JP2008002419A - Scroll compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To solve a problem that, there have occurred many cases that a scroll compressor is operated at a low compression ratio accompanied by the recent requirement of the high efficiency of a refrigerating air-conditioning apparatus, and this causes that a turning scroll is separated from a fixed scroll under such an operation condition, and that the scroll compressor is likely overturned and operated. <P>SOLUTION: In a section of becoming maximum or substantially maximum in the upsetting moment in one rotation of the turning motion of the turning scroll 13, an improvement in compression efficiency and the enhancement of reliability can be achieved by restraining upsetting, by arranging a communicating passage in the turning scroll 13 so that oil at a high-pressure part is intermittently supplied to a back pressure space 29 by straddling a sliding partition ring 78 by the turning motion of the turning scroll 13. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a scroll compressor used in an air conditioner, a cooling device such as a refrigerator, or a hot water supply device.

Conventionally, this type of scroll compressor has formed the inner wall of the fixed scroll spiral wrap by the inner wall curve of the fixed scroll spiral wrap extending to the vicinity of the winding end of the outer wall curve of the spiral scroll spiral wrap. Is asymmetric (see Patent Document 1), or is provided with a sliding partition ring concentric with the base circle of the orbiting scroll, and the sliding partition ring is installed on the back of the end plate of the orbiting scroll (see Patent Document 2). is there.
JP 2000-97176 A Japanese Patent Laid-Open No. 7-229486

  In the conventional technique as described in Patent Document 1, the spiral volume of the fixed scroll is asymmetrically wrapped so that the spiral scroll of the orbiting scroll is extended to near the end of the spiral wrap. The wrap height or outer shape can be reduced. In addition, since the compression chamber in which the outer wall of the spiral wrap of the orbiting scroll is formed on the side can minimize heat loss and pressure loss in the suction process of confining the working fluid, the scroll compressor can be made compact, Loss in the working fluid suction process can be reduced.

  However, the working fluid in the compression chamber formed on the outer wall side of the wrap portion of the orbiting scroll and the working fluid in the compression chamber formed on the inner wall side of the wrap portion of the orbiting scroll are compressed with a pressure difference. become. This pressure difference between the compression chambers increases the rollover moment acting on the orbiting scroll. As a result, it will capsize under operating conditions with a low compression ratio, causing an extreme decrease in refrigerant circulation. If the pressing force acting on the back of the orbiting scroll is increased in order to suppress rollover at a low compression ratio, an excessive pressing force is generated on the orbiting scroll under high compression ratio operating conditions, causing galling and abnormal wear. Had.

  Further, in the configuration as described in Patent Document 2, the symmetric splash is effective, but in the asymmetric splash, the working fluid in the compression chamber formed on the outer wall side of the wrap portion of the orbiting scroll, and the orbiting scroll. Since the working fluid in the compression chamber formed on the inner wall side of the lap part has a pressure difference, the overturning moment that acts on the orbiting scroll increases, and as a result, it overturns under operating conditions with a low compression ratio, It had the problem of causing an extreme decrease.

  In particular, when carbon dioxide is used as a refrigerant, the discharge pressure of the compressor is about 7 to 10 times higher than the high-pressure side pressure of a conventional refrigeration cycle using chlorofluorocarbon as a refrigerant. Since it is low and the heat insulation coefficient is large, the overturning moment is larger than that of the conventional chlorofluorocarbon refrigerant. For this reason, if the orbiting scroll component is applied with a back pressure sufficient to prevent it from being separated from the fixed scroll component, the orbiting scroll component is strongly pressed against the fixed scroll component, leading to abnormal wear of the scroll sliding portion and an increase in input. .

Therefore, the present invention has been made in view of the above-described conventional problems, and regardless of the asymmetrical effect, it does not increase back pressure even at a low compression ratio, prevents rollover, and has high reliability without galling or abnormal wear. An object is to provide a scroll compressor to be secured.

  In order to solve the above-described conventional problems, the scroll compressor according to the present invention is configured so that the oil in the high-pressure section is swirled by the orbiting scroll in a section where the rollover moment during one revolution of the orbiting scroll is maximum or substantially maximum. Is provided in the orbiting scroll so as to be intermittently supplied to the back pressure space across the sliding partition ring.

  The scroll compressor according to the present invention can improve the compression efficiency under the low compression ratio operation and can improve the mechanical efficiency under the high compression ratio operation, and can realize the high efficiency and high reliability of the refrigeration air conditioner. it can.

  According to the first aspect of the present invention, in the section where the overturning moment during one rotation of the orbiting scroll is maximum or substantially maximum, the oil in the high pressure section is intermittently moved across the sliding partition ring by the orbiting scroll. The orbiting scroll is provided so as to be supplied to the pressure space.

  As a result, the oil of the high pressure part is supplied to the back pressure space in the section where the rollover moment to roll over the orbiting scroll by the pressure of the compression chamber formed in the compression mechanism is maximized or almost maximized, and the rollover moment is supplied. The pressure in the back pressure space can be controlled following the change in the overturning moment during one rotation, so that it does not overturn even at a low compression ratio, ensuring high reliability and a high compression ratio. Even under these operating conditions, an excessive pressing force is not generated on the orbiting scroll, and a highly efficient scroll compressor can be realized.

  According to a second aspect of the present invention, there is provided a back pressure adjusting valve for maintaining the pressure in the back pressure space at a constant value, and a turning motion of the orbiting scroll in a section in which the overturning moment during one turning motion of the orbiting scroll is maximum or almost maximum. Accordingly, an inlet hole of the back pressure regulating valve is provided at a position where it does not intermittently communicate with the back pressure space.

  As a result, in a section where the rollover moment to roll over the orbiting scroll due to the pressure of the compression chamber formed in the compression mechanism is maximized or almost maximized, following the change of the rollover moment during one rotation, Since the pressure in the pressure space can be controlled, it does not roll over even at a low compression ratio, ensuring high reliability, and even under high compression ratio operating conditions, an excessive pressing force is not generated on the orbiting scroll, and highly efficient scrolling A compressor can be realized.

  According to a third aspect of the present invention, in a section where the overturning moment during one rotation of the orbiting scroll is maximized or substantially maximized, the oil in the high pressure section is intermittently moved across the sliding partition ring by the orbiting scroll. Provided in the orbiting scroll so as to be supplied to the pressure space, a back pressure adjusting valve that maintains the pressure in the back pressure space at a constant value, and a position that does not intermittently communicate with the back pressure space as the orbiting scroll moves. And an inlet hole for the back pressure regulating valve.

As a result, the oil of the high pressure part is supplied to the back pressure space in the section where the rollover moment to roll over the orbiting scroll by the pressure of the compression chamber formed in the compression mechanism is maximized or almost maximized, and the rollover moment is supplied. Since the inlet hole of the back pressure adjustment valve is installed at a position that does not communicate with the back pressure space, the back pressure space communicates with the suction space of the compression chamber through the back pressure adjustment valve. It is possible to control the pressure in the back pressure space by following the change in the overturning moment during one rotation, so that it does not overturn even at a low compression ratio, ensuring high reliability, and a high compression ratio. Even under driving conditions, excessive pressing force is not generated on the orbiting scroll,
A highly efficient scroll compressor can be realized.

  The fourth invention is the first to third inventions in particular, and the inner wall curve of the fixed scroll swirl wrap is formed by the inner wall curve of the fixed scroll swirl wrap extending near the end of the outer wall curve of the swirl scroll swirl wrap. It is what.

  As a result, the working fluid in the compression chamber formed on the outer wall side of the wrap portion of the orbiting scroll and the working fluid in the compression chamber formed on the inner wall side of the wrap portion of the orbiting scroll are compressed with a pressure difference. Therefore, the pressure difference between the compression chambers increases the rollover moment acting on the orbiting scroll. However, according to the first to third inventions, the compression efficiency does not rollover under the low compression ratio operation, and the high compression ratio operation is achieved. Below, a scroll compressor with improved mechanical efficiency can be realized.

The fifth invention is the first to fourth inventions, in particular, using carbon dioxide as the working refrigerant.
With carbon dioxide, which is a high-pressure refrigerant, the back pressure of the orbiting scroll tends to be excessive, and the sliding loss at the thrust sliding portion tends to increase. In the first to fourth inventions, the increase in sliding loss can be suppressed. it can. In addition, in a heat pump hot water supply system using carbon dioxide as a refrigerant, the scroll compressor may be operated at a very low compression ratio due to the characteristics of the system. An efficient scroll compressor can be provided.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. Note that the present invention is not limited to the embodiments.

(Embodiment 1)
FIG. 1 is a longitudinal sectional view of a scroll compressor according to the first embodiment of the present invention, and FIG. 2 is an enlarged sectional view of a main part of a compression mechanism portion of FIG. The operation and action of the scroll compressor configured as shown in the figure will be described below.

  As shown in FIG. 1, the scroll compressor according to the present invention includes a main bearing member 11 of a crankshaft 4 fixed by welding or shrink fitting in an airtight container 1, and a fixed bolted on the main bearing member 11. The scroll-type compression mechanism 2 is configured by sandwiching the orbiting scroll 13 that meshes with the fixed scroll 12 between the scroll 12 and the rotation of the orbiting scroll 13 between the orbiting scroll 13 and the main bearing member 11 is prevented. A rotation restricting mechanism 14 such as an Oldham ring that guides the orbital motion is provided, and the orbiting scroll 13 is eccentrically driven by the eccentric shaft portion 4a at the upper end of the crankshaft 4, thereby causing the orbiting scroll 13 to move in a circular orbit. Thereby, the compression chamber 15 formed between the fixed scroll 12 and the orbiting scroll 13 is small while moving from the outer peripheral side to the center portion. The refrigerant gas is sucked and compressed from the suction pipe 16 communicating with the outside of the hermetic container 1 and the suction port 17 on the outer peripheral portion of the fixed scroll 12, and the refrigerant gas exceeding the predetermined pressure is fixed. The reed valve 19 is pushed open from the discharge port 18 at the center of the scroll 12 and discharged into the sealed container 1 repeatedly.

  A sliding partition ring 78 disposed on the main bearing member 11 is provided on the back surface portion of the orbiting scroll 13, and the high pressure portion that is an inner region of the sliding partition ring 78 is formed by the sliding partition ring 78 while performing the orbiting motion. 30 and a back pressure space 29 set to an intermediate pressure of high pressure and low pressure, which is an outer region. By applying pressure on the back surface, the orbiting scroll 13 is stably pressed against the fixed scroll 12, reducing leakage and performing stable circular orbit movement.

  Further, the fixed scroll 12 includes a back pressure adjusting valve 9 that controls the pressure in the back pressure space 29 on the back surface of the orbiting scroll 13.

  During operation of the compressor, a pump 25 is provided at the other downward end of the crankshaft 4 and is driven simultaneously with the scroll compressor. As a result, the pump 25 sucks up the oil 6 in the oil reservoir 20 provided at the bottom of the hermetic container 1 and supplies it to the compression mechanism 2 through the oil supply hole 26 extending vertically through the crankshaft 4. The supply pressure at this time is substantially equal to the discharge pressure of the scroll compressor, and also serves as a back pressure source for the orbiting scroll 13. As a result, the orbiting scroll 13 does not move away from the fixed scroll 12 and does not come into contact with each other, and the predetermined compression function is stably exhibited.

  A part of the oil 6 supplied in this way is obtained by a supply pressure or its own weight so as to obtain a clearance, between the fitting portion between the eccentric shaft portion 4a and the orbiting scroll 13, and between the crankshaft 4 and the main bearing member 11. The oil enters the bearing portion 66, lubricates the respective portions, falls, and returns to the oil sump 20. Another part of the oil 6 supplied to the high-pressure unit 30 passes through a passage 54 having an opening in the high-pressure unit 30, and slides 13 d between the end plate of the fixed scroll 12 and the wrap 13 c of the orbiting scroll 13, In addition to lubricating the sliding portion 13d and the sliding portion of the rotation restricting mechanism 14 by branching into the back pressure space 29 around the outer peripheral portion of the scroll 13 where the rotation restricting mechanism 14 is located, The back pressure of the orbiting scroll 13 is applied in the back pressure space 29.

  The oil 6 entering the back pressure space 29 is set to an intermediate pressure that is intermediate between the pressures of the high pressure portion 30 and the low pressure side of the compression chamber 15 by the throttle action of the throttle 57. The back pressure space 29 is sealed between the high pressure portion 30 and the high pressure side by an annular partition ring 78. The pressure increases as the incoming oil is filled, and when the pressure exceeds a predetermined pressure, the back pressure adjusting valve 9 Acts to return to the suction portion of the compression chamber 15 and enter.

  The approach of the oil 6 is repeated at a predetermined cycle, and the timing of this repetition is determined by the combination of the repetitive cycle of suction, compression and discharge and the relationship between the pressure reduction setting by the throttle 57 and the pressure setting by the back pressure adjusting mechanism 9. In addition, intentional lubrication of the sliding portion 13d between the fixed scroll 12 and the wrap 13c of the orbiting scroll 13 is achieved. This intentional lubrication is always ensured by the opening of the communication path 10 into the recess 105 by the back pressure regulating valve 9 as described above. The oil 6 supplied to the suction port 17 moves to the compression chamber 15 along with the orbiting motion of the orbiting scroll 13 and serves to prevent leakage between the compression chambers 15.

  FIG. 3 shows the relative position between the opening of the throttle hole 57 and the annular partition ring 78 provided in the main bearing part 11 with respect to the orbiting motion of the orbiting scroll 13 in a state where the end plate 13a of the orbiting scroll 13 is viewed from the lower surface side. Showing the relationship. The orbiting scroll 13 performs the orbiting motion as shown by the arrows in the order of (a) to (d) in the figure. At this time, on the back surface of the end plate 13 a of the orbiting scroll 13, the inner peripheral portion of the annular partition ring 78 forms the high pressure portion 30, and the outer peripheral portion forms the back pressure space 29. Therefore, only when the opening portion of the throttle hole 57 is positioned on the outer peripheral portion of the annular partition ring 78, the high pressure portion 30 and the back pressure space 29 are communicated, and the high pressure oil 6 is supplied to the back pressure space 29. In the figure, the oil 6 can be supplied only in the state (d). A throttle hole 57 is provided in the orbiting scroll 13 at a position corresponding to (d) in a section in which the overturning moment during one revolution of the orbiting scroll 13 is maximum or substantially maximum.

With the above-described configuration, the oil 6 of the high-pressure part 30 is supplied to the back pressure space 29 in a section where the rollover moment for overturning the orbiting scroll 13 by the pressure in the compression chamber 15 formed in the compression mechanism is maximized or almost maximized. The pressure (discharge pressure) that overcomes the overturning moment is introduced and the pressure in the back pressure space can be controlled following the change in the overturning moment during one rotation, so it does not overturn even at a low compression ratio, and is high In addition to ensuring reliability, even under high compression ratio operating conditions, an excessive pressing force is not generated on the orbiting scroll, and a highly efficient scroll compressor can be realized.

(Embodiment 2)
FIG. 4 is an enlarged cross-sectional view of the main part of the compression mechanism part of the scroll compressor according to the second embodiment of the present invention. As shown in FIG. 4, the inlet hole 83 of the back pressure regulating valve 9 is closed by the end plate 13 a of the orbiting scroll 13 when the orbiting scroll 13 is in the position shown in FIG. Thus, the back pressure space 29 and the suction space of the compression chamber 15 do not communicate with each other. 4B, the inlet hole 83 of the back pressure adjusting valve 9 communicates with the back pressure space 29, and the back pressure space 29 and the suction space of the compression chamber 15 communicate with each other. It becomes.

  An inlet hole 83 of the back pressure regulating valve 9 is provided at a position (a) in a section where the overturning moment during one revolution of the orbiting scroll 13 is maximum or substantially maximum.

  With the above-described configuration, the suction chamber of the compression chamber 15 from the back pressure space 29 in a section where the rollover moment for overturning the orbiting scroll 13 by the pressure of the compression chamber 15 formed in the compression mechanism is maximized or almost maximized. The pressure of the back pressure space 29 can be controlled by following the change of the overturning moment during one rotation to maintain the pressure to overcome the overturning moment without the oil 6 moving to In addition, while ensuring high reliability, even under operating conditions with a high compression ratio, an excessive pressing force is not generated on the orbiting scroll 13, and a highly efficient scroll compressor can be realized.

(Embodiment 3)
FIG. 5 is an enlarged cross-sectional view of the main part of the compression mechanism of the scroll compressor according to the third embodiment of the present invention. As shown in FIG. 5, when the orbiting scroll 13 is turned, when the position is as shown in FIG. 5A, the opening portion of the throttle hole 57 is located on the outer peripheral portion of the annular partition ring 78, and the high pressure portion. 30 and the back pressure space 29 are communicated, and high pressure oil 6 is supplied to the back pressure space 29. At this time, the inlet hole 83 of the back pressure adjusting valve 9 is closed by the end plate 13a of the orbiting scroll 13, and the back pressure space 29 and the suction space of the compression chamber 15 do not communicate with each other. On the other hand, when the position is as shown in FIG. 4B, the opening portion of the throttle hole 57 is located on the inner peripheral portion of the annular partition ring 78, and the high pressure portion 30 and the back pressure space 29 are not communicated with each other. The oil 6 is not supplied to the back pressure space 29. The inlet hole 83 of the back pressure adjusting valve 9 communicates with the back pressure space 29, and the back pressure space 29 and the suction space of the compression chamber 15 communicate with each other.

  A throttle hole 57 and an inlet hole 83 for the back pressure adjustment valve 9 are provided at a position (a) in a section where the rollover moment during one rotation of the orbiting scroll 13 is maximized or substantially maximized.

  With the above-described configuration, the suction chamber of the compression chamber 15 from the back pressure space 29 in a section where the rollover moment for overturning the orbiting scroll 13 by the pressure of the compression chamber 15 formed in the compression mechanism is maximized or almost maximized. In order to introduce the pressure (discharge pressure) that overcomes the overturning moment by supplying the oil 6 of the high-pressure part 30 to the back pressure space 29 and introducing the pressure (discharge pressure), the change of the overturning moment during one rotation is followed. Thus, the pressure in the back pressure space 29 can be controlled and does not overturn even at a low compression ratio, ensuring high reliability, and generating an excessive pressing force on the orbiting scroll 13 even under conditions of a high compression ratio. Therefore, a highly efficient scroll compressor can be realized.

(Embodiment 4)
In the scroll compressor according to the fifth embodiment of the present invention, the spiral of the fixed scroll 12 is swung by the inner wall curve of the spiral wrap 12b of the fixed scroll 12 extending to the vicinity of the winding end of the outer wall curve of the spiral wrap 13b of the orbiting scroll 13. The inner wall of the wrap 12b is formed (not shown). As a result, the working fluid in the compression chamber formed on the outer wall side of the wrap portion 13b of the orbiting scroll 13 and the working fluid in the compression chamber formed on the inner wall side of the wrap portion 13b of the orbiting scroll 13 have a pressure difference. The pressure difference between the compression chambers increases the rollover moment acting on the orbiting scroll 13, but the first to third inventions do not rollover under low compression ratio operation and improve the compression efficiency. It is possible to realize a scroll compressor with improved mechanical efficiency under high compression ratio operation.

(Embodiment 5)
In the scroll compressor according to the fifth embodiment of the present invention, the refrigerant is a high-pressure refrigerant, for example, carbon dioxide (not shown). Even in a scroll compressor in which the back pressure of the orbiting scroll 13 is excessive and the sliding loss at the thrust sliding portion tends to increase, the increase in sliding loss can be suppressed. In addition, in a heat pump hot water supply system using carbon dioxide as a refrigerant, the scroll compressor may be operated at a very low compression ratio (approximately 1.5 or less) due to the characteristics of the system. Even a highly efficient scroll compressor can be provided.

  As described above, the scroll compressor according to the present invention can achieve improved compression efficiency under low compression ratio operation and improved mechanical efficiency under high compression ratio operation, and the air scroll is not limited to a working fluid as a refrigerant. The present invention can also be applied to a scroll fluid machine such as a compressor, a vacuum pump, an oil-free compressor, and a scroll type expander.

Sectional drawing of the scroll compressor in Embodiment 1 of this invention The principal part expanded sectional view of the compression mechanism part of the scroll compressor in Embodiment 1 of this invention The top view which shows the positional relationship of the turning scroll and fixed scroll in the predetermined turning position of the turning scroll in Embodiment 1 of this invention. The principal part expanded sectional view of the compression mechanism part of the scroll compressor in Embodiment 2 of this invention The principal part expanded sectional view of the compression mechanism part of the scroll compressor in Embodiment 3 of this invention

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Airtight container 2 Compression mechanism 3 Electric motor 3a Stator 3b Rotor 4 Crankshaft 4a Main shaft part 6 Oil 7 Oil supply mechanism 9 Back pressure adjustment valve 11 Main bearing member 12 Fixed scroll 12a End plate 12b Wrap 12c Groove 13 Turning scroll 13a End plate 13b Wrap 14 Rotation Restricting Mechanism 15 Compression Chamber 16 Suction Pipe 17 Suction Port 18 Discharge Port 19 Reed Valve 29 Back Pressure Space 57 Throttle Hole 78 Sliding Partition Ring 83 Inlet Hole

Claims (5)

By engaging the fixed scroll and the orbiting scroll where the spiral wrap rises from the end plate, and rotating the orbiting scroll along the circular orbit under the regulation of rotation, the volume is changed and the suction, compression, and discharge are performed. A compression chamber is formed, and a ring-shaped groove is provided in a bearing member that substantially supports the orbiting scroll and its rear face side, and high pressure is applied to the bearing member and the central part on the rear face side by lubricating oil. The high-pressure part and the high-pressure part are partitioned by a ring-shaped sliding partition ring having a joint part attached to the groove part, and a predetermined pressure lower than the high-pressure part is applied to the outer peripheral part of the rear surface of the orbiting scroll end plate In a scroll compressor provided with a back pressure space, in a section where the overturning moment during one rotation of the orbiting scroll is maximum or almost maximum. The scroll compression is provided in the orbiting scroll so that the oil in the high-pressure portion is intermittently supplied to the back pressure space across the sliding partition ring by the orbiting motion of the orbiting scroll. Machine. By engaging the fixed scroll and the orbiting scroll where the spiral wrap rises from the end plate, and rotating the orbiting scroll along the circular orbit under the regulation of rotation, the volume is changed and the suction, compression, and discharge are performed. A compression chamber is formed, and a ring-shaped groove is provided in a bearing member that substantially supports the orbiting scroll and its rear face side, and high pressure is applied to the bearing member and the central part on the rear face side by lubricating oil. The high-pressure part and the high-pressure part are partitioned by a ring-shaped sliding partition ring having a joint part attached to the groove part, and a predetermined pressure lower than the high-pressure part is applied to the outer peripheral part of the rear surface of the orbiting scroll end plate In a scroll compressor provided with a back pressure space, a back pressure adjusting valve for maintaining the pressure in the back pressure space at a constant value, and a turning motion of the orbiting scroll during one rotation Scroll compression characterized by comprising an inlet hole of the back pressure regulating valve at a position not intermittently communicating with the back pressure space with a turning motion of the orbiting scroll in a section where the covering moment is maximum or almost maximum. Machine. By engaging the fixed scroll and the orbiting scroll where the spiral wrap rises from the end plate, and rotating the orbiting scroll along the circular orbit under the regulation of rotation, the volume is changed and the suction, compression, and discharge are performed. A compression chamber is formed, and a ring-shaped groove is provided in a bearing member that substantially supports the orbiting scroll and its rear face side, and high pressure is applied to the bearing member and the central part on the rear face side by lubricating oil. The high-pressure part and the high-pressure part are partitioned by a ring-shaped sliding partition ring having a joint part attached to the groove part, and a predetermined pressure lower than the high-pressure part is applied to the outer peripheral part of the rear surface of the orbiting scroll end plate In a scroll compressor provided with a back pressure space, in a section where the overturning moment during one rotation of the orbiting scroll is maximum or almost maximum. The oil in the high-pressure portion is provided in the orbiting scroll so as to be intermittently supplied to the back pressure space across the sliding partition ring by the orbiting motion of the orbiting scroll, and the pressure in the back pressure space is And a back pressure adjusting valve that maintains a constant value, and a scroll that includes an inlet hole of the back pressure adjusting valve at a position that does not intermittently communicate with the back pressure space as the orbiting scroll moves. Compressor. The inner wall of the spiral wrap of the fixed scroll is formed by the inner wall curve of the spiral wrap of the fixed scroll extending to the vicinity of the winding end of the outer wall curve of the spiral wrap of the orbiting scroll. Scroll compressor. 5. The scroll compressor according to claim 1, wherein carbon dioxide is used as a working refrigerant.

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