparatus of FIG.
4 is a plan view of a compressor case in the apparatus of FIG.
FIG. 5 is a plan view of an expander case in the apparatus of FIG.
6 is a perspective view of the compressor case of FIG.
FIG. 7 is a perspective view of the expander case of FIG.
FIG. 8 is a diagram illustrating the configuration of a swirling partition wall in the apparatus of FIG.
9 is a perspective view of the swirling partition wall of FIG.
10 is an explanatory diagram of the internal configuration of the scroll compressor in the apparatus of FIG.
FIG. 11 is an explanatory diagram of the internal configuration of the scroll expander in the apparatus of FIG.
12 is a PV diagram of the Brayton cycle in the apparatus of FIG.
FIG. 13 is an explanatory diagram of the positional relationship between the compression fixed scroll and the compression orbiting scroll when the Brayton cycle device of FIG. 1 is driven.
14 is an explanatory diagram of the positional relationship between the expansion fixed scroll and the expansion orbiting scroll when the Brayton cycle device of FIG. 1 is driven,
FIG. 15 is a schematic configuration diagram of a Brayton cycle device and an exhaust heat energy recovery device according to a second embodiment of the present invention.
FIG. 16 is a diagram illustrating the configuration of the heat dissipating fins in the compressor case of the apparatus shown in FIG.
FIG. 17 is a diagram illustrating the configuration of heat sink fins in the expander case of the apparatus shown in FIG.
FIG. 18 is a schematic configuration diagram of a Brayton cycle apparatus according to the third embodiment of the present invention.
FIG. 19 is an external explanatory diagram of a heat treatment apparatus in the Brayton cycle apparatus of FIG.
20 is an external explanatory diagram of the heat treatment apparatus of FIG.
21 is a plan view of a compressor case in the apparatus of FIG.
FIG. 22 is a plan view of an expander case in the apparatus of FIG.
FIG. 23 is a perspective view of the compressor case of FIG.
24 is a perspective view of the expander case of FIG.
FIG. 25 is a perspective view of a swirling partition wall in the apparatus of FIG.
FIG. 26 is a diagram illustrating the configuration of the swirling partition wall of FIG.
27 is an explanatory diagram of a positional relationship between the compression fixed scroll and the compression orbiting scroll when the Brayton cycle device of FIG. 18 is driven,
FIG. 28 is an explanatory diagram of the positional relationship between the expansion fixed scroll and the expansion turning scroll when the Brayton cycle device of FIG. 18 is driven;
FIG. 29 is a graph showing a comparison of thermal energy conversion efficiencies due to differences in heating methods for the apparatus of FIG.
FIG. 30 is a schematic configuration diagram of a Brayton cycle apparatus according to the fourth embodiment of the present invention.
FIG. 31 is a configuration explanatory view of another example of the crank mechanism of the present invention.

Hereinafter, a first embodiment of the present invention will be described. FIG. 1 shows a schematic configuration of a Brayton cycle apparatus 1. The heat insulation processing device 2 in the Brayton cycle device 1 is shown in FIGS. 2A is a front view of the heat treatment apparatus 2, FIG. 2B is a rear view, FIG. 3A is a right side view, and FIG. 3B is a left side view. Yes.
The heat insulation processing device 2 includes a scroll compressor 4 and a scroll expander 6. The scroll compressor 4 includes a compressor case 8 as shown in the plan view of FIG. A compression fixed scroll 10 is formed in the internal space 9 of the compressor case 8. A compressed working fluid discharge port 9 a is provided in a portion of the compressor case 8 corresponding to the center portion of the compression fixed scroll 10. A working fluid introduction port 9 b is provided on the outermost peripheral portion of the compression fixed scroll 10. A perspective view of the compressor case 8 is shown in FIG.
The scroll type expander 6 includes an expander case 12 as shown in the plan view of FIG. 5, and an expansion fixed scroll 14 is formed in the internal space 13 of the expander case 12. A portion of the expander case 12 corresponding to the center portion of the expansion fixed scroll 14 is provided with a compressed working fluid suction port 13a. A working fluid discharge port 13 b is provided on the outermost peripheral portion of the expansion fixed scroll 14. A perspective view of the expander case 12 is shown in FIG.
A circular swivel recess 8 b is provided inside the joint surface 8 a of the compressor case 8, and a circular swivel recess 12 b is also provided inside the joint surface 12 a of the expander case 12. When the joint surfaces 8a and 12a come into contact with each other as shown in FIG. 2 and the compressor case 8 is fastened to the expander case 12 with the bolt Bt, the two swivel recesses 8b and 12b are located inside the heat treatment apparatus 2. A storage chamber for storing the swivel partition 18 is defined. In the storage chamber, the swiveling partition wall 18 shown in FIG. 8 can swivel while sliding, or can swivel through a narrow gap.
A compression orbiting scroll 20 is formed to protrude on the compressor-side surface 18a of the orbiting partition wall 18 shown in FIG. An expandable orbiting scroll 22 is formed to project on the expander side surface 18b of the orbiting partition wall 18 shown in FIG. A perspective view of the swirling partition wall 18 is shown in FIG.
Three crank mechanisms 24 formed in a disc shape are rotatably attached to the peripheral edge of the swivel partition wall 18 by crank pins 24b. Each crank mechanism 24 is housed in three crank housing portions 8 c provided in the compressor case 8. A crankshaft 24 a is provided at the center of each crank mechanism 24. The crankshaft 24a is inserted into a crank bearing hole 8d provided at the center of the crank housing portion 8c and is rotatably supported by the compressor case 8. Thus, the crank mechanism 24 is supported by the compressor case 8, so that the entire turning partition wall 18 is supported by the compressor case 8 so as to be turnable.
In the state where the heat insulation processing device 2 is assembled, two of the three crankshafts 24a protrude outside the heat treatment processing device 2 as shown in FIGS. The first crankshaft 24a receives cranking torque from the outside of the heat insulation processing device 2 when the Brayton cycle device 1 is started. The second crankshaft 24 a outputs the torque generated by the Brayton cycle device 1 to the outside of the heat insulation processing device 2. In addition, the crankshaft 24a which protrudes outside the heat insulation processing device 2 is changed to one instead of two, and both functions of cranking torque input and generated torque output are combined into one crankshaft 24a. Also good.
The compression orbiting scroll 20 on one side (surface 18a (surface) on the compressor side) of the orbiting partition wall 18 having the above-described configuration is combined with the compression fixed scroll 10 of the compressor case 8 (FIGS. 4 and 6), and the other side ( The expansion orbiting scroll 22 on the expander side surface 18b (back surface) is combined with the expansion fixed scroll 14 of the expander case 12 (FIGS. 5 and 7). And the heat insulation processing apparatus 2 is formed by fastening the compressor case 8, the expander case 12, and the turning partition 18 with the volt | bolt Bt.
FIG. 10 shows an internal configuration of the scroll compressor 4 in the heat treatment apparatus 2 configured as described above. FIG. 10 shows the compression orbiting scroll 20 on the compressor-side surface 18a (surface) of the orbiting partition wall 18 and the compressor case 8 combined therewith. In the state where the compressor case 8 (compression orbiting scroll 20) is up and the expander case 12 (expanding orbiting scroll 22) is down, the compressor case 8 above the orbiting partition wall 18 is indicated by a one-dot chain line. . The compression orbiting scroll 20 is shown in black.
FIG. 11 shows an internal configuration of the scroll type expander 6 in the heat insulation processing device 2. FIG. 11 shows the expandable orbiting scroll 22 on the expander side surface 18b (rear surface) of the orbiting partition wall 18 and the expander case 12 combined therewith through the orbiting partition wall 18 from the scroll compressor 4 side. Shown in the state. The expanded fixed scroll 14 and the expanded orbiting scroll 22 below the orbiting partition wall 18 are indicated by broken lines.
As shown in FIGS. 10 and 11, the crankshaft 24a rotates clockwise as seen from the compressor case 8 side as shown in the drawing, and the swirling partition wall 18 swivels clockwise. Therefore, the adiabatic compression process in the PV diagram of the Brayton cycle shown in FIG. 12 is realized by the scroll compressor 4, and the adiabatic expansion process is realized by the scroll expander 6.
The turning state will be described with reference to FIGS. FIG. 13 shows the configuration of the orbiting partition wall 18 viewed from the compressor case 8 side and the compressor case 8 thereover in order to explain the positional relationship between the compression fixed scroll 10 and the compression orbiting scroll 20. is there. Similarly, FIG. 14 shows the configuration of the orbiting partition wall 18 and the expander case 12 below the structure as viewed from the compressor case 8 side, in order to explain the positional relationship between the expansion fixed scroll 14 and the expansion orbiting scroll 22. It is a thing. Since the compression orbiting scroll 20 and the expansion orbiting scroll 22 exist on the front and back of the orbiting partition wall 18 and cause the same orbiting motion, the orbiting of FIG. 13 and the orbiting of FIG.
Since the orbiting partition wall 18 orbits clockwise as viewed from the scroll compressor 4 side as described above, the position of the compression orbiting scroll 20 is changed to the compression fixed scroll 10 as shown in the order from (1) to (8) in FIG. Change. As a result, the working fluid (here, air) is introduced from the working fluid introduction port 9b into the internal space 9 of the compressor case 8 with the initial volume Va1, and gradually decreases in volume toward the center of the compressor case 8. Transported. When the working fluid reaches the final volume Va2 (Va1> Va2) at the center of the compressor case 8, the compressed working fluid discharge port 9a is opened, and the compressed working fluid is heated from the compressed working fluid discharge port 9a. It is sent out to the device 30 (FIG. 1).
Simultaneously with the turning of the compression orbiting scroll 20, in the scroll type expander 6, the position of the inflating orbiting scroll 22 changes with respect to the inflatable fixed scroll 14 as shown sequentially from (1) to (8) in FIG. 14. Therefore, the working fluid heated by the heating device 30 is introduced from the compressed working fluid suction port 13a into the internal space 13 of the expander case 12 with the initial volume Vb2, and gradually expands the volume while gradually expanding the volume. Transported to When the final volume Vb1 (Vb1> Vb2) is reached at the peripheral portion of the expander case 12, the working fluid is released from the restraint by the expansion fixed scroll 14 and the expansion orbiting scroll 22 and is expanded from the working fluid discharge port 13b. It is discharged to the outside of the case 12.
The axial dimensions of the inflatable fixed scroll 14 and the inflatable orbiting scroll 22 are larger than the axial dimensions of the compression fixed scroll 10 and the compressive orbiting scroll 20 and are designed to have a relationship of Va1 <Vb1 and Va2 <Vb2.
The Brayton cycle apparatus 1 shown in FIG. 1 is completed by the combination of the heat treatment apparatus 2 and the heating apparatus 30 thus configured. The heating device 30 uses a double tube, and includes a heat source flow path 30a which is an inner passage, and an outer passage 30b provided around the flow path 30a. The heating device 30 causes the working fluid to flow through the outer passage 30b. Therefore, the working fluid in the outer passage 30b is heat-exchanged with the fluid flowing in the heat source flow path 30a via the tube wall (flow path wall) of the heat source flow path 30a. Specifically, if an exhaust pipe of an internal combustion engine is used as the heat source flow path 30a, the exhaust heat energy of the internal combustion engine can be recovered. That is, the exhaust flows through the flow path 30a of the heat source, and the heat of the exhaust is transmitted to the working fluid (air) flowing through the outer passage 30b.
The values of the volumes Va1, Va2, Vb1, and Vb2 are as follows: the working fluid temperature at the working fluid introduction port 9b, the heat exchanger efficiency at the heating device 30, the working fluid temperature at the compression working fluid suction port 13a, the scroll compressor 4 and the scroll. In consideration of the heat insulation efficiency in the mold expander 6, the Brayton cycle apparatus 1 is designed to obtain the maximum thermal efficiency.
The first embodiment described above has the following advantages.
(1). Unlike the conventional gas turbine type Brayton cycle device, the Brayton cycle device 1 according to the present embodiment uses the scroll compressor 4 and the scroll type expander 6, and thus has a simple structure and can be downsized.
In particular, in the heat insulation processing device 2, the working fluid moves inside the scroll compressor 4 and the scroll expander 6 in a state where the working fluid is divided and sealed by a combination of the fixed scrolls 10 and 14 and the orbiting scrolls 20 and 22. Compressed and expanded. For this reason, the conversion efficiency from thermal energy to kinetic energy is also excellent.
Since the external energy source only needs to transfer heat to the working fluid through the tube wall of the flow path 30a to exchange heat, the size of the external energy source can be further reduced. Furthermore, the pressure of the energy source itself does not matter and does not affect the back pressure of the energy source such as exhaust.
Therefore, the Brayton cycle apparatus 1 of the present embodiment can efficiently convert thermal energy into kinetic energy without increasing the back pressure of the energy source. From this, when the Brayton cycle device 1 of the present embodiment is applied to an internal combustion engine, exhaust heat energy can be efficiently recovered without increasing the exhaust back pressure of the internal combustion engine.
(2). The compression orbiting scroll 20 of the scroll type compressor 4 and the expansion orbiting scroll 22 of the scroll type expander 6 are provided on both sides of the orbiting partition wall 18 that orbits around the crankshaft 24a. A compressor case 8 having a compression-fixed scroll 10 formed therein is slidably attached to the side of the orbiting partition wall 18 on the side of the orbiting orbiting scroll 20 so as to be slidable in close contact with each other with a narrow gap therebetween. Therefore, the scroll type compressor 4 is formed by combining the compression turning scroll 20 and the compression fixed scroll 10. An expander case 12 having an expansion fixed scroll 14 formed therein is slidably attached to the side of the orbiting partition wall 18 on the side of the orbiting orbiting scroll 22 in a close contact state or in a state of confronting with a narrow gap. Therefore, the scroll type expander 6 is formed by combining the expansion orbiting scroll 22 and the expansion fixed scroll 14.
By forming the scroll compressor 4 and the scroll expander 6 in this way, the Brayton cycle apparatus 1 can be further simplified and reduced in size.
(3). As described above, the swirling partition wall 18 covers the expander case 12. Therefore, the swirling partition wall 18 is exposed to a high-temperature working fluid introduced into the scroll expander 6. However, the compressor case 8 can contact the swirling partition wall 18 from the side opposite to the expander case 12. Therefore, the heat transmitted from the scroll type expander 6 to the revolving partition wall 18 is taken away by the compressor case 8 and released to the outside.
Due to the heat radiation effect of the compressor case 8, the temperature rise of the swivel partition wall 18 can be suppressed. Therefore, the thermal deformation of the swirling partition wall 18 can be suppressed and the dimensional accuracy of the swirling partition wall 18 can be maintained. Therefore, leakage of the working fluid from the heat insulation processing device 2 can be prevented, and the friction coefficient during turning of the turning partition wall 18 can be prevented from being increased, and high energy conversion efficiency can be maintained.
This makes it possible to use a light alloy with low heat resistance, particularly for the revolving partition wall 18 and the scroll compressor 4, thereby contributing to further weight reduction of the Brayton cycle apparatus 1.
(4). The scroll compressor 4 takes in the atmosphere (air) from the working fluid introduction port 9b and makes it a working fluid, and the scroll expander 6 discharges the expanded working fluid from the working fluid discharge port 13b to the atmosphere. Since the atmosphere is used as the working fluid in this way, a heat radiating device for the working fluid is unnecessary, and the configuration of the Brayton cycle device 1 is further simplified and miniaturized.
Next, a second embodiment of the present invention will be described. In the present embodiment, the exhaust heat energy of the in-vehicle internal combustion engine Eng is recovered by using the Brayton cycle device 51 configured as shown in FIG. The heat insulation processing device 52 includes a scroll compressor 54 and a scroll expander 56. The internal configuration of the scroll compressor 54 and the scroll expander 56 is the scroll compressor 4 described in the first embodiment. And the structure of the scroll type expander 6 is the same.
This embodiment is different from the first embodiment in the following points. That is, the end surface 58a of the compressor case 58 is provided with a number of protrusion-like heat radiating fins 58b as shown in FIGS. The heat dissipated from the internal revolving partition wall 18 to the compressor case 58 is released to the outside by the radiation fins 58b. That is, the radiating fins 58 b are provided in order to increase the radiating efficiency of radiating the heat received by the revolving partition wall 18 from the high temperature scroll expander 56 through the compressor case 58.
Furthermore, as shown in FIGS. 15 and 17, a large number of protrusion-like heat absorption fins 62 b are provided on the end surface 62 a of the expander case 62. A cover 62 c is disposed on the end surface 62 a of the expander case 62. The cover 62c covers the compressed working fluid suction port 63a and the heat absorption fins 62b, and defines the heat absorption chamber 62d. The working fluid heated by the heating device 80 is introduced into the heat absorption chamber 62d. Therefore, the heat absorption fins 62b are heated by the working fluid introduced into the heat absorption chamber 62d. The compressed working fluid suction port 63a opened to the heat absorbing chamber 62d can suck the heated working fluid. For this reason, the working fluid introduced into the endothermic chamber 62d heats the working fluid inside the expander case 62 from the endothermic fin 62b through the end surface 62a of the wall portion of the endothermic chamber 62d. Therefore, the pressure drop due to the expansion of the working fluid in the scroll expander 56 is small. Therefore, even if the expansion rate in the scroll type expander 56 is high, the working fluid can be discharged from the working fluid discharge port 63b in an atmospheric pressure state. Therefore, the Brayton cycle apparatus 51 can recover the exhaust heat energy with higher efficiency.
The heating device 80 has two working fluid paths, a path 80c for passing the working fluid through the entire length of the double pipe 80b and a path 80d for passing the working fluid through only a part of the double pipe 80b. Have. The distribution valve 80e can adjust the path distribution state of the compressed working fluid supplied from the scroll compressor 54. The distribution ratio of the paths 80c and 80d in the present embodiment is such that the working fluid supply temperature detected from the temperature sensor 81 provided at the opening portion of the compressed working fluid suction port 63a in the heat absorbing chamber 62d is a preset reference temperature. Adjusted as follows. That is, after the working fluid has absorbed heat by the heat absorbing fins 62b, the temperature of the working fluid when reaching the compressed working fluid suction port 63a becomes a reference temperature appropriate for the start of expansion in the scroll expander 56. The distribution ratio of the valve 80e is adjusted.
The crankshaft 74a of the Brayton cycle device 51 is rotated at the start of driving of the Brayton cycle device 51 by the output of the internal combustion engine Eng. However, after the drive of the Brayton cycle device 51 is started, the crankshaft 74a rotates independently of the output of the internal combustion engine Eng by the heat energy of the exhaust gas that passes through the heating device 80. Need to be separated from Therefore, an electromagnetic clutch 92 is provided between the output shaft 64 of the internal combustion engine Eng and the crankshaft 74a of the Brayton cycle device 51.
The distribution ratio control of the distribution valve 80e and the engagement / release control of the electromagnetic clutch 92 are executed by an electronic control unit (ECU) 94 based on the operating state of the internal combustion engine Eng.
For example, before starting the internal combustion engine Eng, the electromagnetic clutch 92 is released, and at the timing when the exhaust temperature of the internal combustion engine sufficiently rises after starting the internal combustion engine Eng, the electromagnetic clutch 92 is engaged and the output of the internal combustion engine Eng The crankshaft 74a of the cycle device 51 is rotated. The ECU 94 adjusts the distribution valve 80e by driving the valve actuator 80f so that the working fluid temperature detected by the temperature sensor 81 becomes 350 ° C., for example.
Thereafter, the ECU 94 releases the electromagnetic clutch 92. Thus, the self-sustaining rotation of the crankshaft 74a of the Brayton cycle device 51 causes the exhaust heat energy recovery device, here the generator 96, to be rotated by the crankshaft 74a. Therefore, the exhaust heat energy is recovered as electric energy and used as a vehicle power source or stored in a battery.
In the above-described configuration, the expander case 62 is made of a heat resistant material (for example, an iron alloy such as cast iron) because it directly contacts the high-temperature working fluid. The compressor case 58 is made of a highly thermally conductive material (especially a light alloy such as an aluminum alloy) because the working fluid is at a relatively low temperature. The swirling partition wall 18 is made of a highly thermally conductive material so as to be cooled by transferring heat to the compressor case 58.
The second embodiment described above has the following advantages.
(1). The compressor case 58 is formed with heat radiation fins 58b. Therefore, since the compressor case 58 easily releases heat to the outside, the advantage described in (3) of the first embodiment becomes remarkable.
(2). An end surface 62a of the expander case 62 is covered with a cover 62c to define a heat absorption chamber 62d. Therefore, the working fluid being expanded inside the scroll type expander 56 can be heated via the wall portion of the expander case 62 having the end surface 62a of the expander case 62 as described above. In addition, endothermic fins 62b are formed on the end face 62a. Therefore, heat transfer at the end face 62a is good, and heat energy can be converted into kinetic energy more efficiently in the Brayton cycle device 51 without complicating the configuration.
(3). The exhaust pipe is a double pipe 80b. The heating device 80 is configured as a heat exchanger for exchanging heat between a high-temperature gas (exhaust gas from the internal combustion engine Eng here) and the working fluid. The Brayton cycle device 51 collects exhaust heat energy as kinetic energy. Therefore, the exhaust heat energy can be efficiently converted into kinetic energy without increasing the exhaust back pressure of the internal combustion engine Eng.
(4). As described above, the compressor case 58 and the rotating partition wall 18 can be made into a light alloy. Therefore, the entire Brayton cycle device 51 can also be reduced in weight. Therefore, the fuel economy can be further improved by applying the Brayton cycle device 51 to the in-vehicle internal combustion engine.
(5). The advantages (1), (2), and (4) of the first embodiment are produced.
Next, a third embodiment of the present invention will be described. FIG. 18 shows a schematic configuration of the Brayton cycle apparatus 101. 19 and 20 show an adiabatic treatment apparatus 102 of the Brayton cycle apparatus 101. FIG. 19A is a front view of the heat insulation processing apparatus 102, FIG. 19B is a rear view, FIG. 20A is a right side view, and FIG. 20B is a left side view.
The working fluid introduction port 109b is provided so as to protrude from the outer peripheral portion of the scroll compressor 104, and the working fluid discharge port 113b is provided so as to protrude from the outer peripheral portion of the scroll type expander 106 as in the first embodiment. The same.
However, unlike the first embodiment, as shown in FIGS. 21 to 24, the compressor case 108 is not provided with the compressed working fluid discharge port 9a, and the expander case 112 is provided with the compressed working fluid suction port 13a. Is not provided. 21 is a plan view of the compressor case 108, FIG. 22 is a plan view of the expander case 112, FIG. 23 is a perspective view of the compressor case 108, and FIG. 24 is a perspective view of the expander case 112.
Instead of the compressed working fluid discharge port 9a and the compressed working fluid suction port 13a, a through hole 118c is formed at the center of the swivel partition wall 118 as shown in FIGS. 25 is a perspective view of the swirling partition wall 118, FIG. 26A is a plan view of the swirling partition wall 118 showing the compressor-side surface 118a of the swirling partition wall 118, and FIG. It is a reverse view of the turning partition 118 which shows 118b.
In the scroll compressor 104, as shown in (1) to (8) of FIG. When the compression orbiting scroll 120 of the orbiting partition 118 moves relative to the compression fixed scroll 110 of the compressor case 108, the working fluid introduced into the scroll compressor 104 from the working fluid introduction port 109b is compressed, and the orbiting partitioning wall is compressed. The through hole 118c at the center of 118 is reached. FIG. 27 shows the revolving partition wall 118 viewed from the compressor case 108 side and the compressor case 108 on top of each other in order to explain the positional relationship between the compression fixed scroll 110 and the compression turning scroll 120. . Accordingly, FIG. 27 is shown reversed left and right with respect to FIG.
The compressed working fluid is immediately introduced from the scroll compressor 104 to the scroll expander 106 as shown by the broken line Ap in FIG. 18 by passing through the through hole 118c.
In the scroll type expander 106, as shown in (1) to (8) of FIG. When the expansion orbiting scroll 122 of the orbiting partition wall 118 moves relative to the expansion fixed scroll 114 of the expander case 112, the working fluid introduced into the scroll type expander 106 from the through hole 118c expands, and the working fluid discharge port 113b is reached.
FIG. 28 shows the revolving partition wall 118 viewed from the compressor case 108 side and the expander case 112 thereunder in an overlapping manner in order to explain the positional relationship between the expansion fixed scroll 114 and the expansion revolving scroll 122. .
The expander case 112 is in contact with or joined to a flow path 130a (FIG. 18) that is a heat source. Therefore, the expander case 112 exchanges heat with the fluid flowing through the flow path 130a via the tube wall (flow path wall) of the flow path 130a. Therefore, the working fluid expands while being heated by heat transfer due to contact with the expander case 112 or the expansion fixed scroll 114.
With such a configuration, the swirling partition wall 118 pivots clockwise in FIGS. 27 and 28, so that the adiabatic compression stroke, the isobaric heating stroke, and the adiabatic expansion stroke in the Brayton cycle PV diagram shown in FIG. It has been realized.
In the above-described configuration, the expander case 112 is brought into contact with the high-temperature channel 130a and transferred to heat. Therefore, the working fluid is heated by the expander case 112 and the expansion fixed scroll 114. Therefore, the expander case 112 and the expansion fixed scroll 114 are made of a heat resistant material (for example, an iron alloy such as cast iron). The expander case 112 and the expansion fixed scroll 114 may be made of a light alloy such as an aluminum alloy. Since the working fluid in the compressor case 108 is relatively low temperature, the compressor case 108 is made of a highly heat conductive material (especially a light alloy such as an aluminum alloy). The swirl partition 118 is made of a highly thermally conductive material so that it is cooled by transferring heat to the compressor case 108.
With the above-described configuration, the thermal energy transmitted from the flow path 130a to the expander case 112 is converted into rotational energy of the crankshaft 124a.
When the expander case 112 is heated as in this embodiment, and the expander case 112 is not heated as in the first embodiment, and the working fluid is separately heated and then introduced into the scroll expander 106. FIG. 29 is a graph showing a comparison of the thermal energy conversion efficiency by the experiment and the case of performing the experiment. In this graph, in order to accurately show the difference in torque gain in the scroll type expander 106 due to the difference in heating method, only the scroll type expander 106 is separated from the Brayton cycle device 101 and the expander case 112 itself is heated. The output torque of the crankshaft 124a in this case is compared with the output torque of the crankshaft 124a when the working fluid introduced into the expander case 112 is heated. The horizontal axis of the graph is the temperature difference ΔT of the expander case 112 or the working fluid due to heating, and the vertical axis is the torque gain (N · m).
As shown in the figure, heating the aluminum alloy expander case 112 has higher thermal energy conversion efficiency than heating the working fluid. When the expander case 112 is made of cast iron, the clearance of the scroll expander 106 can be reduced, and the thermal energy conversion efficiency is further increased.
According to the third embodiment described above, the following advantages can be obtained.
(1). The advantages (1) to (4) of the first embodiment are produced.
(2). The Brayton cycle apparatus 101 of the present embodiment heats the working fluid in the scroll expander 106 by heat transfer using a heat source (flow path 130a) without providing a heating device for separately heating the working fluid. It is configured as follows.
For this reason, the compressed working fluid path has a simple configuration. Actually, the compressed working fluid path is a through-hole 118 c formed in the swirl partition wall 118.
Furthermore, the working fluid can be heated by transferring heat to the working fluid by using the expander case 112 and the expansion fixed scroll 114 which are constituent members of the scroll type expander 106. Therefore, the Brayton cycle apparatus 101 is further simplified and downsized.
Next, a fourth embodiment of the present invention will be described. As shown in FIG. 30, the Brayton cycle apparatus 201 of the present embodiment is different from the configuration shown in FIG. 1 of the first embodiment in that a heat insulating material 201 a is provided around the expander case 12 in the heat treatment apparatus 2. Arranged to keep the expander case 12 warm. Since other configurations are the same as those of the first embodiment, the same members are denoted by the same reference numerals.
According to the fourth embodiment described above, the following advantages can be obtained.
(1). The advantages (1) to (4) of the first embodiment are produced.
(2). The heat insulating material 201a keeps the wall surface of the expander case 12 warm. Therefore, when the working fluid is adiabatically expanded in the scroll type expander 6, heat can be prevented from being released to the outside through the expander case 12 due to heat transfer.
As described above, since the wall surface of the expander case 12 is kept warm, leakage of thermal energy from the scroll expander 6 can be prevented. Therefore, heat energy can be converted into kinetic energy more efficiently.
Each said embodiment can be changed as follows.
(A). Instead of the Brayton cycle device used in the second embodiment, the Brayton cycle device shown in FIG. 1, FIG. 18 or FIG. 30 may be used for an exhaust heat energy recovery device of an internal combustion engine.
In each of the above embodiments, the Brayton cycle device used for exhaust heat energy recovery of the internal combustion engine uses a scroll compressor and a scroll expander. Of these, other compressors such as screw type, vane type, and turbo type can be used instead of the scroll type compressor. A turbine type can be used instead of the scroll type expander.
Instead of the scroll compressor and the scroll expander, a positive displacement compressor or a positive displacement expander may be used. It is good also as a Brayton cycle device which combined a positive displacement compressor and a scroll type expander by making a scroll type expander interlock | cooperate with the motion of the positive displacement compressor for compressing a working fluid.
(B). As shown in FIG. 8, the swiveling partition wall 18 is supported by the three crank mechanisms 24, but the present invention is not limited to this, and the swiveling partition wall 18 may be supported by the two crank mechanisms 24. It may be supported by the mechanism 24. Although the crank mechanism 24 is circular, as shown in FIG. 31, a balancer 100 may be provided in the crank mechanism to further enhance the vibration suppressing effect when the Brayton cycle device is driven. The same applies to the swivel partition wall 118 of the third embodiment.
(C). As shown in FIGS. 16 and 17, the heat radiating fins 58b and the heat absorbing fins 62b are each formed in a protruding shape, but may be formed in a flat plate shape or a curved plate shape.
(D). The compressor case 108 of the third embodiment may be provided with heat radiation fins 58b as shown in FIGS. With this configuration, the heat of the compressor case 108 can be easily released to the outside, so that the advantage described in (3) of the first embodiment becomes significant.
In the third embodiment, as shown in FIG. 18, the expander case 112 is in contact with or joined to the flow path 130a, which is a heat source, so that heat exchange is performed via the tube wall (flow path wall) of the flow path 130a. Is done. However, it is also possible to form a flow path for exhaust gas from the beginning in the expander case 112 and guide the exhaust gas to this flow path.
Regarding the expander case 112 of the third embodiment, the outer peripheral portion of the compressor case 112 other than the portion in contact with or joined to the flow path 130a may be covered with a heat insulating material to keep the temperature.
(E). In each of the embodiments described above, the working fluid introduction port and the working fluid discharge port are open to the atmosphere, and the working fluid uses the atmosphere. However, a gas other than the atmosphere may be used with the working fluid path being sealed. In this case, a heat dissipation device may be provided.
(F). In each of the above embodiments, the expander is linked to the movement of the compressor by forming the compression orbiting scroll and the expansion orbiting scroll so as to sandwich the orbiting partition. This “interlocking” means connecting the compressor to the expander so that the movement of the compressor and the expander is performed uniformly. Therefore, linking the expander to the movement of the compressor is equivalent to linking the compressor to the movement of the expander. However, unlike the above embodiments, the present invention is not limited to the configuration in which the compressor is directly connected to the expander. In particular, in the first, second, and fourth embodiments, the expander may be linked to the movement of the compressor by arranging a shaft, a gear, or the like between the compressor and the expander.

Claims (23)

A scroll compressor that compresses the working fluid;
A scroll type expander interlocking with the turning motion of the scroll type compressor, wherein the working fluid compressed by the scroll type compressor is sent to the scroll type expander;
A heating device for heating the compressed working fluid sent from the scroll compressor to the scroll expander;
A Brayton cycle apparatus characterized by comprising: 2. The scroll compressor according to claim 1, wherein the scroll compressor is opposed to the compressor case, a compression fixed scroll formed inside the compressor case, and slidably in contact with the compressor case or with a narrow gap interposed therebetween. A compression orbiting scroll combined with a compression fixed scroll,
The scroll type expander includes an expander case, an expansion fixed scroll formed inside the expander case, and an expansion fixed scroll so as to be slidably attached to the expander case or opposed to each other with a narrow gap therebetween. An inflatable orbiting scroll to be combined,
The Brayton cycle device further includes a turning partition that orbits, and the compression turning scroll and the expansion turning scroll are provided on the turning partition so as to be opposite to each other across the turning partition. apparatus.   3. The Brayton cycle apparatus according to claim 2, wherein the scroll type compressor releases heat transferred from the scroll type expander to the orbiting partition wall to the outside through the compressor case.   The expander case according to claim 2, wherein the expander case includes a heat absorption chamber into which a working fluid before expansion introduced into the scroll expander is introduced, and the expansion unit case is being expanded through a wall section that defines the heat absorption chamber. A Brayton cycle device, wherein the working fluid is heated.   5. The Brayton according to claim 1, wherein the scroll compressor takes in air as a working fluid and compresses it, and the scroll expander discharges the expanded working fluid to the atmosphere. Cycle equipment.   6. The Brayton cycle device according to claim 1, wherein the heating device is a heat exchanger that transfers external heat to the working fluid by heat exchange.   The Brayton cycle device according to any one of claims 1 to 6, wherein a wall surface of the expander is kept warm. A positive displacement compressor that compresses the working fluid;
A scroll type expander that swirls in conjunction with the compression movement of the positive displacement compressor, wherein the working fluid compressed by the positive displacement compressor is sent to the scroll expander;
A Brayton cycle apparatus comprising: a heating device that heats the compressed working fluid sent from the positive displacement compressor to the scroll expander.   The Brayton cycle device according to claim 8, wherein a wall surface of the expander is kept warm. An exhaust heat energy recovery device for an internal combustion engine that recovers exhaust heat energy of an internal combustion engine as kinetic energy, the exhaust heat energy recovery device including a Brayton cycle device,
A compressor for compressing the working fluid;
An expander to which a working fluid compressed by a compressor is sent, and the compressed working fluid sent from the compressor to the expander is heated by heat transmitted from the flow path wall of the exhaust flow path of the internal combustion engine. And an exhaust heat energy recovery device for an internal combustion engine. In Claim 10, the compressor is a scroll compressor, the expander is a scroll expander,
The Brayton cycle device includes a heating device that heats the compressed working fluid sent from the scroll compressor to the scroll expander, and the heating device transfers heat from the flow path wall to the working fluid. An exhaust heat energy recovery device for an internal combustion engine, characterized in that the heat exchanger is disposed so as to come into contact with the exhaust of the internal combustion engine.   12. The exhaust passage according to claim 10, wherein the exhaust passage is configured as a double pipe having an inner passage and an outer passage, and the exhaust passing through one of the inner passage and the outer passage exchanges heat with the working fluid passing through the other. An exhaust heat energy recovery device for an internal combustion engine. 11. The compressor according to claim 10, wherein the compressor is opposed to the compressor case, a compression fixed scroll formed inside the compressor case, and slidably in contact with the compressor case or with a narrow gap therebetween. A scroll type compressor having a compression turning scroll combined with the compression fixed scroll;
The expander includes an expander case, an expansion fixed scroll formed inside the expander case, and the expansion fixed scroll so as to be slidably in contact with the expander case or to face each other with a narrow gap therebetween. A scroll type expander having an inflated orbiting scroll to be combined;
The Brayton cycle apparatus further includes a heating device that heats the compressed working fluid sent from the scroll compressor to the scroll expander by using heat from the flow path wall, and a swirl partition that swirls. The compression turning scroll and the expansion turning scroll are provided on the turning partition so as to be opposite to each other across the turning partition,
The exhaust heat energy recovery apparatus for an internal combustion engine, wherein the swirling partition wall and the compressor case are made of a highly heat conductive material, and the expander case is made of a heat resistant material.   14. The exhaust heat energy recovery apparatus for an internal combustion engine according to claim 13, wherein an aluminum alloy is used as the high thermal conductivity material and an iron alloy is used as the heat resistant material.   The exhaust heat energy recovery device for an internal combustion engine according to any one of claims 10 to 14, wherein a wall surface of the expander is kept warm. A scroll type expander having an inflatable orbiting scroll and an inflatable fixed scroll combined with the inflatable orbiting scroll;
A compressor that compresses the working fluid in conjunction with the orbiting motion of the expansion orbiting scroll;
A compressed working fluid path for supplying compressed working fluid from the compressor to the scroll expander;
A Brayton cycle apparatus comprising: a heat source for heating the working fluid in the scroll expander by heat transfer.   The Brayton cycle apparatus according to claim 16, wherein the compressor is a positive displacement compressor. In Claim 16 or 17, the scroll type expander has a case fixed to the expansion fixed scroll,
The Brayton cycle device according to claim 1, wherein the heat source heats the working fluid in the scroll type expander through the case or the expansion fixed scroll by contacting the case. A orbiting partition having a first one side on which a compression orbiting scroll is formed and a second one side on which an inflating orbiting scroll is formed;
A scroll compressor comprising the compression orbiting scroll and a compression fixed scroll combined with the compression orbiting scroll;
A scroll type expander comprising the inflatable orbiting scroll and an inflatable fixed scroll combined with the inflatable fixed scroll;
A compressed working fluid path for supplying compressed working fluid from the scroll compressor to the scroll expander;
A Brayton cycle apparatus comprising: a heat source for heating the working fluid in the scroll expander by heat transfer.   20. The scroll type compressor according to claim 19, wherein the scroll compressor has a compressor case provided on the first side, and the scroll type expander has an expander case provided on the second side, and the compression working fluid. The path has a through hole formed in the swirling partition wall, and the through hole communicates the inside of the compressor case with the inside of the expander case. In Claim 19, the scroll type expander has a case fixed to the expansion fixed scroll,
The Brayton cycle apparatus according to claim 1, wherein the heat source heats the working fluid in the scroll type expander through the case or the expansion fixed scroll by contacting the case. An exhaust thermal energy recovery device that recovers exhaust thermal energy discharged from an internal combustion engine through an exhaust passage as kinetic energy, the exhaust thermal energy recovery device including a Brayton cycle device having an expander to which a working fluid is sent,
The exhaust heat energy recovery apparatus for an internal combustion engine, wherein the working fluid sent to the expander is heated by heat transmitted from a flow path wall of the exhaust flow path. In claim 22,
The expander is a scroll type expander having an expanded orbiting scroll and an expansion fixed scroll combined with the expanded orbiting scroll,
The Brayton cycle device further includes:
A compressor that interlocks with the orbiting motion of the expansion orbiting scroll to compress the working fluid;
A compressed working fluid path for supplying working fluid from the compressor to the scroll expander;
An exhaust heat energy recovery apparatus for an internal combustion engine, comprising: a heat source for heating the working fluid in the scroll expander by heat transfer, wherein the exhaust of the internal combustion engine is used as the heat source.

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