CN218030611U - Compression mechanism and scroll compressor - Google Patents
Compression mechanism and scroll compressor Download PDFInfo
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- CN218030611U CN218030611U CN202222076401.8U CN202222076401U CN218030611U CN 218030611 U CN218030611 U CN 218030611U CN 202222076401 U CN202222076401 U CN 202222076401U CN 218030611 U CN218030611 U CN 218030611U
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- 238000007906 compression Methods 0.000 title claims abstract description 67
- 230000006835 compression Effects 0.000 title claims abstract description 65
- 230000007246 mechanism Effects 0.000 title claims abstract description 25
- 239000012530 fluid Substances 0.000 claims abstract description 92
- 238000004891 communication Methods 0.000 claims abstract description 5
- 238000005192 partition Methods 0.000 claims description 12
- 230000004323 axial length Effects 0.000 claims description 7
- 230000000903 blocking effect Effects 0.000 claims description 7
- 230000000694 effects Effects 0.000 description 6
- 230000000052 comparative effect Effects 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 230000009471 action Effects 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 125000006850 spacer group Chemical group 0.000 description 2
- 239000002699 waste material Substances 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000009977 dual effect Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000005381 potential energy Methods 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 239000003507 refrigerant Substances 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 230000003014 reinforcing effect Effects 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
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Abstract
The utility model relates to a compression mechanism, it includes: a non-orbiting scroll which is an integral part and includes a non-orbiting scroll end plate and a non-orbiting scroll blade which are integrally formed; an orbiting scroll including an orbiting scroll end plate and orbiting scroll blades formed at a first side of the orbiting scroll end plate, and the non-orbiting scroll blades and the orbiting scroll blades being engaged with each other to form a series of compression chambers therebetween capable of compressing a fluid; and a back pressure chamber in fluid communication with one of the series of compression chambers through a back pressure passage to apply a back pressure that engages the orbiting scroll with the non-orbiting scroll; the back pressure passage includes an expansion section having a fluid flow cross-sectional area larger than a fluid flow cross-sectional area of each of the narrowing sections, and narrowing sections formed on opposite sides of the expansion section. The utility model discloses still relate to the scroll compressor including this compression mechanism. According to the utility model discloses a scroll compressor has the reliability that improves and can prevent energy loss and efficiency extravagant.
Description
Technical Field
The utility model relates to a compression mechanism and have this compression mechanism's scroll compressor.
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 applications such as refrigeration systems, air conditioning systems, and heat pump systems. A compression mechanism of a scroll compressor is used as its main component for achieving compression of a working fluid (e.g., refrigerant). The compression mechanism comprises a fixed scroll and an movable scroll which orbits in translation relative to the fixed scroll. The fixed scroll and the orbiting scroll each include an end plate and a spiral vane extending from one side of the end plate. When the movable scroll orbits relative to the fixed scroll, a series of moving compression chambers are formed between the spiral vanes of the fixed scroll and the movable scroll, the volumes of which gradually decrease from the radially outer side to the radially inner side, thereby compressing the working fluid.
A back pressure chamber is provided in the scroll compressor to provide a back pressure that engages the fixed scroll and the orbiting scroll in an axial direction. However, in the actual operation of the scroll compressor, there is a risk that the fluctuation of the pressure in the back pressure chamber causes a reduction in the operational reliability of the compressor, and there is a risk that the recharge of the working fluid into the compression chamber causes repeated compression, resulting in a loss of energy and a waste of efficiency of the scroll compressor.
Accordingly, there is a need to provide an improved compression mechanism and scroll compressor.
SUMMERY OF THE UTILITY MODEL
An object of one or more embodiments of the present invention is to provide a compression mechanism and a scroll compressor having improved reliability and preventing energy loss and efficiency waste.
According to an aspect of the utility model, provide a compression mechanism includes: the fixed scroll is an integral component and comprises a fixed scroll end plate and a fixed scroll blade which are integrally formed, and the fixed scroll blade is formed on the first side of the fixed scroll end plate; an orbiting scroll including an orbiting scroll end plate and orbiting scroll blades formed at a first side of the orbiting scroll end plate, and the stationary scroll blades and the orbiting scroll blades being engaged with each other to form a series of compression chambers therebetween capable of compressing a fluid; and a back pressure chamber in fluid communication with one of the series of compression chambers through a back pressure passage to apply a back pressure that engages the orbiting scroll with the non-orbiting scroll; characterized in that the back pressure passage includes an expansion section and narrowing sections formed on opposite sides of the expansion section, and the fluid flow cross-sectional area of the expansion section is larger than the fluid flow cross-sectional area of each of the narrowing sections.
Optionally, the central axis of one of the narrowing sections is offset from the central axis of the other of the narrowing sections.
Optionally, the backpressure passage comprises two or more expansion sections, and opposing sides of each of the expansion sections are formed with a narrowing section.
Optionally, the back pressure passage is formed in and extends through the non-orbiting scroll end plate, the non-orbiting scroll further comprising a non-orbiting scroll hub formed on a second side of the non-orbiting scroll end plate opposite the first side, the non-orbiting scroll hub comprising a first annular hub and a second annular hub, the back pressure chamber being constituted by a space surrounded by the non-orbiting scroll end plate, the first annular hub and the second annular hub.
Alternatively, the back pressure passage includes a first narrowed section opened to one compression chamber and a second narrowed section opened to the back pressure chamber, opposite sides of the non-orbiting scroll end plate are machined with a first bore and a second bore communicating with each other, an aperture of the second bore is larger than an aperture of the first bore and the second bore has an end opened to the back pressure chamber, the end is mounted with a partition including a through hole allowing a fluid to flow therethrough and a blocking portion blocking the fluid flow, the first narrowed section is formed of the first bore, the second narrowed section is formed of the through hole, and the expanded section is formed of a portion of the second bore where the partition is not mounted.
Optionally, the divider is removably mounted to an end of the second bore and the divider includes a plurality of spaced apart through holes.
Optionally, a back pressure passage is formed in and extends through the orbiting scroll end plate, the back pressure chamber being formed on a second side of the orbiting scroll end plate opposite the first side.
Optionally, the axial length of the expanding section is greater than the axial length of each of the narrowing sections.
Optionally, each of the narrowing sections has the same flow cross-sectional area, the fluid flow cross-sectional area of the expansion section being in the range of 1.1 to 1.5 times the flow cross-sectional area of the narrowing section, or the narrowing sections each have a different flow cross-sectional area, the fluid flow cross-sectional area of the expansion section being in the range of 1.1 to 1.5 times the maximum fluid flow cross-sectional area of the narrowing section.
Further areas of applicability of the present disclosure 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 disclosure, are intended for purposes of illustration only and are not intended to limit the disclosure.
Drawings
Features and advantages of one or more embodiments of the present disclosure will become more readily understood from the following description with reference to the accompanying drawings, in which:
fig. 1 is a sectional view showing a scroll compressor according to a comparative example;
FIGS. 2a and 2b are schematic views illustrating a variation of compression chambers to which a back pressure passage communicates during an operation of the scroll compressor;
fig. 3 is a sectional view illustrating a non-orbiting scroll of a scroll compressor according to a first embodiment of the present disclosure;
fig. 4 is a sectional view illustrating a non-orbiting scroll of a scroll compressor according to a second embodiment of the present disclosure; and
fig. 5 is a sectional view illustrating a non-orbiting scroll of a scroll compressor according to a third embodiment of the present disclosure.
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 more 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 to provide a thorough understanding of embodiments of the present disclosure. It will be apparent to those skilled in the art that specific details need not be employed, that example embodiments may be embodied in many different forms and that neither should be construed to limit the scope of the disclosure. In some example embodiments, well-known processes, well-known device structures, and well-known technologies are not described in detail.
The overall structure of the scroll compressor 1 is described below with reference to fig. 1. As shown, the scroll compressor 1 includes a compression mechanism, a motor, a rotary shaft, a main bearing housing 50, and a housing defining an internal space accommodating the scroll compression mechanism.
The compression mechanism includes a fixed scroll 20 and an orbiting scroll 30. The motor is configured to rotate the rotating shaft, which in turn drives the orbiting scroll 30 to orbit relative to the non-orbiting scroll 20 (i.e., the central axis of the orbiting scroll orbits the central axis of the non-orbiting scroll, but the orbiting scroll does not rotate about its central axis) to compress the working fluid.
The non-orbiting scroll 20 may be fixed relative to the housing body 10 in any suitable manner. The non-orbiting scroll 20 may include a non-orbiting scroll end plate 22, a non-orbiting scroll blade 24 formed at one side of the non-orbiting scroll end plate 22, and a non-orbiting scroll hub formed at the other side of the non-orbiting scroll end plate 22. The non-orbiting scroll hub may include a first annular hub 26 and a second annular hub 28.
Main bearing housing 50 is adapted to support orbiting scroll end plate 32 of orbiting scroll 30. Orbiting scroll end plate 32 orbits on the bearing surface of main bearing housing 50. The main bearing housing 50 may be secured relative to the housing body 10 of the scroll compressor 1 by any suitable means.
In normal operation of the compressor 1, the non-orbiting scroll 20 and the orbiting scroll 30 must be engaged with each other in an axial direction to compress a working fluid. In addition, in order to provide a certain axial flexibility to the scroll assembly to increase reliability and safety of the compressor, a back pressure chamber is generally provided to one of the non-orbiting scroll 20 and the orbiting scroll 30, thereby enabling the non-orbiting scroll 20 and the orbiting scroll 30 to be reliably engaged with each other by a back pressure. As shown in fig. 1, the first annular hub 26 is formed around the exhaust port 40. The back pressure chamber 70 is formed by the space surrounded by the non-orbiting scroll end plate 22, the first annular hub portion 26, and the second annular hub portion 28 and is closed by a seal assembly disposed therein. The back pressure chamber 70 is in fluid communication with one of a series of compression chambers between the orbiting scroll 30 and the non-orbiting scroll 20 through a back pressure passage 60 formed in the non-orbiting scroll end plate 22, thereby applying a back pressure that engages the orbiting scroll 30 with the non-orbiting scroll 20, and the non-orbiting scroll 20 and the orbiting scroll 30 may be effectively pressed together by the back pressure in the back pressure chamber 70.
However, during operation of the scroll compressor, the volume of the compression chambers through which the back pressure passage 60 communicates, and the corresponding pressure, is dynamically varied. Specifically, as shown in fig. 2 (a), the back pressure channel communicates with a compression chamber (a region covered by a shadow) having a small volume, and the pressure in the compression chamber is large, and at this time, the fluid in the compression chamber flows into the back pressure chamber; as the orbiting scroll 30 orbits around the non-orbiting scroll 20, as shown in fig. 2 (b), the back pressure passage will communicate with the compression chamber (the area covered by the shadow) having a large volume, and the pressure in the compression chamber will be small, and at this time, the fluid in the back pressure chamber will be refilled into the compression chamber. The recharging of the fluid into the compression chamber will be repeated by the scroll compressor, which results in wasted energy and efficiency of the scroll compressor, and the reliability of the scroll compressor is reduced because the pressure in the back pressure chamber is not maintained stable as the compression process fluctuates.
In order to solve the above problem, the present invention discloses an improved compression mechanism and scroll compressor, which not only can reduce or prevent the backpressure of the scroll compressor from fluctuating and prevent the fluid from recharging from the backpressure chamber to the compression chamber to generate repeated compression.
A scroll compressor in accordance with the present disclosure is described in further detail below with reference to fig. 3-5, wherein like reference numerals designate like parts throughout the drawings and detailed descriptions of the parts will be omitted.
The scroll compressor according to the first embodiment of the present disclosure is similar in structure to the scroll compressor according to the comparative example described above, in which the non-orbiting scroll 20 according to the comparative example is replaced with only the non-orbiting scroll 20A shown in fig. 3, and other configurations of the scroll compressor are substantially unchanged.
As shown in fig. 3, the non-orbiting scroll 20A may be a unitary component and include a non-orbiting scroll end plate 22 integrally formed, and a non-orbiting scroll blade 24, wherein the non-orbiting scroll blade 24 may be formed on a first side of the non-orbiting scroll end plate 22. The integral type fixed scroll means that the fixed scroll is formed in a single piece processed integrally, rather than a split type fixed scroll formed by connecting a plurality of components. The non-orbiting scrolls also include non-orbiting scroll hubs 26, 28, which may be formed on a second side of the non-orbiting scroll end plate 22 opposite the first side. It will be appreciated that the non-orbiting scroll hubs 26, 28 are integrally formed with the non-orbiting scroll end plate 22, rather than being formed as two separate components that are mechanically interconnected or fixed.
A back pressure passage 60A may be provided in the non-orbiting scroll end plate 22 to fluidly communicate one of the series of compression chambers with the back pressure chamber 70. The back pressure passage 60A may include an expansion section 62A and a narrowing section formed at opposite sides of the expansion section (herein, the narrowing section opened to the compression chamber is referred to as a first narrowing section 64A, and the narrowing section opened to the back pressure chamber 70 is referred to as a second narrowing section 66A). The fluid flow cross-sectional area of the expanding section 62A may be greater than the fluid flow cross-sectional area of either of the first and second narrowing sections 64A, 66A. Herein, a cross section perpendicular to a fluid moving direction is referred to as a fluid flow cross section, and an area size thereof is referred to as a fluid flow cross section area.
When the fluid flows from the compression chamber to the back pressure chamber, the fluid first flows through the first constriction section 64A, and the fluid undergoes a process of narrowing from a larger fluid flow cross-sectional area in the compression chamber, whereby the flow velocity becomes larger, the dynamic pressure increases, and the static pressure decreases. Then, the fluid enters the expansion section 62A from the first narrowing section 64A, the high-speed fluid ejected from the first narrowing section 64A forms a high-speed main fluid in the middle of the expansion section 62A, symmetrical vortexes are formed on two sides of the main fluid, the high-speed main fluid continuously interacts with the vortexes on two sides, the fluid in the vortexes is pulled forwards by the middle high-speed main fluid, so that the speed of the middle high-speed main fluid is reduced, the speed of the vortex fluid is increased, and the vortex fluid flows back until the middle main fluid is insufficient to overcome the pressure difference, and the middle fluid area is enlarged. At this time, the fluid passes through the second narrowing section 66A, the fluid flow cross-sectional area is again reduced, and the kinetic energy is rapidly converted into pressure potential energy. Thus, the fluid undergoes a dual throttling action. Similarly, when fluid flows from the back pressure chamber to the compression chamber, the fluid flows first through the second narrowing section 66A, then from the second narrowing section 66A into the expansion section 62A, and finally through the first narrowing section 64A, the fluid also undergoes a double throttling action. From this, back pressure passageway 60A can produce the effect of secondary throttle, and the flow resistance of back pressure chamber and compression chamber has been increased to this kind of the throttle effect of reinforcing for back pressure in the back pressure chamber can remain stable and prevent that fluid recharge from taking place the repeated compression to the compression chamber, thereby improves scroll compressor performance.
Preferably, the axial length of the expansion section 62A may be greater than the axial length of each of the first and second narrowing sections 64A, 66A, and the throttling effect of the back pressure passage may be further enhanced by increasing the axial length of the expansion section 62A, so that the back pressure will be further kept stable and the fluid is prevented from being repeatedly compressed. And preferably, the fluid flow cross-sectional area of the expanding section 62A may be in the range of 1.1 to 1.5 times the fluid flow cross-sectional area of the first or second narrowing section 66A or 66A. It should be noted that the first and second narrowing sections 64A and 66A may have the same fluid flow cross-sectional area, and in this case, the fluid flow cross-sectional area of the expansion section 62A may be in the range of 1.1 to 1.5 times the fluid flow cross-sectional area of the first or second narrowing section 64A or 66A. The first narrowing section 64A may also have a different cross-sectional fluid flow area than the second narrowing section 66A, in which case the cross-sectional fluid flow area of the expanding section 62A may be in the range of 1.1 to 1.5 times the larger cross-sectional fluid flow area of the first narrowing section 64A and the second narrowing section 66A. By making the fluid flow cross-sectional area of the expanded section 62A only slightly larger than the fluid flow cross-sectional areas of the first and second narrowed sections 64A and 66A, it is also possible to further enhance the throttling effect of the back pressure passage, thereby keeping the back pressure stable and preventing the fluid from being compressed repeatedly.
Illustratively, opposite sides of the non-orbiting scroll end plate 22 may be machined with communicating first and second bores, the second bore having a larger bore diameter than the first bore and having an end opening to the back pressure chamber 70 in which the partition 80A is mounted. The partition 80A may include a through hole 82A allowing fluid to flow therethrough and a blocking portion 84A blocking fluid flow. At this time, the first narrowed section 64A may be formed of the first bore, the second narrowed section 66A may be formed of the through hole 82A, and the expanded section 62A may be formed of a portion of the second bore where the spacer 80 is not installed. The spacer may be, for example, a screw formed with an external thread to be detachably mounted into the second bore. In this way, the fixed scroll having the secondary throttling effect can be simply machined. The partition 80A is shown in fig. 3 as including a plurality of spaced through holes by way of example, although the partition may be formed with other forms of through holes. It should be understood that, in the case where the partition 80A includes a plurality of through holes, the fluid flow cross-sectional area of the second narrowed portion 66A is the sum of the fluid flow cross-sectional areas of the plurality of through holes.
FIG. 4 is a cross-sectional view showing a non-orbiting scroll of a scroll compressor according to a second embodiment of the present disclosure. The non-orbiting scroll 20B of the scroll compressor according to the second embodiment of the present disclosure has a structure similar to that of the non-orbiting scroll 20A of the scroll compressor according to the first embodiment of the present disclosure described above, except for the structure of the back pressure passage, and only the difference will be described in detail below.
The non-orbiting scroll back pressure passage 60B according to the second embodiment of the present disclosure may include an expansion section 62B and first and second narrowing sections 64B and 66B disposed on opposite sides of the expansion section, wherein a fluid flow sectional area of the expansion section 62B may be greater than a fluid flow sectional area of each of the first and second narrowing sections 64B and 66B. Also, the central axis of the first narrowed portion 64B is offset from the central axis of the second narrowed portion 66B. In the non-orbiting scroll according to the second embodiment of the present disclosure, since the central axis of the first narrowed portion 64B is misaligned with the central axis of the second narrowed portion 66B, the fluid will generate more bypass flow in the back pressure passage 60B, so that the fluid will receive more flow resistance, thereby further improving the stability of the back pressure chamber pressure, and further reducing the risk of the fluid refilling the compression chamber to cause repeated compression, thereby improving the scroll compressor performance. Fig. 4 also shows an alternative embodiment of a partition, which partition 80B may include a through hole 82B to allow fluid flow therethrough and a blocking portion 84B to block fluid flow. The through-hole 82B may be a single through-hole formed in the center of the partition 80B.
Fig. 5 is a sectional view illustrating a non-orbiting scroll of a scroll compressor according to a third embodiment of the present disclosure. The non-orbiting scroll 20C of the scroll compressor according to the third embodiment of the present disclosure has a structure similar to that of the non-orbiting scroll 20A of the scroll compressor according to the first embodiment of the present disclosure described above, except that the structure of the back pressure passage is different, and only the difference will be described in detail below.
The biasing passage 60C of the non-orbiting scroll according to the third embodiment of the present disclosure may include a plurality of expansion sections and a narrowing section disposed at opposite sides of each expansion section, wherein a fluid flow sectional area of the expansion sections may be greater than a fluid flow sectional area of each of the narrowing sections. The fluid is throttled a plurality of times in the back pressure passage 60C so that the fluid experiences a greater flow resistance, thereby further improving the stability of the back pressure chamber pressure and further reducing the risk of the fluid refilling the compression chamber causing repeated compression, thereby improving scroll compressor performance.
In the above-described embodiments, the performance of the scroll compressor is improved by improving the stability of the back pressure chamber pressure and reducing the risk of fluid re-compression due to fluid recharging the compression chamber by using the back pressure passage provided in the non-orbiting scroll. However, it will be appreciated by those skilled in the art that the same object may be achieved by providing a back pressure passage having a secondary throttling effect in the orbiting scroll end plate, i.e., the back pressure passage may extend through the orbiting scroll end plate to communicate with a back pressure chamber formed at one side of the orbiting scroll. Specifically, a back pressure chamber may be formed in a space within main bearing housing 50 and in fluid communication with one of a series of compression chambers via a back pressure passage formed in the orbiting scroll end plate. In addition, although the narrowing section is shown in the exemplary embodiment of the present application to have a uniform cross-sectional shape, it may be understood by those skilled in the art that the narrowing section may also have any other suitable shape, such as a tapered V-shape or the like.
While the present disclosure has been described with reference to exemplary embodiments, it is to be understood that the present disclosure is not limited to the particular embodiments described and illustrated in detail herein, and that various changes may be made to the exemplary embodiments by those skilled in the art without departing from the scope defined by the appended claims. It should also be understood that features of the various embodiments may be combined with each other or may be omitted without departing from the scope of the claims.
Claims (10)
1. A compression mechanism comprising:
a non-orbiting scroll that is an integral component and includes a non-orbiting scroll end plate and a non-orbiting scroll blade that are integrally formed, the non-orbiting scroll blade being formed at a first side of the non-orbiting scroll end plate;
an orbiting scroll including an orbiting scroll end plate and orbiting scroll blades formed on a first side of the orbiting scroll end plate, and the non-orbiting scroll blades and the orbiting scroll blades being engaged with each other to form a series of compression chambers therebetween capable of compressing a fluid; and
a back pressure chamber in fluid communication with one of the series of compression chambers through a back pressure passage to apply a back pressure force that engages the orbiting and non-orbiting scrolls;
characterized in that the back pressure passage includes an expansion section and a narrowing section formed on opposite sides of the expansion section, the fluid flow cross-sectional area of the expansion section being larger than the fluid flow cross-sectional area of each of the narrowing sections.
2. The compression mechanism of claim 1, wherein a central axis of one of the narrowed portions is offset from a central axis of another of the narrowed portions.
3. The compression mechanism of claim 1, wherein the backpressure passage comprises two or more of the expansion sections, and opposing sides of each of the expansion sections are formed with a narrowing section.
4. The compression mechanism as recited in any one of claims 1-3, wherein the backpressure passage is formed in and extends through the non-orbiting scroll end plate, the non-orbiting scroll further comprising a non-orbiting scroll hub formed on a second side of the non-orbiting scroll end plate opposite the first side, the non-orbiting scroll hub comprising a first annular hub and a second annular hub, the backpressure cavity being constituted by a space surrounded by the non-orbiting scroll end plate, the first annular hub, and the second annular hub.
5. The compression mechanism according to claim 4, wherein the back pressure passage includes a first narrowed section opened to the one compression chamber and a second narrowed section opened to the back pressure chamber, opposite sides of the non-orbiting scroll end plate are machined with a first bore hole and a second bore hole communicating with each other, an aperture of the second bore hole is larger than an aperture of the first bore hole and the second bore hole has an end opened to the back pressure chamber, the end is mounted with a partition including a through hole allowing a fluid to flow therethrough and a blocking portion blocking the flow of the fluid, the first narrowed section is formed by the first bore hole, the second narrowed section is formed by the through hole, and the expanded section is formed by a portion of the second bore hole where the partition is not mounted.
6. The compression mechanism of claim 5, wherein the divider is removably mounted to the end of the second bore and includes a plurality of spaced apart through holes or the divider includes a single through hole in its center.
7. The compression mechanism of any one of claims 1-3, wherein the back pressure passage is formed in and extends through the orbiting scroll end plate, the back pressure cavity being formed on a second side of the orbiting scroll end plate opposite the first side.
8. The compression mechanism of any one of claims 1-3, wherein an axial length of the expanded section is greater than an axial length of each of the narrowed sections.
9. The compression mechanism of any one of claims 1-3, wherein each of the constriction sections has the same cross-sectional flow area, the cross-sectional flow area of the expansion section being in the range of 1.1 to 1.5 times the cross-sectional flow area of the constriction section, or,
the constriction sections each have a different cross-sectional fluid flow area, the cross-sectional fluid flow area of the expansion section being in the range of 1.1 to 1.5 times the maximum cross-sectional fluid flow area of the constriction section.
10. A scroll compressor characterized by comprising a compression mechanism according to any one of claims 1 to 9.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202222076401.8U CN218030611U (en) | 2022-08-08 | 2022-08-08 | Compression mechanism and scroll compressor |
| PCT/CN2023/111415 WO2024032534A1 (en) | 2022-08-08 | 2023-08-07 | Compression mechanism and scroll compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202222076401.8U CN218030611U (en) | 2022-08-08 | 2022-08-08 | Compression mechanism and scroll compressor |
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| CN218030611U true CN218030611U (en) | 2022-12-13 |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2024032534A1 (en) * | 2022-08-08 | 2024-02-15 | 谷轮环境科技（苏州）有限公司 | Compression mechanism and scroll compressor |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2024032534A1 (en) * | 2022-08-08 | 2024-02-15 | 谷轮环境科技（苏州）有限公司 | Compression mechanism and scroll compressor |
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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 |