CN211737453U - Scroll compressor and refrigeration device with same - Google Patents
Scroll compressor and refrigeration device with same Download PDFInfo
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- CN211737453U CN211737453U CN202020214708.8U CN202020214708U CN211737453U CN 211737453 U CN211737453 U CN 211737453U CN 202020214708 U CN202020214708 U CN 202020214708U CN 211737453 U CN211737453 U CN 211737453U
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Abstract
A scroll compressor and a refrigeration device having the same, which can suppress poor lubrication between a floating member and a movable scroll. A scroll compressor (1) is provided with: a compression mechanism (20) having a fixed scroll (21) and a movable scroll (26); a drive shaft (40) for driving the orbiting scroll (26) to rotate; and a floating member (50) having a scroll support part (51) that supports the orbiting scroll (26), a support part (53) that rotatably supports the drive shaft (40), and a connection part (55) that connects the scroll support part (51) and the shaft support part (53). The shortest distance between the end of the outer peripheral surface of the shaft support part (53) on the movable scroll (26) side and the inner surface of the coupling part (55) is set to the 1 st wall thickness (t). The 1 st wall thickness (t) is smaller than the maximum length (L) in the radial direction of the shaft support part (53).
Description
Technical Field
The utility model relates to a scroll compressor and refrigerating plant who has this scroll compressor.
Background
Conventionally, a scroll compressor is known which includes a compression mechanism having a fixed scroll and a movable scroll, and a drive shaft for driving the movable scroll to rotate. For example, the scroll compressor of patent document 1 further includes a non-fixed floating member that rotatably supports the drive shaft while pressing the orbiting scroll against the fixed scroll.
Documents of the prior art
Patent document
Patent document 1: japanese patent laid-open publication No. 2018-35749
However, the drive shaft sometimes tilts during operation of the scroll compressor. In this case, the floating member supporting the drive shaft may be pressed by the drive shaft to be inclined. When the floating member is inclined, a portion where the pressing force is relatively large and a portion where the pressing force is relatively small are generated between the floating member and the orbiting scroll. When such a location is generated, the lubrication state between the floating member and the orbiting scroll may be deteriorated.
SUMMERY OF THE UTILITY MODEL
An object of the utility model is to restrain the floating member and move the lubricated between the vortex dish bad.
The first aspect of the present invention is directed to a scroll compressor 1. The scroll compressor 1 includes: a compression mechanism 20 having a fixed scroll 21 and a movable scroll 26; a drive shaft 40 for driving the orbiting scroll 26 to rotate; and a floating member 50 having a scroll support portion 51 supporting the movable scroll 26, a support portion 53 supporting the drive shaft 40 to be rotatable, and a coupling portion 55 coupling the scroll support portion 51 and the shaft support portion 53. The shortest distance between the end of the outer peripheral surface of the shaft support portion 53 on the movable scroll 26 side and the inner surface of the coupling portion 55 is defined as the 1 st wall thickness t. The 1 st wall thickness t is smaller than the maximum length L in the radial direction of the shaft support portion 53.
In the first aspect, even if the drive shaft 40, which is tilted during the operation of the scroll compressor 1, applies a pressing force to the shaft support portion 53, all of the pressing force is not transmitted to the scroll support portion 51, and therefore the scroll support portion 51 is hardly tilted. This can suppress a poor lubrication between the floating member 50 and the orbiting scroll 26.
A second aspect of the present invention is characterized in that, in the first aspect, the inner surface of the coupling portion 55 has a portion where the radial distance from the drive shaft 40 decreases continuously or stepwise as it goes away from the orbiting scroll 26.
In the second aspect, even if the drive shaft 40 that is tilted during the operation of the scroll compressor 1 exerts a pressing force on the shaft support portion 53, the pressing force is less likely to be transmitted to the scroll support portion 51. Therefore, a lubrication failure between the floating member 50 and the orbiting scroll 26 can be further suppressed.
A third aspect of the present invention is characterized in that, in the first or second aspect, an end portion of the inner peripheral surface of the shaft support portion 53 on the movable scroll 26 side is farther from the movable scroll 26 than an outer surface of the connection portion 55 in the axial direction of the drive shaft 40.
In the third aspect, even if the drive shaft 40 that is tilted during the operation of the scroll compressor 1 exerts a pressing force on the shaft support portion 53, the pressing force is less likely to be transmitted to the scroll support portion 51. Therefore, a lubrication failure between the floating member 50 and the orbiting scroll 26 can be further suppressed.
The fourth aspect of the present invention is directed to a refrigeration apparatus 100. The refrigeration apparatus 100 includes the scroll compressor 1 according to any one of the first to third aspects.
Drawings
Fig. 1 is a refrigerant circuit diagram showing a schematic configuration of a refrigeration apparatus according to embodiment 1.
Fig. 2 is a longitudinal sectional view of the scroll compressor according to embodiment 1.
Fig. 3 is an enlarged sectional view showing a main portion of the scroll compressor of embodiment 1.
Fig. 4 is an enlarged sectional view showing a main part of a scroll compressor according to modification 1 of embodiment 1.
Fig. 5 is an enlarged sectional view showing a main part of a scroll compressor according to modification 2 of embodiment 1.
Fig. 6 is an enlarged cross-sectional view showing a main portion of a scroll compressor according to modification 3 of embodiment 1.
Fig. 7 is an enlarged sectional view showing a main portion of a scroll compressor according to modification 4 of embodiment 1.
Fig. 8 is an enlarged cross-sectional view showing a main portion of a scroll compressor according to modification 5 of embodiment 1.
Fig. 9 is an enlarged sectional view showing a main portion of a scroll compressor of embodiment 2.
Description of the reference symbols
1: a scroll compressor; 20: a compression mechanism; 21: a fixed scroll; 26: a movable scroll; 40: a drive shaft; 50: a floating member; 51: a scroll support; 53: a shaft support portion; 55: a connecting portion; l: the maximum radial length (of the shaft bearing); t: wall thickness 1.
Detailed Description
EXAMPLE 1
As shown in fig. 1, the refrigeration apparatus 100 includes a refrigerant circuit 101 that performs a refrigeration cycle. The refrigerant circuit 101 includes the scroll compressor 1, a radiator 102, an expansion mechanism 103, and an evaporator 104. In the refrigerant circuit 101, the refrigerant compressed in the scroll compressor 1 radiates heat in the radiator 102, and is decompressed in the expansion mechanism 103. The refrigerant whose pressure has been reduced is evaporated in the evaporator 104 and sucked into the scroll compressor 1.
As shown in fig. 2 and 3, the scroll compressor 1 includes a casing 10, a compression mechanism 20, a motor 30, a drive shaft 40, a floating member 50, and a frame 60.
The casing 10 is formed in a longitudinal cylindrical shape with both ends closed. A compression mechanism 20 and a motor 30 are accommodated in the casing 10. The compression mechanism 20 and the motor 30 are coupled by a drive shaft 40 extending in the axial direction (vertical direction) in the casing 10.
A partition member 11 is provided at an upper portion in the casing 10. The partition member 11 partitions the inner space of the cabinet 10 into two spaces. The space above the partition member 11 constitutes a first space S1. The space below the partition member 11 constitutes a second space S2.
The casing 10 is provided with a suction pipe (not shown) and a discharge pipe 12. The suction pipe radially penetrates the main body of the casing 10 and communicates with the second space S2. The suction pipe introduces a low-pressure fluid (for example, a gas refrigerant) into the second space S2. The discharge pipe 12 radially penetrates the upper portion of the casing 10 to communicate with the first space S1. The discharge pipe 12 discharges the high-pressure fluid in the first space S1 to the outside of the casing 10.
The compression mechanism 20 includes a fixed scroll 21 and a movable scroll 26. The fixed scroll 21 is fixed to the frame 60. The orbiting scroll 26 is disposed between the floating member 50 and the fixed scroll 21. The orbiting scroll 26 is configured to mesh with the fixed scroll 21 and perform eccentric orbiting motion with respect to the fixed scroll 21.
The fixed scroll 21 is disposed on one side (upper side in this example) in the axial direction of the frame 60. The fixed scroll 21 has a fixed-side end plate 22, a fixed-side wrap 23, and an outer peripheral wall portion 24.
The stationary-side end plate 22 is formed in a substantially circular plate shape. The fixed wrap 23 is formed in a spiral wall shape that describes an involute curve, and protrudes from a front surface (a lower surface in this example) of the fixed end plate 22. An outer peripheral wall portion 24 is formed so as to surround the outer peripheral side of the stationary wrap 23, and projects from the front surface of the stationary end plate 22. A tip end surface (a lower end surface in this example) of the fixed wrap 23 is substantially coplanar with a tip end surface of the outer circumferential wall portion 24.
A suction port (not shown) is formed in the outer peripheral wall portion 24 of the fixed scroll 21. The suction port communicates with the second space S2. A discharge port 25 penetrating the stationary end plate 22 in the thickness direction is formed in the center portion of the stationary end plate 22 of the stationary scroll 21.
The orbiting scroll 26 has an orbiting side end plate 27, an orbiting side wrap 28, and a boss portion 29.
The movable-side end plate 27 is formed in a substantially circular plate shape. The orbiting wrap 28 is formed in a spiral wall shape that describes an involute curve, and protrudes from a front surface (an upper surface in this example) of the orbiting side end plate 27. The boss portion 29 is formed in a cylindrical shape and is disposed in a central portion of a rear surface (lower surface in this example) of the movable-side end plate 27. The orbiting wrap 28 of the orbiting scroll 26 meshes with the stationary wrap 23 of the stationary scroll 21.
With this structure, a compression chamber S20 is formed between the fixed scroll 21 and the orbiting scroll 26. The compression chamber S20 is a space for compressing the fluid. The compression chamber S20 is configured to compress the fluid sucked through the suction pipe, the second space S2, and the suction port, and discharge the compressed fluid through the discharge port 25.
The motor 30 is accommodated in the casing 10 and disposed below the compression mechanism 20. The motor 30 has a stator 31 and a rotor 32. The stator 31 is formed substantially in a cylindrical shape and is fixed to the housing 10. The rotor 32 is inserted rotatably through the inner periphery of the stator 31. A drive shaft 40 is fixed to the inner periphery of the rotor 32 so as to be inserted therethrough.
The drive shaft 40 has a main shaft portion 41 and an eccentric shaft portion 42. The main shaft portion 41 extends in the axial direction (vertical direction) of the housing 10. The eccentric shaft portion 42 is provided at the upper end of the main shaft portion 41. The outer diameter of the eccentric shaft portion 42 is smaller than the outer diameter of the main shaft portion 41. The axis of the eccentric shaft 42 is eccentric by a predetermined distance from the axis of the main shaft 41.
The floating member 50 is formed substantially in a cylindrical shape. The float member 50 includes a scroll support portion 51, a shaft support portion 53, and a coupling portion 55. In fig. 3 (and fig. 4 to 9), the boundary line between the scroll support portion 51, the shaft support portion 53, and the coupling portion 55 is shown by a broken line.
The scroll support portion 51 is a substantially cylindrical portion that contacts the back surface of the orbiting scroll 26. The scroll support portion 51 supports the orbiting scroll 26. A first annular groove 52 for accommodating an O-ring (not shown) is formed near the lower end of the outer wall of the scroll support portion 51.
The shaft support portion 53 is a substantially cylindrical portion having an inner diameter smaller than that of the scroll support portion 51. The shaft support portion 53 rotatably supports the main shaft portion 41 of the drive shaft 40. A second annular groove 54 for accommodating an O-ring (not shown) is formed near the upper end of the outer wall of the shaft support portion 53.
The coupling portion 55 is a substantially annular portion. The coupling portion 55 couples the lower end portion of the scroll support portion 51 and the upper end portion of the shaft support portion 53 to each other. The inner surface of the coupling portion 55 has a reduced diameter portion 55 a.
The reduced diameter portion 55a is formed on the end portion on the movable scroll 26 side and radially inward of the inner surface of the coupling portion 55. The reduced diameter portion 55a is a portion whose radial distance from the drive shaft 40 decreases continuously or stepwise as it goes away from the orbiting scroll 26 (in this example, as it goes downward). In this example, the diameter-reduced portion 55a includes a first region and a second region in this order from above. The first region is a region where the radial distance from the drive shaft 40 linearly and continuously decreases with the downward direction. The second region is a region that is continuous with the first region and whose radial distance from the drive shaft 40 decreases stepwise in the downward direction.
Here, the shortest distance between the end portion of the outer peripheral surface of the shaft support portion 53 on the orbiting scroll 26 side and the inner surface of the coupling portion 55 is set to the first thickness t. More specifically, the first thickness t is the shortest distance between the end portion of the outer peripheral surface of the shaft support portion 53 on the orbiting scroll 26 side and the inner surface of the reduced diameter portion 55 a. The first wall thickness t is smaller than the maximum length L in the radial direction of the shaft support portion 53.
The frame 60 is formed substantially in a cylindrical shape. The frame 60 is fixed to the casing 10 in the second space S2 by press fitting, for example. The frame 60 has a fixing portion 61 and a protruding portion 62. In addition, the fixing portion 61 is only partially shown in the cross-sections of fig. 2 and 3.
The fixing portion 61 is a substantially cylindrical portion. The outer peripheral surface of the fixing portion 61 is fixed to the housing 10. The fixed scroll 21 is fixed to the upper surface of the fixing portion 61.
The protruding portion 62 is a portion formed substantially in a cylindrical shape or a ring shape. The protruding portion 62 protrudes radially inward from the inner peripheral portion of the fixing portion 61. A third annular groove 63 for accommodating a seal member (not shown) is formed near the inner periphery of the upper surface of the protruding portion 62.
A through hole 64 is formed radially inward of the protruding portion 62. The drive shaft 40 and the shaft support 53 are inserted into the through hole 64.
Effects of embodiment 1
The scroll compressor 1 of the present embodiment includes: a compression mechanism 20 having a fixed scroll 21 and a movable scroll 26; a drive shaft 40 for driving the orbiting scroll 26 to rotate; and a floating member 50 having a scroll support portion 51 for supporting the movable scroll 26, a support portion 53 for rotatably supporting the drive shaft 40, and a coupling portion 55 for coupling the scroll support portion 51 and the shaft support portion 53, wherein a shortest distance between an end portion of an outer peripheral surface of the shaft support portion 53 on the movable scroll 26 side and an inner surface of the coupling portion 55 is a 1 st wall thickness t, and the 1 st wall thickness t is smaller than a maximum length L in a radial direction of the shaft support portion 53. In other words, the coupling portion 55 of the floating member 50 has a thin portion having a first wall thickness t smaller than the maximum length L in the radial direction of the shaft support portion 53. Therefore, even if the drive shaft 40, which is tilted during the operation of the scroll compressor 1, applies a pressing force to the shaft support portion 53, the thin portion is elastically deformed to absorb a part or all of the pressing force. Since the entire pressing force is not transmitted to the scroll support portion 51, the scroll support portion 51 is hardly inclined. This can suppress a poor lubrication between the floating member 50 and the orbiting scroll 26.
Further, in the scroll compressor 1 of the present embodiment, the inner surface of the coupling portion 55 has a portion in which the radial distance from the drive shaft 40 decreases continuously or stepwise with distance from the orbiting scroll 26. In other words, the end portion of the inner peripheral surface of the shaft support portion 53 on the orbiting scroll 26 side is farther from the orbiting scroll 26 than the inner surface of the coupling portion 55 in the axial direction of the drive shaft 40. Therefore, the area of the inner peripheral surface of the shaft support portion 53 facing the scroll support portion 51 in the radial direction via the connection portion 55 is reduced. Therefore, even if the drive shaft 40, which is tilted during the operation of the scroll compressor 1, applies a pressing force to the scroll support portion 53, the pressing force is less likely to be transmitted to the scroll support portion 51. Poor lubrication between the floating member 50 and the orbiting scroll 26 can be further suppressed.
As shown in fig. 4, the radial distance between the reduced diameter portion 55a of the coupling portion 55 and the drive shaft 40 as a whole decreases linearly and continuously with distance from the orbiting scroll 26. Here, the first thickness t is the shortest distance between the end portion of the outer peripheral surface of the shaft support portion 53 on the orbiting scroll 26 side and the inner surface of the reduced diameter portion 55 a. The first wall thickness t is smaller than the maximum length L in the radial direction of the shaft support portion 53.
Effect of modification 1 of embodiment 1
The scroll compressor 1 according to the present modification also provides the same effects as those of the above-described embodiment 1.
As shown in fig. 5, the radial distance between the reduced diameter portion 55a of the coupling portion 55 and the drive shaft 40 as a whole is continuously reduced in a curved shape as it is farther from the orbiting scroll 26. The reduced diameter portion 55a is curved so as to project downward. Here, the first thickness t is the shortest distance between the end portion of the outer peripheral surface of the shaft support portion 53 on the orbiting scroll 26 side and the inner surface of the reduced diameter portion 55 a. The first wall thickness t is smaller than the maximum length L in the radial direction of the shaft support portion 53.
Effect of modification example 2 of embodiment 1
The scroll compressor 1 according to the present modification also provides the same effects as those of the above-described embodiment 1.
Modification 3 of embodiment 1
Modification 3 of embodiment 1 will be described. The scroll compressor 1 of the present modification differs from the above-described embodiment 1 in the structure of the shaft support portion 53 and the coupling portion 55. Hereinafter, differences from embodiment 1 will be mainly described.
As shown in fig. 6, an end portion (in this example, an upper end portion) of the inner peripheral surface of the shaft support portion 53 on the orbiting scroll 26 side is farther from the orbiting scroll 26 than an outer surface (in this example, a lower surface) of the coupling portion 55 in the axial direction of the drive shaft 40.
The radial distance between the reduced diameter portion 55a of the coupling portion 55 and the drive shaft 40 as a whole decreases linearly and continuously with distance from the orbiting scroll 26. Here, the first thickness t is the shortest distance between the end portion of the outer peripheral surface of the shaft support portion 53 on the orbiting scroll 26 side and the inner surface of the reduced diameter portion 55 a. The first wall thickness t is smaller than the maximum length L in the radial direction of the shaft support portion 53.
Effect of modification example 3 of embodiment 1
The scroll compressor 1 according to the present modification also provides the same effects as those of the above-described embodiment 1.
In the scroll compressor 1 according to the present modification, the end portion of the inner peripheral surface of the shaft support portion 53 on the orbiting scroll 26 side is farther from the orbiting scroll 26 than the outer surface of the coupling portion 55 in the axial direction of the drive shaft 40. Therefore, there is substantially no region on the inner peripheral surface of the shaft support portion 53 that faces the scroll support portion 51 in the radial direction through the connection portion 55. Therefore, even if the drive shaft 40, which is tilted during the operation of the scroll compressor 1, applies a pressing force to the scroll support portion 53, the pressing force is less likely to be transmitted to the scroll support portion 51. Poor lubrication between the floating member 50 and the orbiting scroll 26 can be further suppressed.
Modification 4 of embodiment 1
Modification 4 of embodiment 1 will be described. The scroll compressor 1 of the present modification differs from the modification 3 of the above embodiment 1 in the configuration of the coupling portion 55. Next, differences from modification 3 of embodiment 1 will be mainly described.
As shown in fig. 7, the radial distance between the reduced diameter portion 55a of the coupling portion 55 and the drive shaft 40 as a whole is continuously reduced in a curved shape as it is farther from the orbiting scroll 26. The reduced diameter portion 55a is curved so as to project downward. Here, the first thickness t is the shortest distance between the end portion of the outer peripheral surface of the shaft support portion 53 on the orbiting scroll 26 side and the inner surface of the reduced diameter portion 55 a. The first wall thickness t is smaller than the maximum length L in the radial direction of the shaft support portion 53.
Effect of modification example 4 of embodiment 1
The scroll compressor 1 according to the present modification also provides the same effects as those of modification 3 of embodiment 1.
Modification 5 of embodiment 1
Modification 5 of embodiment 1 will be described. The scroll compressor 1 of the present modification differs from the modification 3 of the above embodiment 1 in the configuration of the coupling portion 55. Next, differences from modification 3 of embodiment 1 will be mainly described.
As shown in fig. 8, the reduced diameter portion 55a of the coupling portion 55 includes a first region and a second region in this order from above. The first region is a region where the radial distance from the drive shaft 40 linearly and continuously decreases with the downward direction. The second region is continuous with the first region and linearly extends downward. Here, the first thickness t is the shortest distance between the end portion of the outer peripheral surface of the shaft support portion 53 on the orbiting scroll 26 side and the inner surface of the reduced diameter portion 55 a. The first wall thickness t is smaller than the maximum length L in the radial direction of the shaft support portion 53.
Effect of modification example 5 of embodiment 1
The scroll compressor 1 according to the present modification also provides the same effects as those of modification 3 of embodiment 1.
EXAMPLE 2
As shown in fig. 9, the coupling portion 55 is a substantially disk-shaped portion of the floating member 50. The coupling portion 55 couples the lower end portion of the scroll support portion 51 and the upper end portion of the shaft support portion 53 to each other.
Let a be a minimum thickness (vertical length in this example) in the coupling portion 55, and let w be a radial length of a region having the thickness a. In this case, a: w is 1: 1.5-1: 6 is true.
Here, the shortest distance between the end portion of the outer peripheral surface of the shaft support portion 53 on the orbiting scroll 26 side and the inner surface (upper surface in this example) of the coupling portion 55 is set as the first thickness t. In this example, the first wall thickness t is equal to the thickness a. The first wall thickness t is smaller than the maximum length L in the radial direction of the shaft support portion 53.
Effects of embodiment 2
The scroll compressor 1 according to the present embodiment also provides the same effects as those of the above-described embodiment 1.
In the scroll compressor 1 according to the present embodiment, the minimum thickness of the coupling portion 55 is defined as "a", and the radial length of the region having the thickness "a" is defined as "w, a: w is 1: 1.5-1: 6 is true. Therefore, when the drive shaft 40 inclined during the operation of the scroll compressor 1 applies a pressing force to the shaft support portion 53, the region having the thickness a is easily elastically deformed, and absorbs a part or all of the pressing force. Since the entire pressing force is not transmitted to the scroll support portion 51, the scroll support portion 51 is hardly inclined. This can suppress a poor lubrication between the floating member 50 and the orbiting scroll 26.
While the embodiments and the modifications have been described above, it is to be understood that various changes in form and details may be made therein without departing from the spirit and scope of the appended claims. Further, the above embodiments and modifications may be combined or substituted as appropriate without impairing the functions of the objects of the present invention.
Industrial applicability
As described above, the present invention is useful for a scroll compressor and a refrigeration apparatus having the scroll compressor.
Claims (4)
1. A scroll compressor has:
a compression mechanism (20) having a fixed scroll (21) and a movable scroll (26),
a drive shaft (40) for driving the orbiting scroll (26) in rotation, an
A floating member (50) having a scroll support portion (51) for supporting the movable scroll (26), a support portion (53) for supporting the drive shaft (40) to be rotatable, and a coupling portion (55) for coupling the scroll support portion (51) and the shaft support portion (53),
the scroll compressor is characterized in that,
the shortest distance between the end of the outer peripheral surface of the shaft support part (53) on the movable scroll (26) side and the inner surface of the connection part (55) is set to be the 1 st wall thickness (t),
the 1 st wall thickness (t) is smaller than a maximum length (L) in a radial direction of the shaft support portion (53).
2. The scroll compressor of claim 1,
the inner surface of the coupling portion (55) has a portion in which the radial distance from the drive shaft (40) decreases continuously or stepwise away from the orbiting scroll (26).
3. The scroll compressor of claim 1 or 2,
an end portion of the inner peripheral surface of the shaft support portion (53) on the movable scroll (26) side is farther from the movable scroll (26) than an outer surface of the coupling portion (55) in the axial direction of the drive shaft (40).
4. A refrigeration apparatus, characterized in that it has a scroll compressor (1) according to any one of claims 1 to 3.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2019-033674 | 2019-02-27 | ||
| JP2019033674A JP2020139425A (en) | 2019-02-27 | 2019-02-27 | Scroll compressor |
| JP2019098468A JP2020193576A (en) | 2019-05-27 | 2019-05-27 | Scroll compressor and refrigerator with the same |
| JP2019-098468 | 2019-05-27 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN211737453U true CN211737453U (en) | 2020-10-23 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202020214708.8U Active CN211737453U (en) | 2019-02-27 | 2020-02-26 | Scroll compressor and refrigeration device with same |
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| CN (1) | CN211737453U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114909286A (en) * | 2021-02-08 | 2022-08-16 | 大金工业株式会社 | Scroll compressor having a discharge port |
-
2020
- 2020-02-26 CN CN202020214708.8U patent/CN211737453U/en active Active
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114909286A (en) * | 2021-02-08 | 2022-08-16 | 大金工业株式会社 | Scroll compressor having a discharge port |
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