CN208900359U - A counter weight subassembly and scroll compressor for scroll compressor - Google Patents
A counter weight subassembly and scroll compressor for scroll compressor Download PDFInfo
- Publication number
- CN208900359U CN208900359U CN201821719127.9U CN201821719127U CN208900359U CN 208900359 U CN208900359 U CN 208900359U CN 201821719127 U CN201821719127 U CN 201821719127U CN 208900359 U CN208900359 U CN 208900359U
- Authority
- CN
- China
- Prior art keywords
- balance weight
- weight assembly
- counterweight
- bushing
- outer peripheral
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Landscapes
- Rotary Pumps (AREA)
Abstract
The utility model relates to a counter weight subassembly and scroll compressor. In one aspect, a counterweight assembly for a scroll compressor is provided, the counterweight assembly comprising a bushing (200) and a counterweight (100, 400) mounted on the bushing, a drive shaft (30) of the scroll compressor driving an orbiting scroll (160) of the scroll compressor via the bushing, the counterweight (100, 400) comprising a counterweight (300, 500), the counterweight (300, 500) comprising a leading end (310, 510) and a trailing end (320, 520) with respect to a direction of Rotation (RD) of the counterweight assembly, the counterweight (300, 500) being configured such that a radial distance from an outer periphery of the counterweight (300, 500) to a center (O1) of the counterweight assembly varies from the leading end to the trailing end. According to the utility model discloses an above-mentioned structure for can change the shape and the barycenter position of counter weight in a flexible way, distribute, reduce gaseous power consumption and/or improve oil circulation with the adaptation gas power.
Description
Technical field
The utility model relates to balance weight assembly and including the screw compressor of the balance weight assembly, more particularly, to can
Improved balance weight assembly is made in power power consumption.
Background technique
The content of this part provides only background information relevant to the disclosure, may not constitute the prior art.
It is including that (such as compressor is special for the rotary machine of moving component (such as compression mechanism, motor, rotary shaft etc.)
It is screw compressor) in, vibration will increase due to the movement of moving component (such as rotation) imbalance in machine operation, make an uproar
Sound etc..In some cases, the movement imbalance of moving component is the component installed by moving component itself and/or thereon
Mismachining tolerance and caused by causing mass center uneven.In other situations, the movement imbalance of moving component is due to spy
Caused by eccentric structure is set to realize specific function in the component that meaning ground is installed in moving component itself and/or thereon
(for example, cam pin is arranged at drive shaft to make dynamic vortex relative to determine vortex using eccentric center principle in screw compressor
Carry out circular translational).
Uneven for this movement, setting is capable of providing the counterweight of reversed centrifugal force to balance usually on moving component
Generated movement is uneven to reduce vibration and noise.
Counterweight is moved with the movement of moving component.The environment locating for such as moving component high speed rotation, counterweight is deposited
There are in the application scenarios of liquid flow (such as oil stream), the presence of counterweight will lead to the environment locating for gas stream, and/or counterweight
The resistance of motion of moving component increases so as to cause the increase of system dynamic power consumption.In addition, if counterweight due to shape etc. and
Cause intensity insufficient, then the counterweight in high-speed motion is readily able to that fracture (such as fatigue fracture) occurs.
For in the counterweight of compressor disclosed in the prior art (WO2017199435A1), for each portion of counterweight
Radius, center location and the height of the respective circular arc outer peripheral surface divided are designed and are adjusted with improving the height of corresponding counterweight part
The height of counterweight mass center, to reduce the bending torque of counterweight.However, counterweight is to carry out eccentric rotary motion around the centre of gyration
, particularly, there are radial compliance compensation using unloading bushing, thus the movement carried out be not about counterweight with
The rotary motion of the centre of gyration of bushing.Since outer peripheral surface of the prior art to counterweight is confined to the equal circular arc of radius size
Face, but the motion profile of circular arc is the noncircular locus relative to the centre of gyration, therefore generates biggish gas force power consumption.
Moreover, in the prior art, counterweight part makes counterbalance design single and has a single function due to being confined to arc surface.This
Outside, the prior art also lacks the design for promoting oil circulation aspect.
Utility model content
One purpose of one or more embodiments of the utility model is to provide one kind and does in terms of power
Improved balance weight assembly out, to overcome or alleviated by least one of drawbacks described above.
To achieve the goals above, one aspect according to the present utility model provides a kind of for screw compressor
Balance weight assembly, the balance weight assembly include bushing and the counterweight that is mounted on the bushing, the drive shaft of the screw compressor
The dynamic vortex of the screw compressor is driven via the bushing, the counterweight includes counterweight part, the counterweight part include about
The front end of the direction of rotation of the balance weight assembly and tail end, the counterweight part are configured so that the outer peripheral edge of the counterweight part
It is to change to the radial distance at the center of the balance weight assembly from the front end to the tail end.
Preferably, the outer peripheral edge of the counterweight part is in generally arcuate.
Preferably, the radius of curvature of the outer peripheral edge changes with changing from small to big from the front end to the tail end.
Preferably, the radius of curvature of the outer peripheral edge is changed from small to big from the front end to the tail end and is become with becoming smaller again
Change.
Preferably, the variation turning point of the radius of curvature is located at the middle position of the outer peripheral edge.
Preferably, the outer peripheral edge of the counterweight part is in polygonal shape.
Preferably, the outer peripheral edge is in equilateral polygon shape.
Preferably, the outer peripheral edge is in inequilateral polygonal shape.
Preferably, the exterior angle of the inequilateral polygon of the outer peripheral edge is changed from small to big from the front end to the tail end
Ground variation.
Preferably, the front end includes preceding axial end surface and preceding circumferential ends, and the preceding axial end surface is towards institute
It states preceding circumferential ends axially and circumferentially tilts.
Preferably, when radially observing, it is 25 degree to 60 degree that the front end, which is formed by front end angle,.
Preferably, the tail end includes tail axial end surface and tail circumferential ends, and the tail axial end surface is towards institute
It states tail circumferential ends axially and circumferentially tilts.
Preferably, the front end is streamlined.
Preferably, the bushing is the unloading bushing for allowing the dynamic vortex to have radial compliance.
Other side according to the present utility model, provides a kind of screw compressor, and the screw compressor includes as above
The balance weight assembly stated.
Preferably, the dynamic vortex includes hub, and the drive shaft of the screw compressor includes eccentric crank pin, institute
Eccentric crank pin is stated to cooperate in the hub via the bushing to drive the dynamic vortex；Or the dynamic vortex includes handle
Portion, and the drive shaft includes eccentric recess portion, and the shank cooperates via the bushing and makes institute in the eccentric recess portion
Dynamic vortex is stated to be driven by the drive shaft.
The advantages of balance weight assembly and screw compressor of one or more embodiment according to the present utility model, for example exists
In: counterweight part with counterweight (disk) in circular arc (in the counterweight part, outer peripheral edge to its center, that is, rotation center it is radial away from
It is equal from i.e. radius, so that the centroid position of the counterweight and then radius of gyration is relatively fixed and lack variation, inclined therefore, it is difficult to adapt to
Non-circular motion profile caused by the heart rotates and lead to the increase of gas force power consumption) compare, by making counterweight and (unloading) bushing
Cooperation center (i.e. rotation center) to counterweight part periphery (outer periphery) radial distance (radius) be variation, allow to
Change the shape and centroid position of counterweight, neatly to adapt to gas force distribution, reduce gas force power consumption.Also, according to this reality
Oil is conveniently stirred with the outer peripheral edge shape design of novel balance weight assembly, so as to improve oil circulation, and for example, by using polygon
The installation of counterweight and (unloading) bushing can be facilitated to position in the case where periphery.
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
It obtains easier to understand, in which:
Fig. 1 is the sectional side elevation for showing the screw compressor for applying balance weight assembly according to the present utility model；
Fig. 2 is the amplification sectional side elevation for showing the balance weight assembly of Fig. 1；
Fig. 3 is the perspective view for showing the balance weight assembly of Fig. 1；
Fig. 4 is the top view for showing the balance weight assembly of one aspect of first embodiment according to the present utility model；
Fig. 5 is the top view for showing the balance weight assembly of other side of first embodiment according to the present utility model；
Fig. 6 is the perspective view for showing the counterweight of balance weight assembly according to the present utility model；
Fig. 7 is the top view for showing the counterweight of Fig. 6；
Fig. 8 is the side view for showing the counterweight of Fig. 6；
Fig. 9 is the side view for showing the counterweight of balance weight assembly of other side according to the present utility model；
Figure 10 is the top view for showing the counterweight of one aspect of second embodiment according to the present utility model；
Figure 11 is the top view for showing the counterweight of other side of second embodiment according to the present utility model；
Figure 12 is the partial longitudinal section for showing another screw compressor for applying balance weight assembly according to the present utility model.
Specific embodiment
Description related to the preferred embodiment is only exemplary below, and be definitely not to the utility model and its application or
The limitation of usage.
The same reference numerals are used to designate identical components in various figures, therefore the construction of same parts will not
Repeat description.
The balance weight assembly of first embodiment according to the present utility model is applied below with reference to Fig. 1 to Fig. 9 description
The essential structure and principle of screw compressor 10.
As described in Figure 1, shell 110 is generally comprised according to the screw compressor 10 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 30 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 hub 162 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.
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.
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 rotated 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 into low-pressure side via exhaust outlet 152 under specific circumstances, at exhaust outlet 152 is provided with list
To valve or exhaust valve 170.
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, referring to fig. 2 to Fig. 3, screw compressor 10 is further provided with balance weight assembly according to the present utility model,
The balance weight assembly includes bushing 200 and the counterweight 100 that is mounted on bushing 200, and the drive shaft 30 of screw compressor is via bushing
The dynamic vortex 160 of 200 driving screw compressors.In conjunction with Fig. 4 to Fig. 5, counterweight 100 includes counterweight part 300, and counterweight part 300 includes
The front end 310 of direction of rotation RD about balance weight assembly and tail end 320, wherein the outer peripheral edge of counterweight part 300 is in substantially arc
Shape, and counterweight part 300 is configured so that the radius of curvature ρ of the outer peripheral edge of counterweight part 300 from front end 310 to tail end 320
Change (as shown in figure 4, outer peripheral edge changes relative to circular arc shown in dotted line) with changing from small to big, to adapt to balance weight assembly along rotation
Gas force distribution when direction RD rotates, to reduce gas force power consumption, there is movement stream in the environment especially locating for counterweight
Such as bushing of moving component attached by body stream and/or counterweight needs to carry out such as 3600 revs/min or more of high-speed motion of compression
In the variable speed compressor of machine such as high-speed motion, by moving component, that is, entire rotational structure institute attached by counterweight and then counterweight
The resistance of motion (fluid resistance) that is subject to reduces, therefore rotational structure and then the power power consumption of compressor are reduced.Meanwhile it should
Construction so that the mass center M of the counterweight at a distance from the centre of gyration O2 of the balance weight assembly (that is, radius of gyration r) is adjustable
, that is, radius of gyration r is determined by the configuration design of counterweight, can be by changing counterweight (particularly, the periphery of counterweight part
Edge) radius of curvature adjust the position of mass center M, can also to reduce influence of the different compressor designs to Assembling Production
To meet mechanical requirements when the different operating conditions of compressor, different materials, balance requires and structural requirement etc..
Advantageously, as shown in figure 5, the radius of curvature ρ of the outer peripheral edge of counterweight part can also be from front end to tail end by small
Become larger and change with becoming smaller again, not only reduce the pressure at the front end (windward side) of counterweight but also makes at the tail end of counterweight
Wake flow (turbulent flow) caused by resistance reduce, also that is, hindering counterweight suffered pressure drag and then head-on during exercise
Power (because fluid there are due to cause) reduce, be further reduced gas force power consumption.Further, the curvature of the outer peripheral edge of counterweight part
The variation turning point of radius ρ can be located at the middle position of outer peripheral edge, reduce resistance with further improvement.
One aspect according to the present embodiment, referring to Fig. 6 to Fig. 8, the front end 310 of counterweight part includes preceding axial end table
Face 311 and preceding circumferential ends 312, the preceding axial end surface 311 tilt axially and circumferentially towards preceding circumferential ends 312.It borrows
The oblique structure of axial end surface before helping can reduce air resistance to reduce and increase gas force power consumption, and provide and work as
The effect that balance weight assembly is bought oil upwards in the axial direction when rotating, so as to improve oil circulation.
Further, referring to Fig. 8, when radially observing, front end is formed by front end angle γ can be big
In 0 degree less than 90 degree, particularly, which is 25 degree to 60 degree, and more particularly, which is 25 degree
To 40 degree.
In addition, the tail end 320 of counterweight part also may include tail axial end surface 321 and tail circumferential ends 322, tailing axle to
End surfaces 321 tilt axially and circumferentially towards tail circumferential ends 322, so that the wake flow reduced at the tail end of counterweight is drawn
The resistance risen.
Advantageously, referring to Fig. 9, the front end 310 of counterweight part is streamlined, (is met with further decreasing fluid in front end
Wind face) at resistance, wherein the preceding axial end surface 311 of front end 310 be streamlined curved surface.
In addition, above-mentioned bushing can have the unloading bushing of radial compliance for permission dynamic vortex.
Figure 10 and Figure 11 is the top view for showing the balance weight assembly of another embodiment according to the present utility model, wherein
Referring to Figure 10, the outer peripheral edge of the counterweight part 500 of the counterweight 400 of balance weight assembly can be in equilateral polygon shape.Particularly, referring to
Figure 11, the outer peripheral edge of counterweight part 500 can also be in inequilateral polygonal shape, and the exterior angle of the inequilateral polygon of outer peripheral edge
A1, A2, A3 (schematically show only 3 exterior angles, the number at exterior angle is polygon according to the inequilateral of the outer peripheral edge of counterweight part in figure
Shape determines) change with changing from small to big from front end 510 to tail end 520.That is, by means of above-mentioned construction, with aforementioned reality
Apply that mode is similar, the diameter of the center O1 (rotation center corresponding to counterweight) of the outer peripheral edge of the counterweight part to the balance weight assembly
It is to change to distance (radius) from front end to tail end, so that the revolution of the mass center of the counterweight and the balance weight assembly
The distance at center changes therewith, to adapt to gas force distribution of the balance weight assembly along direction of rotation RD rotation when, to reduce gas
Power power consumption.Particularly, since the counterweight part of counterweight is in polygon, so that facilitating stirring oil to improve oily circulation, and and counterweight
Arc-shaped circumference edge compare, may be implemented accurate setting angle of the counterweight with respect to bushing, particularly, using unloading bushing
In the case of, with the corresponding edge of polygon and the angle that unloads between the driving surface of bushing realizes the accurate of the opposite bushing of counterweight
Setting angle.
It should be pointed out that the inclination of the preceding axial end surface of the front end about counterweight part in the first embodiment
The features such as construction, front end angle, fairshaped front end cage structure and unloading bushing are suitable for the second of the utility model
Embodiment.
It is practical new according to this referring to Figure 12 other than screw compressor 10 according to the present utility model as shown in Figure 1
The balance weight assembly of type applies also for another screw compressor as shown in figure 12.It is different from screw compressor as shown in Figure 1
Place be that in screw compressor as shown in figure 12, dynamic vortex 160 includes shank 163, and the drive of screw compressor
Moving axis 30 includes eccentric recess portion 132, and shank 163 cooperates via bushing 200 drives 160 driven shaft 30 of dynamic vortex in recess portion
It is dynamic
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 (16)
1. a kind of balance weight assembly for screw compressor, which is characterized in that the balance weight assembly includes bushing and is mounted on institute
The counterweight on bushing is stated, the drive shaft of the screw compressor drives the dynamic vortex of the screw compressor via the bushing,
The counterweight includes counterweight part, and the counterweight part includes front end and the tail end of the direction of rotation about the balance weight assembly,
The counterweight part is configured so that the radial distance at outer peripheral edge to the center of the balance weight assembly of the counterweight part before described
End to the tail end is variation.
2. balance weight assembly as described in claim 1, wherein the outer peripheral edge of the counterweight part is in generally arcuate.
3. balance weight assembly as claimed in claim 2, wherein the radius of curvature of the outer peripheral edge is from the front end to the tail
End changes with changing from small to big.
4. balance weight assembly as claimed in claim 2, wherein the radius of curvature of the outer peripheral edge is from the front end to the tail
End is changed from small to big to be changed with becoming smaller again.
5. balance weight assembly as claimed in claim 4, wherein the variation turning point of the radius of curvature is located at the outer peripheral edge
Middle position.
6. balance weight assembly as described in claim 1, wherein the outer peripheral edge of the counterweight part is in polygonal shape.
7. balance weight assembly as claimed in claim 6, wherein the outer peripheral edge is in equilateral polygon shape.
8. balance weight assembly as claimed in claim 6, wherein the outer peripheral edge is in inequilateral polygonal shape.
9. balance weight assembly as claimed in claim 8, wherein the exterior angle of the inequilateral polygon of the outer peripheral edge is from the front end
Portion changes with changing from small to big to the tail end.
10. balance weight assembly as claimed in any one of claims 1-9 wherein, wherein the front end include preceding axial end surface and
Preceding circumferential ends, the preceding axial end surface tilt axially and circumferentially towards the preceding circumferential ends.
11. balance weight assembly as claimed in claim 10, wherein when radially observing, the front end is formed by
Front end angle is 25 degree to 60 degree.
12. balance weight assembly as claimed in claim 10, wherein the tail end includes tail axial end surface and the circumferential end of tail
End, the tail axial end surface tilt axially and circumferentially towards the tail circumferential ends.
13. balance weight assembly as claimed in any one of claims 1-9 wherein, wherein the front end is streamlined.
14. balance weight assembly as claimed in any one of claims 1-9 wherein, wherein the bushing is that the dynamic vortex is allowed to have
The unloading bushing of radial compliance.
15. a kind of screw compressor, which is characterized in that the screw compressor includes such as any one of claims 1 to 14 institute
The balance weight assembly stated.
16. screw compressor as claimed in claim 15, in which:
The dynamic vortex includes hub, and the drive shaft of the screw compressor includes eccentric crank pin, the eccentric mechanism
Pin is via bushing cooperation to drive the dynamic vortex in the hub；Or the dynamic vortex includes shank, and institute
Stating drive shaft includes eccentric recess portion, and the shank cooperates via the bushing and makes the dynamic vortex quilt in the eccentric recess portion
The drive shaft driving.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201821719127.9U CN208900359U (en) | 2018-10-23 | 2018-10-23 | A counter weight subassembly and scroll compressor for scroll compressor |
| PCT/CN2019/112759 WO2020083312A1 (en) | 2018-10-23 | 2019-10-23 | Counterweight, counterweight assembly and scroll compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201821719127.9U CN208900359U (en) | 2018-10-23 | 2018-10-23 | A counter weight subassembly and scroll compressor for scroll compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN208900359U true CN208900359U (en) | 2019-05-24 |
Family
ID=66576561
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201821719127.9U Active CN208900359U (en) | 2018-10-23 | 2018-10-23 | A counter weight subassembly and scroll compressor for scroll compressor |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN208900359U (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110733669A (en) * | 2019-10-24 | 2020-01-31 | 北京空间技术研制试验中心 | Spacecraft re-entry capsule mass center dynamic adjusting device |
| WO2020083312A1 (en) * | 2018-10-23 | 2020-04-30 | 艾默生环境优化技术(苏州)有限公司 | Counterweight, counterweight assembly and scroll compressor |
| CN112539173A (en) * | 2020-12-03 | 2021-03-23 | 珠海格力节能环保制冷技术研究中心有限公司 | Movable scroll assembly, scroll compressor and air conditioning system |
| 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 |
| US11852144B2 (en) | 2021-09-03 | 2023-12-26 | Danfoss (Tianjin) Ltd. | Scroll compressor |
-
2018
- 2018-10-23 CN CN201821719127.9U patent/CN208900359U/en active Active
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2020083312A1 (en) * | 2018-10-23 | 2020-04-30 | 艾默生环境优化技术(苏州)有限公司 | Counterweight, counterweight assembly and scroll compressor |
| CN110733669A (en) * | 2019-10-24 | 2020-01-31 | 北京空间技术研制试验中心 | Spacecraft re-entry capsule mass center dynamic adjusting device |
| CN110733669B (en) * | 2019-10-24 | 2021-06-18 | 北京空间技术研制试验中心 | Spacecraft re-entry capsule mass center dynamic adjusting device |
| 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 |
| CN112539173A (en) * | 2020-12-03 | 2021-03-23 | 珠海格力节能环保制冷技术研究中心有限公司 | Movable scroll assembly, scroll compressor and air conditioning system |
| US11852144B2 (en) | 2021-09-03 | 2023-12-26 | Danfoss (Tianjin) Ltd. | Scroll compressor |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN208900359U (en) | A counter weight subassembly and scroll compressor for scroll compressor | |
| CN209012065U (en) | A counter weight subassembly and scroll compressor for scroll compressor | |
| US9347450B2 (en) | Centrifugal compressor | |
| CN205823629U (en) | Scroll compressor having a plurality of scroll members | |
| CN207093295U (en) | Axial plunger pump | |
| US5320507A (en) | Scroll machine with reverse rotation protection | |
| JPS61210285A (en) | Rotary compressor | |
| JP2004044576A (en) | Compressor | |
| CN208885525U (en) | Balance weight, balance weight assembly and scroll compressor | |
| JP2000039000A5 (en) | ||
| CN101498306B (en) | Rotary compressor | |
| CN208900360U (en) | Scroll compressor having a plurality of scroll members | |
| CN205001192U (en) | Balancing weight and rotary machine comprising same | |
| JPH0458086A (en) | Fluid compressor | |
| CN108519204A (en) | A kind of adjustable blade vibrator of three-dimensional vibrating mode and its design method | |
| KR20110109090A (en) | Turbo compressor | |
| CN208134589U (en) | A kind of propeller pitch adjusting structure | |
| CN106555755B (en) | Balancing weight and rotary machine comprising same | |
| US11174861B2 (en) | Compressor with discharge valve | |
| CN206429394U (en) | A kind of spacing swinging blower fan of slide plate root roller | |
| WO2020083312A1 (en) | Counterweight, counterweight assembly and scroll compressor | |
| CN112483342A (en) | Compact high-efficient type pump of sound bars is inhaled in area | |
| CN113018614A (en) | Rotary wheel with reduced inertia for a respiratory therapeutic appliance | |
| JPS5965586A (en) | Scroll system pump | |
| JP2004218471A (en) | Hermetic electric compressor |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| GR01 | Patent grant | ||
| GR01 | Patent grant |