CN208900360U - Scroll compressor having a plurality of scroll members - Google Patents
Scroll compressor having a plurality of scroll members Download PDFInfo
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- CN208900360U CN208900360U CN201821719557.0U CN201821719557U CN208900360U CN 208900360 U CN208900360 U CN 208900360U CN 201821719557 U CN201821719557 U CN 201821719557U CN 208900360 U CN208900360 U CN 208900360U
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- bushing
- screw compressor
- counterweight
- drive shaft
- mounting portion
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Abstract
The utility model relates to a scroll compressor (10), include: an orbiting scroll (160), the orbiting scroll (160) comprising a shank (163); a drive shaft (130), the drive shaft (130) including an eccentric recess (132, 132a, 132 b); a bushing (400, 400a, 400b), the shank (163) fitted in the eccentric recess (132, 132a, 132b) via the bushing (400, 400a, 400b) such that the orbiting scroll (160) is driven by the drive shaft (130), wherein the scroll compressor (100) further comprises a counterweight (600), the counterweight (600) being mounted on the bushing (400). The utility model provides a can ensure safe and reliable, compact structure, the scroll compressor who makes an uproar falls under high rotational speed operating mode.
Description
Technical field
The utility model relates to a kind of screw compressors.
Background technique
The content of this part provides only background information relevant to the disclosure, may not constitute the prior art.
Screw compressor (especially variable speed scroll compressor), under especially high speed conditions, volution blade contact wall
Between contact force can due to the centrifugal force of dynamic vortex increase and increase.Therefore, it is necessary to counterweight is arranged to offset part and move whirlpool
The centrifugal force of rotation.For example, counterweight can be set with the consistent axial positions of dynamic vortex hub (for example being connected to bushing).So
And in some cases, since the space in the recess portion of main bearing seat is limited, it is difficult to counterweight be made to be arranged so that the centrifugation of counterweight
In the same plane, this causes bushing and/or counterweight to produce moment of flexure to the driving force that the cam pin of power and drive shaft is applied.And
And be arranged in the case where axial positions consistent with dynamic vortex hub in counterweight, it frequently can lead to cam pin and lengthen in turn
The axial dimension of entire compressor is caused to lengthen.
Therefore, it is necessary to one kind can be under especially high speed conditions for example, by reducing vortex contact force and/or reduction
The bending torque of bushing and ensure screw compressor that is safe and reliable and realizing compact-sized, noise reduction etc..
Utility model content
One or more of to achieve the goals above, on one side according to the utility model, provide a kind of vortex
Compressor comprising: dynamic vortex, the dynamic vortex include shank；Drive shaft, the drive shaft include eccentric recess portion；Bushing, institute
It states shank and in the eccentric recess portion dynamic vortex is driven by the drive shaft via bushing cooperation, wherein institute
Stating screw compressor further includes counterweight, and the counterweight is mounted on the bushing.
Advantageously, the bushing can be relative to the drive shaft radial translation, on the side surface of the eccentric recess portion
Be provided with the driving surface of general planar, be provided on the outer surface of the bushing be slidably matched with the driving surface it is big
It causes flat to be driven surface.
Advantageously, the bushing is fixedly attached to the drive shaft.
Advantageously, it is provided with first positioning hole on the outer surface of the bushing, on the side surface of the eccentric recess portion
It is provided with second location hole corresponding with the first positioning hole, and is provided through the first positioning hole and described second
The transverse pin axle of location hole；And/or the first positioning groove is provided on the outer surface of the bushing, in the eccentric recess portion
Side surface on be provided with the second positioning groove corresponding with first positioning groove, and be provided with cooperation be contained in it is described
Perpendicular pin shaft in first positioning groove and second positioning groove.
Advantageously, the shape of the transverse pin axle is cylinder, cuboid or Cone edge platform, the shape of the perpendicular pin shaft be cylinder,
Cuboid or Cone edge platform.
Advantageously, the bushing is bolted to connection to the drive shaft.
Advantageously, side surface interference, transition or the clearance fit of the outer surface of the bushing and the eccentric recess portion.
Advantageously, the driving bearing of tubular is provided between the bushing and the shank, it is described to drive the interior of bearing
Cylindrical surface and the outer surface of the shank are interference fitted, the external cylindrical surface of the driving bearing and the internal surface gaps of the bushing
Cooperation.
Advantageously, the counterweight includes mounting portion and eccentric exacerbation portion, the mounting portion in complete or partial circular ring shape simultaneously
And installation, to the end adjacent with the end plate of the dynamic vortex of the bushing, the bias exacerbation portion is axial from the mounting portion
Ground extends away from the end plate of the dynamic vortex.
Advantageously, the counterweight includes mounting portion and eccentric exacerbation portion, and the mounting portion is in complete or partial circular ring shape, institute
It states eccentric exacerbation portion axially to extend relative to the mounting portion, radially or axially and radially, to adjust
The mass center of the counterweight is saved, so that driving force provided by the centrifugal force of the counterweight and the eccentric recess portion is in same flat
Face.
Advantageously, the counterweight includes the mounting portion in complete or partial circular ring shape and the bias from mounting portion extension
Exacerbation portion, the axial width of the mounting portion are set smaller than the part adjacent with the mounting portion in the eccentric exacerbation portion
Thickness.
The advantages of screw compressor of one or more embodiment according to the present utility model, is for example:
1) it can conveniently adjust the mass center of counterweight, so that the centrifugal force of counterweight and the driving force of drive shaft are in same plane
On, reduce the moment of flexure to bushing, while can reduce the abrasion to driving bearing, improves compressor reliability；2) can shorten
The height of drive shaft, and reduce the height of shell, to reduce the cost of compressor, while making an uproar for compressor can also be reduced
Sound；3) by by drive shaft and bushing by finger setting, the fixed forms such as be bolted and connect, reliably to drive dynamic vortex,
The setting angle for positioning counterweight relative to bushing with also can be convenient simultaneously, to save cost.
Detailed description of the invention
By description referring to the drawings, the feature and advantage of one or several embodiments of the utility model will become
Must be easier to understand, in the accompanying drawings:
Fig. 1 is the longitudinal section view of screw compressor；
Fig. 2 is the centrifugal force of the dynamic vortex of the screw compressor in Fig. 1, the driving force of drive shaft, dynamic vortex and determine vortex
Between contact force, counterweight centrifugal force schematic diagram；
Fig. 3 shows the longitudinal section view of the screw compressor of an embodiment according to the present utility model；
Fig. 4 shows handle mate the putting in the eccentric recess portion of drive shaft of the dynamic vortex of the screw compressor in Fig. 3
Big longitudinal section view, which schematically illustrates the centrifugal force of counterweight, the driving force of drive shaft；
Fig. 5 shows handle mate the putting in the eccentric recess portion of drive shaft of the dynamic vortex of the screw compressor in Fig. 3
Big sectional elevation, which schematically illustrates the centrifugal force of counterweight, the driving force of drive shaft；
Fig. 6 shows the counterweight of the screw compressor in Fig. 3 and the combination stereogram of bushing；
Fig. 7 shows the perspective view of the eccentric recess portion of the drive shaft in Fig. 3；
Fig. 8 shows the perspective view of the dynamic vortex including shank in Fig. 3；
Fig. 9 shows the perspective view of the driving bearing in Fig. 4；
Figure 10 shows bushing and the driving of the screw compressor of the one aspect of embodiment according to the present utility model
The longitudinal section view that axis is fixedly connected；
Figure 11 shows the sectional elevation that the bushing in Figure 10 is fixedly connected with drive shaft；
Figure 12 shows the counterweight of the screw compressor in Figure 10 and the combination stereogram of the bushing with location hole；
Figure 13 shows the perspective view of the eccentric recess portion with cooperation location hole of the drive shaft in Figure 10；
Figure 14 shows the perspective view of the transverse pin axle as fixing component in Figure 10；
Figure 15 shows bushing and the driving of the screw compressor of the another aspect of embodiment according to the present utility model
The longitudinal section view that axis is fixedly connected by erecting pin shaft；And
Figure 16 shows the sectional elevation that the bushing in Figure 15 is fixedly connected with drive shaft.
Specific embodiment
It is only exemplary to the description of embodiment below, and be definitely not to the utility model and its application or usage
Limitation.
The same reference numerals are used to designate identical components in various figures, therefore the construction of same parts will not
Repeat description.
Firstly, describing the screw compressor and its counterweight according to the relevant technologies referring to Figures 1 and 2.
Referring to Fig. 1, screw compressor 10 generally comprise shell 110, the top cover 112 that 110 one end of shell is set, setting exist
The bottom cover 114 of 110 other end of shell and be arranged between top cover 112 and shell 110 with by the inner space of compressor separate
At the partition 116 of high-pressure side and low-pressure side.Constitute high-pressure side between partition 116 and top cover 112, and partition 116,110 and of shell
Low-pressure side is constituted between bottom cover 114.Low-pressure side is provided with the inlet suction port 118 for sucking fluid, is provided in high-pressure side
For the exhaust joint 119 of compressed fluid to be discharged.The motor being made of stator 122 and rotor 124 is provided in shell 110
120.Drive shaft 30 is provided in rotor 124 to drive the compression mechanism being made of determine vortex 150 and dynamic vortex 160.Dynamic vortex
160 include end plate 164, the hub 162 for being formed in end plate side and the spiral helicine blade 166 for being formed in the end plate other side.It is fixed
Vortex 150 includes end plate 154, is formed in the spiral helicine blade 156 of end plate side and is formed in the substantial middle position of end plate
The exhaust outlet 152 at place.It is formed between the helical blade 156 of determine vortex 150 and the helical blade 166 of dynamic vortex 160 a series of
The compression chamber that volume is gradually reduced from radial outside to radially inner side.
A part of drive shaft 30 is supported by the base bearing 144 being arranged in main bearing seat 20.One end shape of drive shaft 30
At there is eccentric crank pin 32.Eccentric crank pin 32 cooperates in the hub 162 of dynamic vortex 160 via bushing 200 to drive dynamic whirlpool
Rotation 160.
The base bearing cover board 50 as thrust plate is provided on main bearing seat 20.Base bearing cover board 50 can be filled by fixed
It sets and is fixed on main bearing seat 20.Space is formed between main bearing seat 20 and base bearing cover board 50.The side of dynamic vortex 160 by
Base bearing cover board 50 supports.By the driving of motor 120, dynamic vortex 160 will be relative to 150 translation rotation of determine vortex (that is, dynamic whirlpool
The central axis of rotation 160 is turned round around the central axis of determine vortex 150, but dynamic vortex 160 itself will not be around itself central axis
Line rotation) to realize the compression of fluid.It is sliding that above-mentioned translation rotation passes through the cross being arranged between determine vortex 150 and dynamic vortex 160
Ring 190 is realized.High-pressure side is discharged to by exhaust outlet 152 by determine vortex 150 and the compressed fluid of dynamic vortex 160.For
It prevents on high-tension side fluid from flowing back under specific circumstances via exhaust outlet 152, at the central aperture of partition 116 is provided with list
To valve or exhaust valve 170.
During operation, referring to fig. 2, by the driving of motor 120, dynamic vortex 160 will be translatable relative to determine vortex 150
(that is, the central axis of dynamic vortex 160 is turned round around the central axis of determine vortex 150, but dynamic vortex 160 itself will not be around for rotation
The central axis rotation of itself), so that dynamic vortex 160 will generate centrifugal force F3, due to dynamic vortex 160 during operation from
Mental and physical efforts F3And/or the gas force of compression mechanism, therefore in the side surface of the helical blade of determine vortex 150 156 and dynamic vortex 160
Contact force F is generated between the side surface of helical blade 1664.It is pointed out here that the mark in the direction of the power in Fig. 2 is only
It is exemplary.
However, screw compressor, especially frequency-changing cyclone compressor, can be according to environment temperature and demand for example changes compression
Machine revolving speed is to realize that operating condition changes.With the raising of revolving speed, the centrifugal force of dynamic vortex becomes larger, and dynamic vortex and determine vortex are indirectly
Touch can also become larger, and may be damaged failure when being more than volution blade contact wall maximum intensity, cause unexpected prominent
Hair-like condition.
In order to reduce determine vortex 150 helical blade 156 side surface and dynamic vortex 160 helical blade 166 side table
Contact force between face, screw compressor 10 can be further provided with counterweight 300.Counterweight 300 is constructed to be permeable to drive shaft
30 rotation and counterweight 300 as rotation and caused by centrifugal force F1It can for example act in the hub 162 of dynamic vortex 160.
For example, the drive shaft 30 of screw compressor drives the dynamic vortex 160 of screw compressor, counterweight packet via bushing 200
Circular through hole 301 is included, bushing 200 includes the cylindrical portion 201 cooperated with circular through hole 301, wherein counterweight 300 is with circular through hole
The mode of 301 inner peripheral surface and the outer peripheral surface elastic conjunction of cylindrical portion 201 is installed to bushing 200.The centrifugal force F1's of counterweight 300
Direction can be set into substantially opposite with the direction of the centrifugal force F3 of dynamic vortex 160.Therefore, counterweight can effectively cancel out dynamic whirlpool
160 centrifugal force is revolved to reduce contact force F4.
However in the above-mentioned exemplary screw compressor with counterweight, counterweight centrifugal force F as caused by rotation1With
The driving force F that drive shaft 130 provides2Not in one plane, which produces along as shown in Figure 2 clockwise curved
Square, so that bushing generates certain bending torque.The construction of the counterweight in above-mentioned screw compressor is so that drive shaft is (special simultaneously
Not, eccentric crank pin) it lengthens, this causes the shell of compressor to lengthen, increases cost and increase noise.
The basic structure of the screw compressor 100 of embodiment according to the present utility model is described below with reference to Fig. 3 to Fig. 9
It makes and principle.
As shown in figure 3, generally comprising shell 110 according to the screw compressor 100 of the utility model embodiment, setting exists
The top cover 112 of 110 one end of shell, the bottom cover 114 that 110 other end of shell is set and setting top cover 112 and shell 110 it
Between the inner space of compressor to be separated into the partition 116 of high-pressure side and low-pressure side.It is constituted between partition 116 and top cover 112
High-pressure side, and low-pressure side is constituted between partition 116, shell 110 and bottom cover 114.It is provided in low-pressure side for sucking fluid
Inlet suction port 118 is provided with the exhaust joint 119 for compressed fluid to be discharged in high-pressure side.Be provided in shell 110 by
The motor 120 that stator 122 and rotor 124 are constituted.Drive shaft 130 is provided in rotor 124 to drive by determine vortex 150 and dynamic whirlpool
The compression mechanism that rotation 160 is constituted.Dynamic vortex 160 includes end plate 164, is formed in the shank 163 of end plate side and is formed in end plate
The spiral helicine blade 166 of the other side.Determine vortex 150 includes end plate 154, the spiral helicine blade 156 for being formed in end plate side
With the exhaust outlet 152 being formed at the substantial middle position of end plate.In the helical blade 156 and dynamic vortex 160 of determine vortex 150
A series of compression chamber that volumes are gradually reduced from radial outside to radially inner side is formed between helical blade 166.
The base bearing cover board 50 as thrust plate is provided on main bearing seat 20.Base bearing cover board 50 can be filled by fixed
It sets and is fixed on main bearing seat 20.Space is formed between main bearing seat 20 and base bearing cover board 50.The side of dynamic vortex 160 by
Base bearing cover board 50 supports.By the driving of motor 120, dynamic vortex 160 will be relative to 150 translation rotation of determine vortex (that is, dynamic whirlpool
The central axis of rotation 160 is turned round around the central axis of determine vortex 150, but dynamic vortex 160 itself will not be around itself central axis
Line rotation) to realize the compression of fluid.It is sliding that above-mentioned translation rotation passes through the cross being arranged between determine vortex 150 and dynamic vortex 160
Ring 190 is realized.High-pressure side is discharged to by exhaust outlet 152 by determine vortex 150 and the compressed fluid of dynamic vortex 160.For
It prevents on high-tension side fluid from flowing back under specific circumstances via exhaust outlet 152, at the central aperture of partition 116 is provided with list
To valve or exhaust valve 170.
A part of drive shaft 130 is supported by the base bearing 144 being arranged in main bearing seat 20.One end of drive shaft 130
It is formed with eccentric recess portion 132.Shank 163 makes 160 driven shaft of dynamic vortex via the cooperation of bushing 400 in eccentric recess portion 132
130 drivings, screw compressor 100 include counterweight 600, and counterweight 600 is mounted on bushing 400 and can rotate with drive shaft 130
And counterweight 300 generates centrifugal force due to rotation to balance the centrifugal force of dynamic vortex 160, to reduce the spiral of determine vortex 150
Contact force between the side surface of the helical blade 166 of the side surface and dynamic vortex 160 of blade 156.
As shown in figure 4, since the handle mate of dynamic vortex is contained in the eccentric recess portion of drive shaft to drive dynamic vortex simultaneously
And counterweight is mounted on bushing, compared with the relevant technologies, it can make at the centrifugal force F1 of the counterweight and driving force F2 of drive shaft
In the same plane, reduce to the moment of flexure of bushing, at the same can reduce to driving bearing (be generally arranged at bushing and shank it
Between) abrasion, improve compressor reliability.Meanwhile by means of the construction, can shortening drive shaft, (especially drive shaft is upper
End) height, and reduce the height of shell, to reduce the cost of compressor, while making an uproar for compressor can also be reduced
Sound.
Specifically, referring to fig. 4 and Fig. 6, counterweight 600 may include mounting portion 601 and eccentric exacerbation portion 602, mounting portion 601
It in complete or partial circular ring shape and installs to the end adjacent with the end plate 164 of dynamic vortex 160 of bushing 400, bias aggravates
Portion 602 axially extends away from the end plate of dynamic vortex 160 from mounting portion 601.
Advantageously, eccentric exacerbation portion 602 can axially extend relative to mounting portion 601, is radially or axial
Ground and radially, to adjust the mass center of counterweight 600, so that being driven provided by the centrifugal force of counterweight 600 and eccentric recess portion 132
Power is in same plane.Wherein, more advantageously, the axial width of mounting portion 601 can be set to be less than eccentric exacerbation portion 602
The part adjacent with mounting portion 601 thickness, which can further reduce matching on the axial direction of drive shaft
Size is re-mounted, and thus reduces the height of shell, to reduce the cost of compressor.
Referring to Fig. 5 to Fig. 7, bushing 400 can be can be relative to the unloading bushing of 130 radial translation of drive shaft, inclined
It is provided with the driving surface 1331 of general planar on the side surface of heart recess portion 132, is provided on the outer surface of unloading bushing 400
The general planar being slidably matched with driving surface 1331 is driven surface 4001.By means of the driving table for unloading bushing and recess portion
This of face is slidably matched, and provides radial compliance for the dynamic vortex of compressor.
Advantageously, it is provided with the driving bearing 500 (referring to fig. 4 and Fig. 9) of tubular between bushing 400 and shank 163, drives
The inner cylinder face of dynamic bearing 500 and the outer surface of shank 163 are interference fitted, and drive the external cylindrical surface of bearing 500 and bushing 400
Internal surface gaps cooperation.By the way that driving bearing is arranged further in this manner, be capable of providing reliable bearing, reduce friction to
Ensure reliable driving force transmitting.
The otherwise scroll compression of embodiment according to the present utility model is described below with reference to Figure 10 to Figure 16
Machine, wherein bushing 400a, 400b are fixedly attached to drive shaft, with the aspect of above embodiment the difference is that: bushing
It is not the mode for being capable of providing the unloading bushing of radial compliance, but be fixedly connected with drive shaft by using bushing, thus
Facilitate the setting angle for being accurately positioned counterweight and bushing relative to drive shaft, to save cost.
Specifically, referring to Figure 10 to Figure 14, first positioning hole can be set on the outer surface of bushing 400a, in bias
Second location hole corresponding with first positioning hole can be set on the side surface of recess portion 132a, and it is fixed to be provided through first
The transverse pin axle 700 in position hole and second location hole, is fixed to drive shaft for bushing.The shape of transverse pin axle 700 can be cylinder, length
Cube or Cone edge platform.In this way, can according to need the perpendicular pin shaft of selection suitable shape, it is suitable fixed to provide.
And the first positioning or alternatively, can be set on the outer surface of bushing 400b referring to Figure 15 to Figure 16
The second positioning groove corresponding with the first positioning groove has can be set in groove on the side surface of eccentric recess portion 132b, and
It is provided with the perpendicular pin shaft 800 that cooperation is contained in the first positioning groove and the second positioning groove.The shape of perpendicular pin shaft 800 can be
Cylinder, cuboid or Cone edge platform.In this way, can according to need the perpendicular pin shaft of selection suitable shape, it is suitable fixed to provide.
In addition, above-mentioned bushing 400a, 400b can also be bolted to connection to drive shaft 130.Advantageously, above-mentioned lining
400a is covered, the outer surface of 400b can be with eccentric recess portion 132a, side surface interference, transition or the clearance fit of 132b.In this way, can
To select appropriate fit system as needed, for example, select interference fit in the case where, may further ensure that bushing and partially
Heart recess portion is fixedly connected.
It will be appreciated by those skilled in the art that being related to drive shaft described in embodiment of the Fig. 3 into Fig. 9
Holding construction, the shape design of counterweight (mounting portion and eccentric exacerbation portion) and seperated construction of counterweight etc. also can be applied to Figure 10
In embodiment into Figure 16.
Although the various embodiments of the utility model have been described in detail herein, it should be appreciated that the utility model is not
It is confined to the specific embodiment be described in detail and shown here, without departing from the spirit and scope of the utility model
It may be effected by one skilled in the art other modifications and variant.All these modifications and variant both fall within the utility model
In range.Moreover, all components described herein can be replaced by component equivalent in other technologies.
Claims (11)
1. a kind of screw compressor, characterized by comprising:
Dynamic vortex, the dynamic vortex include shank；
Drive shaft, the drive shaft include eccentric recess portion；
Bushing, the shank cooperates via the bushing drives the dynamic vortex by the drive shaft in the eccentric recess portion
It is dynamic,
Wherein, the screw compressor further includes counterweight, and the counterweight is mounted on the bushing.
2. screw compressor as described in claim 1, wherein the bushing can relative to the drive shaft radial translation,
The driving surface of general planar is provided on the side surface of the eccentric recess portion, be provided on the outer surface of the bushing with
The general planar that the driving surface is slidably matched is driven surface.
3. screw compressor as described in claim 1, wherein the bushing is fixedly attached to the drive shaft.
4. screw compressor as claimed in claim 3, in which:
Be provided with first positioning hole on the outer surface of the bushing, be provided on the side surface of the eccentric recess portion with it is described
The corresponding second location hole of first positioning hole, and it is provided through the lateral pin of the first positioning hole and the second location hole
Axis；And/or
It is provided with the first positioning groove on the outer surface of the bushing, is provided on the side surface of the eccentric recess portion and institute
Corresponding second positioning groove of the first positioning groove is stated, and is provided with cooperation and is contained in first positioning groove and described
Perpendicular pin shaft in two positioning grooves.
5. screw compressor as claimed in claim 4, wherein the shape of the transverse pin axle be cylinder, cuboid or Cone edge platform,
The shape of the perpendicular pin shaft is cylinder, cuboid or Cone edge platform.
6. screw compressor as claimed in claim 3, wherein the bushing is bolted to connection to the drive shaft.
7. the screw compressor as described in any one of claim 4 to 6, wherein the outer surface of the bushing and it is described partially
Side surface interference, transition or the clearance fit of heart recess portion.
8. screw compressor according to any one of claims 1 to 6, wherein between the bushing and the shank
It is provided with the driving bearing of tubular, the inner cylinder face of the driving bearing and the outer surface of the shank are interference fitted, the drive
The internal surface gaps of the external cylindrical surface of dynamic bearing and the bushing cooperate.
9. screw compressor according to any one of claims 1 to 6, wherein the counterweight includes mounting portion and bias
Exacerbation portion, the mounting portion is in complete or partial circular ring shape and installs adjacent with the end plate of the dynamic vortex to the bushing
End, it is described bias exacerbation portion from the mounting portion axially deviate from the dynamic vortex end plate extend.
10. screw compressor according to any one of claims 1 to 6, wherein the counterweight includes mounting portion and bias
Exacerbation portion, the mounting portion be in complete or partial circular ring shape, it is described bias exacerbation portion axially extend relative to the mounting portion,
Radially or axially and radially, to adjust the mass center of the counterweight so that the centrifugal force of the counterweight with
Driving force provided by the bias recess portion is in same plane.
11. screw compressor according to any one of claims 1 to 6, wherein the counterweight includes in complete or partial
The mounting portion of circular ring shape and from the eccentric exacerbation portion that the mounting portion extends, the axial width of the mounting portion is set smaller than institute
State the thickness of the part adjacent with the mounting portion in eccentric exacerbation portion.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201821719557.0U CN208900360U (en) | 2018-10-23 | 2018-10-23 | Scroll compressor having a plurality of scroll members |
| PCT/CN2019/112760 WO2020083313A1 (en) | 2018-10-23 | 2019-10-23 | Scroll compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201821719557.0U CN208900360U (en) | 2018-10-23 | 2018-10-23 | Scroll compressor having a plurality of scroll members |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN208900360U true CN208900360U (en) | 2019-05-24 |
Family
ID=66576585
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201821719557.0U Active CN208900360U (en) | 2018-10-23 | 2018-10-23 | Scroll compressor having a plurality of scroll members |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN208900360U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2020083313A1 (en) * | 2018-10-23 | 2020-04-30 | 艾默生环境优化技术(苏州)有限公司 | Scroll compressor |
| CN111089055A (en) * | 2018-10-23 | 2020-05-01 | 艾默生环境优化技术(苏州)有限公司 | Scroll compressor having a plurality of scroll members |
| WO2021147337A1 (en) * | 2020-01-21 | 2021-07-29 | 艾默生环境优化技术(苏州)有限公司 | Scroll compressor |
-
2018
- 2018-10-23 CN CN201821719557.0U patent/CN208900360U/en active Active
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2020083313A1 (en) * | 2018-10-23 | 2020-04-30 | 艾默生环境优化技术(苏州)有限公司 | Scroll compressor |
| CN111089055A (en) * | 2018-10-23 | 2020-05-01 | 艾默生环境优化技术(苏州)有限公司 | Scroll compressor having a plurality of scroll members |
| WO2021147337A1 (en) * | 2020-01-21 | 2021-07-29 | 艾默生环境优化技术(苏州)有限公司 | Scroll compressor |
| US11867182B2 (en) | 2020-01-21 | 2024-01-09 | Copeland Climate Technologies (Suzhou) Co. Ltd. | Scroll compressor |
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