CN219344963U - Scroll compression mechanism and scroll compressor - Google Patents
Scroll compression mechanism and scroll compressor Download PDFInfo
- Publication number
- CN219344963U CN219344963U CN202320178897.1U CN202320178897U CN219344963U CN 219344963 U CN219344963 U CN 219344963U CN 202320178897 U CN202320178897 U CN 202320178897U CN 219344963 U CN219344963 U CN 219344963U
- Authority
- CN
- China
- Prior art keywords
- scroll
- orbiting scroll
- thickness
- orbiting
- compression mechanism
- 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
- 230000006835 compression Effects 0.000 title claims abstract description 38
- 238000007906 compression Methods 0.000 title claims abstract description 38
- 230000007246 mechanism Effects 0.000 title claims abstract description 31
- 239000012530 fluid Substances 0.000 claims abstract description 8
- 230000004323 axial length Effects 0.000 claims description 10
- 238000000034 method Methods 0.000 claims description 4
- 208000035874 Excoriation Diseases 0.000 abstract description 7
- 238000005299 abrasion Methods 0.000 abstract description 7
- 230000002035 prolonged effect Effects 0.000 abstract 1
- 238000005452 bending Methods 0.000 description 4
- 238000005192 partition Methods 0.000 description 4
- 238000007789 sealing Methods 0.000 description 3
- 230000009471 action Effects 0.000 description 1
- 238000004378 air conditioning Methods 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000008094 contradictory effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 239000003507 refrigerant Substances 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 239000013585 weight reducing agent Substances 0.000 description 1
Images
Abstract
The present utility model relates to a scroll compression mechanism and a scroll compressor, wherein the scroll compression mechanism comprises: a non-orbiting scroll including a non-orbiting scroll end plate and a non-orbiting scroll vane formed at one side of the non-orbiting scroll end plate; an orbiting scroll including an orbiting scroll end plate and an orbiting scroll vane formed on one side of the orbiting scroll end plate, the orbiting scroll vane intermeshes with the orbiting scroll vane to define a series of compression chambers of the scroll compression mechanism for compressing a working fluid, at least a portion of the orbiting scroll vane having a thickness less than a thickness of at least a portion of the orbiting scroll vane. According to the vortex compression mechanism, the abrasion risk of the thrust plate can be reduced, the thrust plate can be ensured to stably and reliably axially support and thrust the movable vortex, the abrasion of the driving bearing is prevented, and the service life of the driving bearing is prolonged.
Description
Technical Field
The present utility model relates to the field of compressors, and in particular, to a scroll compression mechanism and scroll compressor capable of reducing the mass of orbiting scroll.
Background
The statements in this section merely provide background information related to the present disclosure and may not constitute prior art.
Scroll compressors may be used in, for example, refrigeration systems, air conditioning systems, and heat pump systems. The compression mechanism of the scroll compressor is used as its main component for achieving compression of a working fluid (e.g., refrigerant). The compression mechanism includes a fixed scroll and an orbiting scroll that moves in translation relative to the fixed scroll. The movable vortex can generate huge inertia force when rotating at high speed, and the excessive inertia force can cause the damage of parts of the compressor. In order to balance the inertial force, a counterweight is generally installed in the compressor to balance a part of the inertial force of the orbiting scroll, thereby reducing the load of the compressor components.
However, the conventional scroll compressor has problems of large load of parts, limited rotation speed of the orbiting scroll, and the like. In addition, the greater the mass of the orbiting scroll, the greater the inertial force and thus the greater the weight required, and the provision of such weights may reduce the thrust area of the thrust plate, resulting in greater thrust face pressure and wear of the thrust plate, thereby affecting the operational stability of the scroll compressor. Moreover, the use of a larger counterweight also makes the drive bearing susceptible to wear due to edge contact.
Accordingly, there is a need to provide an improved scroll compression mechanism and scroll compressor.
Disclosure of Invention
It is an object of one or more embodiments of the present utility model to improve the loading of compressor components and to increase the rotational speed of the orbiting scroll.
It is a further object of one or more embodiments of the present utility model to reduce the risk of wear of the thrust plate, ensuring that the thrust plate is able to stably and reliably axially support and thrust the orbiting scroll.
It is a further object of one or more embodiments of the present utility model to prevent vortex instability or tipping, and to prevent wear of the drive bearing, thereby extending the service life of the drive bearing.
According to one aspect of the present utility model, there is provided a scroll compression mechanism comprising: the fixed vortex comprises a fixed vortex end plate and a fixed vortex blade formed on one side of the fixed vortex end plate; an orbiting scroll including an orbiting scroll end plate and an orbiting scroll vane formed at one side of the orbiting scroll end plate, the orbiting scroll vane intermeshed with the orbiting scroll vane to define a series of compression chambers of the scroll compression mechanism for compressing a working fluid; wherein the thickness of at least a portion of the orbiting scroll blade is less than the thickness of at least a portion of the non-orbiting scroll blade.
According to one aspect of the utility model, the orbiting scroll blade has a constant thickness along the axial length and the constant thickness of the orbiting scroll blade is less than the thickness of the non-orbiting scroll blade.
According to one aspect of the utility model, the orbiting scroll blade has a first thickness in a first axial section and a second thickness in a second axial section, the first axial section being closer to the orbiting scroll base than the second axial section, the second thickness being less than the first thickness.
According to one aspect of the utility model, the axial length of the first axial section is smaller than the axial length of the second axial section.
According to one aspect of the utility model, the non-orbiting scroll blade has a third thickness in a third axial section and a fourth thickness in a fourth axial section, the third axial section being closer to the non-orbiting scroll base plate than the fourth axial section, the fourth thickness being less than the third thickness.
According to one aspect of the utility model, the first thickness is less than the fourth thickness.
According to another aspect of the present utility model, there is provided a scroll compressor comprising the above-described scroll compression mechanism.
According to another aspect of the present utility model, the scroll compression mechanism further includes a hub formed at the other side of the movable scroll end plate, and the scroll compressor further includes: a thrust plate provided on the other side of the movable scroll end plate and formed with a thrust portion supporting the movable scroll end plate; and a counterweight disposed between the thrust plate and the hub and configured to at least partially balance inertial forces generated by the orbiting scroll.
According to another aspect of the utility model, the ratio of the outer diameter of the thrust portion to the outer diameter of the weight is in the range of 1.4 to 1.7.
According to another aspect of the utility model, the ratio of the outer diameter of the thrust portion to the outer diameter of the hub portion is in the range of 1.9 to 2.1.
According to another aspect of the present utility model, the scroll compressor further includes an unloading bush provided inside the hub portion, and a driving bearing provided between the hub portion and the unloading bush and fixed to an inner wall surface of the hub portion, and the weight is fixed to the unloading bush.
According to the scroll compressor, the mass of the movable scroll is reduced in a unique mode, so that the load of parts of the compressor can be improved, the rotating speed of the variable frequency compressor can be increased, the thrust surface area of the thrust part can be increased, the axial sealing between the fixed scroll and the movable scroll is ensured, in addition, the bending moment applied to the driving bearing can be lightened, the driving bearing and the unloading bushing are prevented from being correspondingly smaller in size and mass, the unloading bushing and the driving bearing are prevented from being in edge contact, the risk of abrasion of the driving bearing can be reduced, and the thrust surface area of the thrust part can be increased to reduce the abrasion of the thrust part.
Further areas of applicability of the present utility model will become apparent from the detailed description provided hereinafter. It should be understood that the detailed description and specific examples, while indicating the preferred embodiment of the utility model, are intended for purposes of illustration only and are not intended to limit the utility model.
Drawings
The features and advantages of one or more embodiments of the utility model will become more readily apparent from the following description with reference to the accompanying drawings, in which:
fig. 1 is a longitudinal sectional view showing a scroll compressor according to the related art;
fig. 2a and 2b are a sectional view and a partial enlarged view showing a compression mechanism of a scroll compressor according to the related art;
fig. 3a and 3b are a sectional view and a partial enlarged view showing a compression mechanism of a scroll compressor according to a first embodiment of the present utility model;
FIG. 4 is a cross-sectional view showing the orbiting scroll and related components of a scroll compressor according to a first embodiment of the present utility model;
FIG. 5 is a cross-sectional view showing a counterweight, thrust portion, and related components of a scroll compressor according to a first embodiment of the utility model;
fig. 6a and 6b are a perspective view and a longitudinal sectional view showing a non-orbiting scroll of a scroll compressor according to a second embodiment of the present utility model;
fig. 7a and 7b are a perspective view and a longitudinal sectional view showing an orbiting scroll of a scroll compressor according to a second embodiment of the present utility model; and
fig. 8a and 8b are a sectional view and a sectional view showing a compression mechanism of a scroll compressor according to a second embodiment of the present utility model.
Detailed Description
Exemplary embodiments will now be described more fully with reference to the accompanying drawings.
The exemplary embodiments are provided so that this disclosure will be thorough and will fully convey the scope to those skilled in the art. Numerous specific details are set forth, such as examples of specific components, devices, and methods, in order to provide a thorough understanding of embodiments of the present utility model. It will be apparent to those skilled in the art that the exemplary embodiments may be embodied in many different forms without the use of specific details, and should not be construed as limiting the scope of the utility model. In some exemplary embodiments, well-known processes, well-known device structures, and well-known techniques are not described in detail.
The general construction and operation principle of the scroll compressor will be described first with reference to fig. 1. As shown in fig. 1, a scroll compressor 1 (hereinafter, also sometimes referred to as a compressor) may include a housing 10, a top cover provided at one end of the housing 10, a bottom cover provided at the other end of the housing 10, and a partition 12 provided between the top cover and the housing 10 to partition an inner space of the compressor into a high pressure side and a low pressure side. The space between the partition 12 and the top cover constitutes a high pressure side, and the space between the partition 12, the housing 10 and the bottom cover constitutes a low pressure side. A motor composed of a stator and a rotor is provided in the housing 10. A driving shaft is provided in the rotor to drive a compression mechanism composed of the fixed scroll 20 and the movable scroll 30. The orbiting scroll 30 includes an orbiting scroll end plate 32, a spiral orbiting scroll blade 34 formed on one side of the orbiting scroll end plate, and a hub 36 formed on the other side of the orbiting scroll end plate. The non-orbiting scroll 20 includes a non-orbiting scroll end plate 22, a spiral non-orbiting scroll blade 24 formed at one side of the non-orbiting scroll end plate, and an exhaust port formed at a substantially central position of the non-orbiting scroll end plate. A series of compression chambers whose volumes gradually decrease from the radially outer side to the radially inner side are formed between the fixed scroll blade 24 of the fixed scroll 20 and the movable scroll blade 34 of the movable scroll 30.
One end of the drive shaft is supported by a main bearing housing 40. An eccentric crank pin 52 is provided at one end of the drive shaft, and an unloading bushing 62 (see fig. 4) and a drive bearing (not shown) are provided between the eccentric crank pin 52 and the hub portion 36 of the orbiting scroll 30. The unloading bush 62 may be disposed inside the hub portion, and the driving bearing may be disposed between the hub portion and the unloading bush and fixed to an inner wall surface of the hub portion. By the driving of the motor, the orbiting scroll 30 translationally moves with respect to the non-orbiting scroll 20 (i.e., the central axis of the orbiting scroll 30 rotates about the central axis of the non-orbiting scroll 20, but the orbiting scroll 30 itself does not rotate about its central axis) to effect compression of a fluid. The fluid compressed by the fixed scroll 20 and the movable scroll 30 is discharged to the high pressure side through the discharge port.
In order to achieve compression of the fluid, an effective axial seal is required between the fixed scroll 20 and the orbiting scroll 30. Specifically, axial seals are required between the tips of the fixed scroll blades 24 of the fixed scroll 20 and the orbiting scroll end plate 32 of the orbiting scroll 30 and between the tips of the orbiting scroll blades 34 of the orbiting scroll 30 and the fixed scroll end plate 22. In general, a back pressure chamber is provided on the side of the non-orbiting scroll end plate 22 opposite to the non-orbiting scroll 24. The back pressure chamber is in fluid communication with the intermediate pressure chamber through axially extending through holes (not shown) formed in the end plate 22 to create a force that presses the non-orbiting scroll 20 against the orbiting scroll 30. Meanwhile, the opposite side of the orbiting scroll 30 is axially supported/thrust by the thrust portion 72 of the thrust plate 70 (specifically, the thrust surface of the thrust portion 72) against the orbiting scroll end plate 32, so the fixed scroll 20 and the orbiting scroll member 30 can be effectively pressed together by the back pressure chamber and the thrust plate.
During operation of the scroll compressor 1, centrifugal or inertial forces resulting from the orbiting scroll may cause vibration of the compressor and even damage to compressor components. For this purpose, a balance weight 80 is provided to provide a counter centrifugal force or an inertial force to balance a part of the inertial force generated by the orbiting scroll. A balance weight 80 may be provided in a space between the hub portion 36 of the orbiting scroll 30 and the thrust plate 70. The counterweight 80 may be fixed to the unloading bushing by an interference fit, for example, so as to rotate in the above-mentioned space under the action of the drive shaft.
In the scroll compressor, the outer diameter of the orbiting scroll end plate 32 (i.e., the distance from the outer periphery of the orbiting scroll end plate 32 to the centerline of the scroll compressor) is limited by the size of the housing 10. The outer diameter of the thrust portion 72 of the thrust plate 70 (i.e., the distance from the outer periphery of the thrust portion 72 to the centerline of the scroll compressor) is the difference between the outer diameter of the orbiting scroll end plate 32 and the radius of rotation of the compressor. The area of the thrust surface of the thrust portion 72 that contacts the orbiting scroll end plate 32 is an annular area between the outer diameter and the inner diameter of the thrust portion 72. The weight 80 needs to have a large size in order to provide a sufficient counter centrifugal force or inertial force to balance a part of the inertial force generated by the orbiting scroll. In this case, the inner diameter of the thrust plate 70 needs to be set large enough to provide the required space for the balance weight 80, thereby making the area of the thrust surface of the thrust plate 70 small and the pressure of the thrust surface increasing. This may cause the thrust portion 72 to be easily worn, and the thrust portion may not be able to stably and reliably secure the axial seal between the fixed scroll and the movable scroll, affecting the operation stability of the scroll compressor.
Furthermore, during normal operation of the scroll compressor, the unloading bushing 62 and the drive bearing are in surface contact with each other and do not interfere with each other. However, since the weight of the weight 80 fixed to the unloading bushing 62 is large, the unloading bushing 62 receives a bending moment applied by the weight 80 to come into edge contact with the driving bearing, which causes abrasion of the driving bearing, affecting the service life of the driving bearing.
In order to solve the above problems, the present inventors have conceived an improved scroll compressor. The scroll compressor according to the present utility model will be described in further detail with reference to the accompanying drawings, wherein like reference numerals denote like parts, and a detailed description of the parts will be omitted.
The thickness of at least a portion of the orbiting scroll blade of the orbiting scroll of the compression mechanism of the scroll compressor according to the present utility model may be smaller than the thickness of at least a portion of the non-orbiting scroll blade of the non-orbiting scroll. Referring to fig. 3a and 3b, the orbiting scroll blade 34a of the orbiting scroll of the compression mechanism of the scroll compressor according to the first embodiment of the present utility model may have a constant thickness along the axial length, and the constant thickness of the orbiting scroll blade 34a may be smaller than that of the non-orbiting scroll blade 24. In the present application, "the thickness of at least a portion of the orbiting scroll blade is smaller than the thickness of at least a portion of the non-orbiting scroll blade" may refer to: the thickness of at least a portion of the orbiting scroll blade is less than the thickness of a portion of the non-orbiting scroll blade corresponding to the position of the at least a portion of the orbiting scroll blade in the direction of the scroll line and/or in the direction of the scroll axis.
In the scroll compressor according to the related art, as shown in fig. 2a and 2b, the thickness of the orbiting scroll blade is the same as that of the non-orbiting scroll blade. In the scroll compressor according to the first embodiment of the present utility model, however, since the thickness of the orbiting scroll blade 34a is designed to be smaller than that of the non-orbiting scroll blade 24, the weight of the entire orbiting scroll 30a can be reduced. At this time, the inertial force generated by the orbiting scroll is reduced, and accordingly, the weight 80a for balancing the inertial force of the orbiting scroll 30a may have a reduced weight and thus a reduced size. In this way, the space for disposing the weight 80a inside the thrust portion 72a can be reduced, so that the area of the thrust surface of the thrust portion 72a in contact with the base plate 32a of the orbiting scroll 30a can be increased, thereby ensuring reliable and stable axial support/thrust of the orbiting scroll 30a by the thrust plate 70, ensuring stable orbiting of the orbiting scroll 30a, and achieving effective axial sealing between the fixed scroll 20 and the orbiting scroll 30 a.
The scroll compressor according to the first embodiment of the present utility model can reduce the weight of the orbiting scroll by up to 20% by having a reduced thickness of the orbiting scroll blade, compared to a compression mechanism in which the fixed scroll blade and the orbiting scroll blade have the same thickness. In one example, the ratio of the outer diameter of the thrust portion to the outer diameter of the weight of the scroll compressor according to the related art is about 1.28. In contrast, in the scroll compressor according to the first embodiment of the present utility model, referring to fig. 4, since the size of the weight 80a may be reduced, the ratio of the outer diameter r3 of the thrust portion 72a to the outer diameter r2 of the weight 80a (i.e., the outer diameter at the portion of the weight where the weight is disposed, that is, the distance from the outermost periphery of the weight to the center line of the scroll compressor) may be in the range of 1.4 to 1.7. Thus, as shown in fig. 5, the area S of the annular thrust surface of the thrust portion 72a can be significantly increased. Preferably, the radius r1 of the hub portion 36a of the orbiting scroll (i.e., the distance from the outer periphery of the hub portion 36a to the center line of the scroll compressor) may also be reduced so as to dispose the weight 80a at a position closer to the radially inner side to further increase the area of the thrust surface. Illustratively, the ratio of the outer diameter r3 of the thrust portion 72a to the radius r1 of the orbiting scroll hub 36a may be in the range of 1.9 to 2.1.
In the scroll compressor according to the first embodiment of the present utility model, the orbiting scroll 30a has a reduced weight, the load of the compressor components (such as a reduced scroll sidewall load and a reduced scroll screw load) can be improved, and the rotational speed of the compressor can be further increased. Due to the reduced weight of orbiting scroll 30, counterweight 80a may have a reduced size (e.g., its outer diameter r2 is reduced) such that only a small space may be reserved inside thrust portion 72a for providing counterweight 80a, thereby increasing the thrust surface area of thrust portion 72a, ensuring an axial seal between the fixed and orbiting scrolls. In addition, the weight of the balance weight 80a can be reduced, so that the bending moment applied to the driving bearing by the balance weight can be reduced, the edge contact between the driving bearing and the unloading bushing is avoided, and the abrasion risk of the driving bearing is reduced.
Fig. 6a and 6b are perspective and longitudinal sectional views showing a fixed scroll of a scroll compressor according to a second embodiment of the present utility model, fig. 7a and 7b are perspective and longitudinal sectional views showing an orbiting scroll of a scroll compressor according to a second embodiment of the present utility model, and fig. 8a and 8b are sectional and sectional views showing a compression mechanism of a scroll compressor according to a second embodiment of the present utility model. The scroll compressor according to the second embodiment of the present utility model is similar in structure to the scroll compressor according to the related art in that the fixed scroll 20 and the movable scroll 30 according to the related art are replaced with the fixed scroll 20b and the movable scroll 30b, and other configurations of the scroll compressor are substantially unchanged.
As shown in fig. 7b and 8a, the orbiting scroll blade 34b of the orbiting scroll 30b of the scroll compressor according to the second embodiment of the present utility model has a different thickness along the axial length thereof. Specifically, the orbiting scroll blade 34b may have a first thickness t1 in a first axial section and a second thickness t2 in a second axial section, the first axial section may be closer to the orbiting scroll base 32b than the second axial section, the second thickness t2 being less than the first thickness t1. In this way, by reducing the thickness of the orbiting scroll blade 34b in the second axial section, the weight of the orbiting scroll 30b may be reduced.
The orbiting scroll blade 34b may have a larger thickness at a first axial section adjacent to the orbiting scroll base plate 32b, whereby the connection strength of the orbiting scroll blade 34b with the orbiting scroll base plate 32b may be ensured. Preferably, as shown in fig. 7b, the axial length of the first axial section may be smaller than the axial length of the second axial section, in this way, the weight of the orbiting scroll 30b may be further reduced.
The fixed scroll 20b may be formed corresponding to the movable scroll 30 b. Specifically, as shown in fig. 6b, the non-orbiting scroll 24b may have a third thickness t3 at a third axial section and a fourth thickness t4 at a fourth axial section, the third axial section being closer to the non-orbiting scroll base 22b than the fourth axial section, and the fourth thickness t4 may be less than the third thickness t3. In this way, the connection strength of the non-orbiting scroll blade 24b and the non-orbiting scroll base plate 22b can be ensured. As shown in fig. 8a, the first thickness t1 of the orbiting scroll blade 34b may be smaller than the fourth thickness t4 of the non-orbiting scroll blade 24b, i.e., the first thickness t1 of the first axial section of the orbiting scroll blade 34b that is thicker may be smaller than the fourth thickness t4 of the fourth axial section of the non-orbiting scroll blade 24b that is thinner, in this way, the weight of the orbiting scroll 30b may be further reduced.
In the scroll compressor according to the second embodiment of the present utility model, the orbiting scroll 30b has a reduced weight, the load of the compressor components (such as a reduced scroll sidewall load and a reduced scroll screw load) can be improved, and the rotational speed of the compressor can be further increased. Due to the weight reduction of the orbiting scroll 30b, the weight may have a reduced size such that only a small space may be reserved inside the thrust portion for providing the weight, whereby the thrust surface area of the thrust portion may be increased, ensuring axial sealing between the fixed scroll and the orbiting scroll. And moreover, the weight of the balance weight can be reduced, so that the bending moment applied to the driving bearing by the balance weight can be reduced, the edge contact between the driving bearing and the unloading bushing is avoided, and the abrasion risk of the driving bearing is reduced.
In the example of the scroll compressor according to the related art, the radius R1 of the boss portion is 29.5mm, the outer diameter R2 of the weight 80a is 41mm, and the annular thrust surface area s=pi (R32-R22) of the thrust portion is 4000mm2, where r2/r1=1.4, r3/r1=1.8. In the scroll compressor with the improved scroll blade according to the present utility model, the radius r1 of the boss portion is 25.0mm, the outer diameter r2 of the balance weight 80a is 33mm, and the annular thrust surface area S of the thrust portion is=4900 mm2, where r 2/r1=1.4, r 3/r1=1.8. It is apparent that in the scroll compressor having the improved scroll blade according to the present utility model, the thrust surface area of the thrust portion may be increased, thereby securing the axial seal between the fixed scroll and the movable scroll.
While the present utility model has been described with reference to exemplary embodiments, it is to be understood that the utility model is not limited to the specific embodiments described and illustrated herein, and that various changes in the exemplary embodiments may be made by those skilled in the art without departing from the scope defined by the claims. It should also be understood that features of the various embodiments may be combined with each other or omitted where the technical solutions are not contradictory.
Claims (11)
1. A scroll compression mechanism comprising:
a non-orbiting scroll including a non-orbiting scroll end plate and a non-orbiting scroll blade formed at one side of the non-orbiting scroll end plate; and
an orbiting scroll including an orbiting scroll end plate and an orbiting scroll vane formed at one side of the orbiting scroll end plate, the orbiting scroll vane intermeshed with the orbiting scroll vane to define a series of compression chambers of the scroll compression mechanism for compressing a working fluid,
it is characterized in that the method comprises the steps of,
the thickness of at least a portion of the orbiting scroll blade is less than the thickness of at least a portion of the non-orbiting scroll blade.
2. The scroll compression mechanism of claim 1, wherein,
the orbiting scroll blade has a constant thickness along an axial length, and the constant thickness of the orbiting scroll blade is less than the thickness of the non-orbiting scroll blade.
3. The scroll compression mechanism of claim 1, wherein,
the orbiting scroll blade has a first thickness in a first axial section and a second thickness in a second axial section, the first axial section being closer to the orbiting scroll base than the second axial section, the second thickness being less than the first thickness.
4. A scroll compression mechanism according to claim 3, wherein,
the axial length of the first axial section is less than the axial length of the second axial section.
5. The scroll compression mechanism of claim 4, wherein the scroll compressor is configured to compress the compressed air,
the non-orbiting scroll blade has a third thickness at a third axial section and a fourth thickness at a fourth axial section, the third axial section being closer to the non-orbiting scroll base plate than the fourth axial section, the fourth thickness being less than the third thickness.
6. The scroll compression mechanism of claim 5, wherein,
the first thickness is less than the fourth thickness.
7. A scroll compressor comprising the scroll compression mechanism of any one of claims 1-6.
8. The scroll compressor of claim 7, wherein,
the scroll compression mechanism further includes a hub formed at the other side of the movable scroll end plate, and
the scroll compressor further includes:
a thrust plate provided on the other side of the movable scroll end plate and formed with a thrust portion supporting the movable scroll end plate; and
a counterweight disposed between the thrust plate and the hub and configured to at least partially balance inertial forces generated by the orbiting scroll.
9. The scroll compressor of claim 8, wherein,
the ratio of the outer diameter of the thrust portion to the outer diameter of the weight is in the range of 1.4 to 1.7.
10. The scroll compressor of claim 8, wherein,
the ratio of the outer diameter of the thrust portion to the outer diameter of the hub portion is in the range of 1.9 to 2.1.
11. The scroll compressor of any one of claims 8-10, wherein:
the scroll compressor further includes an unloading bush provided inside the hub, and a driving bearing provided between the hub and the unloading bush and fixed to an inner wall surface of the hub, and,
the counterweight is secured to the unloading bushing.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202320178897.1U CN219344963U (en) | 2023-02-10 | 2023-02-10 | Scroll compression mechanism and scroll compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202320178897.1U CN219344963U (en) | 2023-02-10 | 2023-02-10 | Scroll compression mechanism and scroll compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN219344963U true CN219344963U (en) | 2023-07-14 |
Family
ID=87110618
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202320178897.1U Active CN219344963U (en) | 2023-02-10 | 2023-02-10 | Scroll compression mechanism and scroll compressor |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN219344963U (en) |
-
2023
- 2023-02-10 CN CN202320178897.1U patent/CN219344963U/en active Active
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US5213489A (en) | Scroll compressor with axial vibration prevention for a shaft bearing | |
| KR100330456B1 (en) | Scroll Machine with Reduced Reverse Noise | |
| KR100916554B1 (en) | Scroll compressor having a clearance for the oldham coupling | |
| US6752607B2 (en) | Apparatus for reducing friction loss in scroll compressor | |
| JPH0545800B2 (en) | ||
| KR0169333B1 (en) | Operating device for scroll compressor | |
| EP1818541B1 (en) | Horizontally-mounted scroll compressor | |
| WO2017159393A1 (en) | Scroll compressor | |
| US5540572A (en) | Structure for preventing axial leakage in scroll compressor | |
| KR20140142046A (en) | Scroll compressor | |
| US6179591B1 (en) | Conical hub bearing for scroll machine | |
| CN219344963U (en) | Scroll compression mechanism and scroll compressor | |
| CN112460017A (en) | Pump body assembly and fluid machine with same | |
| JP4618645B2 (en) | Scroll compressor | |
| CN217327670U (en) | Bushing assembly and scroll compressor | |
| CN113482923B (en) | Compression assembly, scroll compressor and air conditioner | |
| CN113530827A (en) | Scroll compressor having a plurality of scroll members | |
| WO2024042984A1 (en) | Scroll compressor | |
| JP2003301784A (en) | Rotation preventing mechanism of scroll fluid machine | |
| CN218493802U (en) | Scroll compressor having a discharge port for discharging refrigerant from a discharge chamber | |
| JPS62126203A (en) | Scroll hydraulic machine | |
| CN212643042U (en) | Compression mechanism and scroll compressor comprising same | |
| CN220869651U (en) | Scroll compressor having a rotor with a rotor shaft having a rotor shaft with a | |
| WO2022000887A1 (en) | Compression mechanism and scroll compressor comprising compression mechanism | |
| CN212155162U (en) | Scroll compressor having a plurality of scroll members |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| CP03 | Change of name, title or address |
Address after: No. 69 Suhong West Road, Industrial Park, Suzhou City, Jiangsu Province, 215101 Patentee after: Gulun Environmental Technology (Suzhou) Co.,Ltd. Country or region after: China Address before: Emerson R & D and overall solution center, No. 35, Suhong West Road, Suzhou Industrial Park, Suzhou, Jiangsu 215101 Patentee before: EMERSON CLIMATE TECHNOLOGIES (SUZHOU) Co.,Ltd. Country or region before: China |