EP2098730A1 - Strömungsmaschine - Google Patents

Strömungsmaschine Download PDF

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Publication number
EP2098730A1
EP2098730A1 EP07832306A EP07832306A EP2098730A1 EP 2098730 A1 EP2098730 A1 EP 2098730A1 EP 07832306 A EP07832306 A EP 07832306A EP 07832306 A EP07832306 A EP 07832306A EP 2098730 A1 EP2098730 A1 EP 2098730A1
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EP
European Patent Office
Prior art keywords
casing
expansion mechanism
refrigerant
fluid machine
side mounting
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP07832306A
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English (en)
French (fr)
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EP2098730B1 (de
EP2098730A4 (de
Inventor
Eiji Kumakura
Katsumi Sakitani
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Daikin Industries Ltd
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Daikin Industries Ltd
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Filing date
Publication date
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Publication of EP2098730A1 publication Critical patent/EP2098730A1/de
Publication of EP2098730A4 publication Critical patent/EP2098730A4/de
Application granted granted Critical
Publication of EP2098730B1 publication Critical patent/EP2098730B1/de
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Classifications

    • 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
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • F04C11/001—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle
    • F04C11/003—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle having complementary function
    • 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
    • F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F01C1/32—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F01C1/02 and relative reciprocation between the co-operating members
    • F01C1/322—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F01C1/02 and relative reciprocation between the co-operating members with vanes hinged to the outer member and reciprocating with respect to the outer member
    • 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
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F01C21/108—Stators; Members defining the outer boundaries of the working chamber with an axial surface, e.g. side plates
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • 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
    • F04C2230/00—Manufacture
    • F04C2230/60—Assembly methods

Definitions

  • a fourth aspect of the invention is the fluid machine according to the second aspect of the invention, wherein the fluid machine is configured so that the refrigerant is introduced from the refrigerant circuit (20) directly into the compression mechanism (50) and the compressed refrigerant is discharged directly to the outside of the casing (31), and the compression mechanism (50) is fixed through the mounting plate (101) to the casing (31).
  • the mechanism-side mounting parts (104) are arranged to reduce the surface temperature differences between the expansion mechanism (60) and regions of the casing (31) near to the expansion mechanism (60), thereby reducing heat input from the high-temperature side to the low-temperature side. This further prevents performance degradation and decrease in power recovery effect.
  • This embodiment is directed to an air conditioner including a compression/expansion unit that is a fluid machine according to the present invention.
  • the air conditioner (1) includes a refrigerant circuit (20). Connected in the refrigerant circuit (20) are the compression/expansion unit (30), an outdoor heat exchanger (23), an indoor heat exchanger (24), a first four-way selector valve (21) and a second four-way selector valve (22). Furthermore, the refrigerant circuit (20) is filled with carbon dioxide (CO2) as refrigerant.
  • CO2 carbon dioxide
  • the compression mechanism (50) is connected at its discharge side (a discharge pipe (37)) to the first port of the first four-way selector valve (21) and connected at its suction side (suction pipes (36)) to the fourth port of the first four-way selector valve (21).
  • the expansion mechanism (60) is connected at its outflow side (an outlet pipe (39)) to the first port of the second four-way selector valve (22) and connected at its inflow side (an inlet pipe (38)) to the fourth port of the second four-way selector valve (22).
  • the outdoor heat exchanger (23) is connected at one end to the second port of the second four-way selector valve (22) and connected at the other end to the third port of the first four-way selector valve (21).
  • the indoor heat exchanger (24) is connected at one end to the second port of the first four-way selector valve (21) and connected at the other end to the third port of the second four-way selector valve (22).
  • the compression/expansion unit (30) includes a casing (31) that is a vertically long, cylindrical, closed container. Inside the casing (31), the compression mechanism (50), the electric motor (45) and the expansion mechanism (60) are arranged in bottom to top order. Furthermore, refrigerating machine oil serving as lubricating oil is accumulated at the bottom of the casing (31). In other words, inside the casing (31), refrigerating machine oil is accumulated towards the compression mechanism (50).
  • the two lower eccentric parts (58, 59) are formed with a larger diameter than the main spindle (44), in which the lower of the two constitutes a first lower eccentric part (58) and the upper constitutes a second lower eccentric part (59).
  • the first lower eccentric part (58) and the second lower eccentric part (59) have opposite directions of eccentricity with respect to the axis of the main spindle (44).
  • the compression mechanism (50) is constituted by a so-called oscillating piston rotary compressor.
  • the compression mechanism (50) includes two cylinders (51, 52) and two pistons (57).
  • a rear head (55), the first cylinder (51), a middle plate (56), the second cylinder (52) and a front head (54) are stacked in bottom to top order.
  • the first and second cylinders (51, 52) contain their respective cylindrical pistons (57) disposed, one in the interior of each cylinder. Although not shown, a plate-shaped blade extends from the side surface of each piston (57) and is supported through a swing bush to the associated cylinder (51, 52).
  • the piston (57) in the first cylinder (51) engages with the first lower eccentric part (58) of the rotary shaft (40).
  • the piston (57) in the second cylinder (52) engages with the second lower eccentric part (59) of the rotary shaft (40).
  • Each of the pistons (57, 57) is in slidable contact at its inner periphery with the outer periphery of the associated lower eccentric part (58, 59) and in slidable contact at its outer periphery with the inner periphery of the associated cylinder (51, 52).
  • a compression chamber (53) is defined between the outer periphery of each of the pistons (57, 57) and the inner periphery of the associated cylinder (51, 52).
  • the first and second cylinders (51, 52) have their respective suction ports (32) formed, one in each cylinder.
  • Each suction port (32) radially passes through the associated cylinder (51, 52) and its distal end opens on the inner periphery of the cylinder (51, 52). Furthermore, each suction port (32) is extended to the outside of the casing (31) by the associated suction pipe (36).
  • joint parts (67) joined to the respective mechanism-side mounting parts (104) are formed to extend outward from the outer periphery of the front head (61).
  • the joint parts (67) are formed at three points along the circumference of the front head (61) at equally spaced 120° intervals.
  • each joint part (67) has a bolt hole (68) formed in the center thereof.
  • the rim of the bolt hole (68) is formed to protrude upward.
  • each mechanism-side mounting part (104) has a bolt hole (104a) formed in the center thereof.
  • the rim of the bolt hole (104a) is formed to protrude downward. This reduces the contact area between the mechanism-side mounting parts (104) and the joint parts (67).
  • the casing-side mounting parts (105) are formed to extend radially outward from the outer periphery of the mounting plate (101). In this embodiment, the casing-side mounting parts (105) are formed at three points along the circumference of the mounting plate (101) at equally spaced 120° intervals.
  • the casing-side mounting parts (105) are welded to the inside surface of the casing (31). Between each pair of adjacent casing-side mounting parts (105), a plate outside clearance (108) from the casing (31) is formed to have a given width.
  • a sector of the mounting plate (101) lying between each mechanism-side mounting part (104) and the adjacent casing-side mounting part (105) has a smaller cross-sectional area across the circumference than a sector of the mounting plate (101) lying within the casing-side mounting part (105).
  • the mounting plate (101) has a plurality of through holes (106, 107) for reducing the cross-sectional area across the circumference.
  • the first piston (75) is slidably engaged at the outer periphery with the inner periphery of the first cylinder (71), is in slidable contact at one end surface thereof with the front head (61) and is in slidable contact at the other end surface with the middle plate (63).
  • first cylinder (71) its inner periphery defines a first expansion chamber (72) together with the outer periphery of the first piston (75).
  • second piston (85) is slidably engaged at the outer periphery with the inner periphery of the second cylinder (81), is in slidable contact at one end surface thereof with the rear head (62) and is in slidable contact at the other end surface with the middle plate (63).
  • the second cylinder (81) its inner periphery defines a second expansion chamber (82) together with the outer periphery of the second piston (85).
  • each cylinder (71, 81) passes through the associated cylinder (71, 81) in a thickness direction and opens on the inner periphery of the cylinder (71, 81).
  • These bush holes (78, 88) constitute through holes.
  • the cylinders (71, 81) are provided with pairs of bushes (77, 87), each cylinder with one pair of bushes.
  • Each bush (77, 87) is a small piece formed so that its inside surface is flat and its outside surface is arcuate.
  • the pair of bushes (77, 87) are inserted into the associated bush hole (78, 88) to sandwich the associated blade (76, 86) therebetween.
  • Each bush (77, 87) slides with the inside surface on the associated blade (76, 86) and slides with the outside surface on the associated cylinder (71, 81).
  • Each blade (76, 86) integral with the piston (75, 85) is supported through the associated bushes (77, 87) to the associated cylinder (71, 81) and is free to angularly move with respect to and free to enter and retract from the cylinder (71, 81).
  • the middle plate (63) has a communicating channel (64) formed therein.
  • the communicating channel (64) passes through the middle plate (63) in the thickness direction.
  • one end of the communicating channel (64) opens at a position to the right of the first blade (76).
  • the other end of the communicating channel (64) opens at a position to the left of the second blade (86).
  • the communicating channel (64) extends obliquely with respect to the thickness direction of the middle plate (63) and brings about communication between the first low-pressure chamber (74) and the second high-pressure chamber (83).
  • the internal space of the casing (31) contains a heat insulator (90, 96) covering the entire exposed surface of the expansion mechanism (60) within the casing (31) and passed through by the rotary shaft (40).
  • the heat insulator (90, 96) is divided in the axial direction of the rotary shaft (40) into a first heat insulator (90) and a second heat insulator (96) that are bounded by each other in line with the mounting plate (101).
  • the heat insulator (90, 96) extends also into the plate outside clearances (108) from the casing (31) between the adjacent casing-side mounting parts (105). More specifically, the side surface of the mounting plate (101) is covered with extensions from the under surface of the second heat insulator (96). Alternatively, the side surface of the mounting plate (101) may be covered with extensions from the top surface of the first heat insulator (90).
  • Actions of the air conditioner (10) will be described below. Here, a description is given first of the action of the air conditioner (10) in cooling operation, then the action thereof in heating operation and then the action of the expansion mechanism (60).
  • the first four-way selector valve (21) and the second four-way selector valve (22) are switched to the positions shown in the broken lines in FIG. 1 .
  • the electric motor (45) of the compression/expansion unit (30) is energized, refrigerant circulates through the refrigerant circuit (20) so that the refrigerant circuit (20) operates in a vapor compression refrigeration cycle.
  • the refrigerant compressed by the compression mechanism (50) is discharged through the discharge pipe (37) out of the compression/expansion unit (30). In this state, the refrigerant pressure is higher than the critical pressure.
  • the discharged refrigerant is sent to the outdoor heat exchanger (23) and therein releases heat to the outdoor air.
  • the high-pressure refrigerant having released heat in the outdoor heat exchanger (23) passes through the inlet pipe (38) and then flows into the expansion mechanism (60). In the expansion mechanism (60), the high-pressure refrigerant expands and power is recovered from the high-pressure refrigerant.
  • the low-pressure refrigerant obtained by expansion is sent through the outlet pipe (39) to the indoor heat exchanger (24).
  • the refrigerant having flowed therein takes heat from room air to evaporate, thereby cooling the room air.
  • the low-pressure gas refrigerant having flowed out of the indoor heat exchanger (24) passes through the suction pipes (36) and is then sucked through the suction ports (32) into the compression mechanism (50).
  • the compression mechanism (50) compresses the sucked refrigerant and discharges it.
  • the first four-way selector valve (21) and the second four-way selector valve (22) are switched to the positions shown in the solid lines in FIG. 1 .
  • the electric motor (45) of the compression/expansion unit (30) is energized, refrigerant circulates through the refrigerant circuit (20) so that the refrigerant circuit (20) operates in a vapor compression refrigeration cycle.
  • the refrigerant compressed by the compression mechanism (50) is discharged through the discharge pipe (37) out of the compression/expansion unit (30). In this state, the refrigerant pressure is higher than the critical pressure.
  • the discharged refrigerant is sent to the indoor heat exchanger (24). In the indoor heat exchanger (24), the refrigerant having flowed therein releases heat to room air, thereby heating the room air.
  • the refrigerant having released heat in the indoor heat exchanger (24) passes through the inlet pipe (38) and then flows into the expansion mechanism (60). In the expansion mechanism (60), the high-pressure refrigerant expands and power is recovered from the high-pressure refrigerant.
  • the low-pressure refrigerant obtained by expansion is sent through the outlet pipe (39) to the outdoor heat exchanger (23) and therein takes heat from the outdoor air to evaporate.
  • the low-pressure gas refrigerant having flowed out of the outdoor heat exchanger (23) passes through the suction pipes (36) and is then sucked through the suction ports (32) into the compression mechanism (50).
  • the compression mechanism (50) compresses the sucked refrigerant and discharges it.
  • the action of the expansion mechanism (60) is described with reference to FIG. 8 .
  • the increase in the volume of the expansion chamber (66) continues until just before the angle of rotation of the rotary shaft (40) reaches 360°.
  • the refrigerant in the expansion chamber (66) expands during the increase in the volume of the expansion chamber (66).
  • the expansion of the refrigerant causes the rotary shaft (40) to be driven into rotation.
  • the refrigerant in the first low-pressure chamber (74) flows through the communicating channel (64) into the second high-pressure chamber (83) while expanding.
  • the second low-pressure chamber (84) starts to be communicated with the outlet port (35) at a point of time when the rotary shaft (40) is at an angle of rotation of 0°.
  • the refrigerant starts to flow out of the second low-pressure chamber (84) to the outlet port (35).
  • low-pressure refrigerant obtained by expansion flows out of the second low-pressure chamber (84).
  • bolts (not shown) are inserted into the bolt holes (68) in the front head (61) and the bolt holes (104a) in the mechanism-side mounting parts (104) and then tightened.
  • the first heat insulator (90) is mounted to the expansion mechanism (60) from below the mounting plate (101), and the second heat insulator (96) is mounted to the expansion mechanism (60) from above. Since in this manner the heat insulator (90, 96) is divided into the first heat insulator (90) and the second heat insulator (96), the heat insulator (90, 96) can be easily assembled.
  • the first heat insulator (90) partitions the internal space of the casing (31) into the first space (48) in which the expansion mechanism (60) is placed and the second space (49) in which the compression mechanism (50) is placed, the first space (48) is kept at low temperature and high density and the second space (49) is kept at high temperature and low density.
  • the interior of the casing (31) is kept under high-temperature and high-pressure conditions, thereby providing a so-called high-pressure dome fluid machine.
  • the low-temperature expansion mechanism (60) significantly different in temperature from the atmosphere in the rest of the interior of the casing (31) is fixed through the mounting plate (101) to the casing (31), this prevents direct fixation between the casing (31) and the expansion mechanism (60) significantly different in temperature from the casing (31) that would conventionally be done. Furthermore, since the joints between the mounting plate (101) and the casing (31) are the casing-side mounting parts (105) only, the heat transfer area is reduced as compared with the case where the mounting plate (101) is joined over the entire circumference to the casing (31). This reduces the amount of heat exchange due to heat conduction between low-temperature refrigerant in the expansion mechanism (60) and high-temperature refrigerant in the compression mechanism (50).
  • the mechanism-side mounting parts (104) are circumferentially offset from the casing-side mounting parts (105), the heat transfer paths can be extended as compared with the case where each pair of mechanism- and casing-side mounting parts are arranged at the same circumferential angle. Thus, the heat resistance is increased, thereby reducing heat exchange between the expansion mechanism (60) and the casing (31).
  • a sector of the mounting plate (101) lying between each mechanism-side mounting part (104) and the adjacent casing-side mounting part (105) has a smaller cross-sectional area across the circumference than a sector of the mounting plate (101) lying within the casing-side mounting part (105), this reduces the heat transfer areas of the heat transfer paths in the mounting plate (101). Furthermore, since the mounting plate (101) has a sheet metal structure formed of a thin metal sheet, the heat transfer areas of the heat transfer paths are further reduced. Moreover, since the mounting plate (101) has through holes (106, 107) formed therein, the heat transfer areas of the heat transfer paths are further reduced.
  • first heat insulator (90) isolates the first space (48) located around the low-temperature expansion mechanism (60) and having a significant temperature difference from the atmosphere in the rest of the interior of the casing (31), this effectively prevents occurrence of refrigerant convection.
  • the heat insulator (90, 96) covers the entire exposed surface of the expansion mechanism (60) within the casing (31), this prevents heat exchange between the internal space of the casing (31) and the expansion mechanism (60) covered with the heat insulator (90, 96). Therefore, heat exchange between the expansion mechanism (60) and the casing (31) is further reduced.
  • the mounting plate (101) is also covered with the heat insulator (90, 96), heat exchange between the mounting plate (101) and refrigerant is prevented, whereby heat exchange between the expansion mechanism (60) and the casing (31) is further reduced. This reduces the amount of heat exchange due to heat conduction between low-temperature refrigerant in the expansion mechanism (60) and high-temperature refrigerant in the compression mechanism (50).
  • the low-temperature expansion mechanism (60) significantly different in temperature from the atmosphere of the rest of the interior of the casing (31) is not fixed directly to the casing (31) but only the casing-side mounting parts (105) are fixed to the casing (31) through the mounting plate (101) welded to the casing (31), thereby reducing heat exchange due to heat conduction between the high-temperature casing (31) and the low-temperature expansion mechanism (60). This further prevents performance degradation and decrease in power recovery effect.
  • the mechanism-side mounting parts (104) of the ring-shaped mounting plate (101) are circumferentially offset from the casing-side mounting parts (105) thereof to extend the heat transfer paths and thereby increase the heat resistance, this further prevents performance degradation and decrease in power recovery effect.
  • the heat transfer areas of the heat transfer paths in the mounting plate (101) are reduced to reduce heat exchange between the expansion mechanism (60) and the casing (31), such as by forming the mounting plate (101) in a sheet metal structure formed of a thin metal sheet, forming a plurality of through holes (106, 107) in the mounting plate (101) and protruding the mechanism-side mounting parts (104) and the joint parts (67), this further prevents performance degradation and decrease in power recovery effect.
  • the heat insulator (90, 96) covers the entire exposed surface of the expansion mechanism (60) within the casing (31), this prevents heat exchange between the second space (48) in the casing (31) and the expansion mechanism (60) covered with the heat insulator (90, 96) and thereby prevents performance degradation and decrease in power recovery effect.
  • the heat insulator (90, 96) extends also in the plate outside clearances (108) to prevent heat exchange between the mounting plate (101) and refrigerant and thereby reduce heat exchange between the expansion mechanism (60) and the casing (31), this further prevents performance degradation and decrease in power recovery effect.
  • the heat insulator (90, 96) is divided in the axial direction of the rotary shaft (40) into two parts bounded by each other in line with the mounting plate (101), the heat insulator (90, 96) can be easily assembled with the other components, which reduces the production cost.
  • the mechanism-side mounting parts (104) may be arranged to connect regions of the expansion mechanism (60) higher in surface temperature than the rest thereof to regions of the casing (31) near to the expansion mechanism (60) and lower in surface temperature than the rest thereof.
  • the through holes (106, 107) are not given in the figure.
  • the expansion mechanism (60) has a generally circumferential, surface temperature distribution in which the surface temperature decreases in order from Region A to Region F when viewed in the axial direction.
  • Region A is at 30°C that is a suction temperature
  • Region F is at 0°C that is a discharge temperature.
  • the casing (31) has a generally circumferential, surface temperature distribution in which the surface temperature decreases in order from Region A to Region F.
  • Region A is at 90°C that is a discharge temperature of the compression mechanism (50)
  • Region F is at a low temperature (approximately 0°C) that is a discharge temperature of the expansion mechanism (60).
  • the mechanism-side mounting parts (104) located at one ends of the heat transfer paths in the mounting plate (101) are arranged to reduce the surface temperature differences between the expansion mechanism (60) and regions of the casing (31) near to the expansion mechanism (60). Therefore, heat input from the high-temperature side to the low-temperature side is reduced. This reduces the amount of heat exchange due to heat conduction between low-temperature refrigerant in the expansion mechanism (60) and high-temperature refrigerant in the compression mechanism (50). Hence, performance degradation and decrease in power recovery effect of the compression/expansion unit (30) can be prevented.
  • the casing-side mounting parts (105) may be arranged to connect regions of the expansion mechanism (60) higher in surface temperature than the rest thereof to regions of the casing (31) near to the expansion mechanism (60) and lower in surface temperature than the rest thereof.
  • the through holes (106, 107) are not given in the figure.
  • the expansion mechanism (60) is kept at low temperatures as a whole. Therefore, it is desirable to arrange the casing-side mounting parts (105) to avoid Region A of the casing (31) having the highest surface temperature. Furthermore, the casing (31) naturally has a low-temperature region between the inlet pipe (38) and the outlet pipe (39). Therefore, it is desirable to dispose a casing-side mounting part (105) in this region.
  • the casing-side mounting parts (105) located at one ends of the heat transfer paths in the mounting plate (101) are arranged to reduce the surface temperature differences between the expansion mechanism (60) and regions of the casing (31) near to the expansion mechanism (60). Therefore, heat input from the high-temperature side to the low-temperature side is reduced.
  • a heat insulating spacer (110) made of a heat insulating material may be disposed between each pair of the mechanism-side mounting part (104) and the joint part (67) of the expansion mechanism (60) joined to the mechanism-side mounting part (104). Since the heat insulating spacers (110) are disposed in the vicinity of the expansion mechanism (60) always kept at relatively low temperatures, they may be made of a low heat-resistance material. Therefore, the freedom of choice of materials is high.
  • the above embodiment of the present invention may have the following configurations.
  • the expansion mechanism (60) is constituted by an oscillating piston rotary expander
  • the expansion mechanism (60) may be constituted by a rolling piston rotary expander.
  • the blade (76, 86) in each of the rotary mechanisms (70, 80) is formed separately from the associated piston (75, 85).
  • the distal end of the blade (76, 86) is pushed against the outer periphery of the associated piston (75, 85), whereby the blade (76, 86) moves forward and backward with movement of the associated piston (75, 85).
  • the compression mechanism (50) is constituted by an oscillating piston rotary compressor and the expansion mechanism (60) is constituted by an oscillating piston rotary expander
  • the mechanisms may be constituted by a scroll compressor and a scroll expander.
  • the plate outside clearances (108) between the mounting plate (101) and the casing (31) are at a certain width (for example, 5 mm) or more and the refrigerant accumulates in the plate outside clearance (108), there is no need to extend the heat insulator (90, 96) into the clearances.
  • the resin-based material making up a common heat insulator (90, 96) has a heat conductivity of 0.3 w/m-k
  • carbon dioxide refrigerant in the space around the expansion mechanism (60) has a heat conductivity of 0.07 w/m-k. Therefore, carbon dioxide refrigerant has a one-order lower heat conductivity than the resin-based material. Since thus the coefficient of heat transfer of gas refrigerant is smaller than that of the heat insulator (90, 96), heat exchange is not increased but rather reduced.
  • each set of mounting parts may be composed of two, four, or more mounting parts.
  • the mechanism-side mounting parts (104) are preferably circumferentially offset from the casing-side mounting parts (105).
  • R410A, R407C or isobutane may be used instead as refrigerant.
  • the electric motor (45) is disposed above the compression mechanism (50) in the second space (49), it may be disposed below the compression mechanism (50).
  • the present invention is useful for a fluid machine in which a compression mechanism and an expansion mechanism are contained in a single casing.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressor (AREA)
EP07832306.0A 2006-11-24 2007-11-21 Strömungsmaschine Active EP2098730B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2006317127A JP4997935B2 (ja) 2006-11-24 2006-11-24 流体機械
PCT/JP2007/072576 WO2008062839A1 (en) 2006-11-24 2007-11-21 Fluid machine

Publications (3)

Publication Number Publication Date
EP2098730A1 true EP2098730A1 (de) 2009-09-09
EP2098730A4 EP2098730A4 (de) 2014-02-19
EP2098730B1 EP2098730B1 (de) 2015-03-04

Family

ID=39429769

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07832306.0A Active EP2098730B1 (de) 2006-11-24 2007-11-21 Strömungsmaschine

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JP (1) JP4997935B2 (de)
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DE102012019040A1 (de) * 2012-09-28 2014-04-03 Harald Teinzer Scrollmotor

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EP1724436A1 (de) * 2004-03-10 2006-11-22 Daikin Industries, Ltd. Rotationsexpansionsmaschine

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JPH086702B2 (ja) * 1988-10-31 1996-01-29 株式会社東芝 ロータリコンプレッサ
JP4462023B2 (ja) * 2003-09-08 2010-05-12 ダイキン工業株式会社 ロータリ式膨張機
JP2005240562A (ja) * 2004-02-24 2005-09-08 Nippon Soken Inc スクロール型圧縮機
JP4617831B2 (ja) * 2004-11-02 2011-01-26 ダイキン工業株式会社 流体機械
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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012019040A1 (de) * 2012-09-28 2014-04-03 Harald Teinzer Scrollmotor
DE102012019040B4 (de) * 2012-09-28 2014-08-14 Harald Teinzer Scrollmotor

Also Published As

Publication number Publication date
JP4997935B2 (ja) 2012-08-15
WO2008062839A1 (en) 2008-05-29
ES2536770T3 (es) 2015-05-28
JP2008128183A (ja) 2008-06-05
EP2098730B1 (de) 2015-03-04
EP2098730A4 (de) 2014-02-19

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