CN212643042U

CN212643042U - Compression mechanism and scroll compressor comprising same

Info

Publication number: CN212643042U
Application number: CN202021265968.4U
Authority: CN
Inventors: 胡小伟; 倪凌枫
Original assignee: Emerson Climate Technologies Suzhou Co Ltd
Current assignee: Copeland Suzhou Co Ltd
Priority date: 2020-07-02
Filing date: 2020-07-02
Publication date: 2021-03-02
Anticipated expiration: 2030-07-02

Abstract

The application relates to a compression mechanism for a scroll compressor, which comprises an orbiting scroll part and a non-orbiting scroll part. The orbiting scroll member includes an orbiting scroll end plate and an orbiting scroll blade extending from one side of the driven scroll end plate.The non-orbiting scroll member includes a non-orbiting scroll end plate, a non-orbiting scroll blade, a compression region, and an outer peripheral wall. The non-orbiting scroll blade extends from one side of the non-orbiting scroll end plate. In the compression region, the non-orbiting and orbiting scroll blades engage to form a series of compression chambers for compressing a working fluid. The outer peripheral wall is located radially outward of the compression region and has a thrust surface in sliding contact with the orbiting scroll end plate. The outer radial dimension Ro of the thrust surface is less than or equal to the radius R of the movable scroll end plate_{Movable part}And the radius of rotation R_{Wound around}The difference of (a). The application also relates to a scroll compressor comprising the compression mechanism.

Description

Compression mechanism and scroll compressor comprising same

Technical Field

The present application relates to a compression mechanism for a scroll compressor and a 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. Scroll compressors include a non-orbiting scroll member and an orbiting scroll member orbiting in translation relative to the non-orbiting scroll member to compress a working fluid. The non-orbiting and orbiting scroll members have thrust surfaces in sliding contact with respect to each other during operation of the scroll compressor.

Typically, the thrust surface will be designed to have a sufficiently large area to provide adequate support.

However, the large area of the thrust surfaces may result in insufficient lubrication between the thrust surfaces, particularly under heavy load conditions. Insufficient lubrication can result in localized wear of the thrust surfaces and even failure of the scroll components, affecting the performance and reliability of the compressor.

As the end plate of the orbiting scroll member overturns, the contact point between the thrust surfaces is located farther from the compression chamber, creating a larger wedge that is not conducive to load bearing and lubrication, resulting in wear (scuffing) problems.

SUMMERY OF THE UTILITY MODEL

An object of the present disclosure is to provide a scroll compressor capable of alleviating a wear problem of a thrust surface of a scroll member.

According to one aspect of the present disclosure, a compression mechanism for a scroll compressor is provided that includes an orbiting scroll member and a non-orbiting scroll member. The orbiting scroll part including an orbiting scrollAnd an orbiting scroll blade extending from one side of the end plate and the driven scroll end plate. The non-orbiting scroll member includes a non-orbiting scroll end plate, a non-orbiting scroll blade, a compression region, and an outer peripheral wall. The non-orbiting scroll blade extends from one side of the non-orbiting scroll end plate. In the compression region, the non-orbiting and orbiting scroll blades engage to form a series of compression chambers for compressing a working fluid. The outer peripheral wall is located radially outward of the compression region and has a thrust surface in sliding contact with the orbiting scroll end plate. The outer radial dimension Ro of the thrust surface is less than or equal to the radius R of the movable scroll end plate_{Movable part}And the radius of rotation R_{Wound around}The difference of (a).

According to the non-orbiting scroll member of the present disclosure, the thrust surface is always in sliding contact with the orbiting scroll end plate during operation of the scroll compressor. The area of the thrust surface of the non-orbiting scroll member of the present disclosure is greatly reduced compared to that of the conventional non-orbiting scroll member, and thus it is easy to supply sufficient lubricating oil to the thrust surface, and thus it is possible to significantly improve the lubrication problem of the thrust surface. Further, since the outer edge of the thrust surface of the non-orbiting scroll member according to the present disclosure is offset toward the central axis, the bearing and lubrication problems of the wedge area can be improved when the orbiting scroll member is overturned.

In some examples, the outer peripheral wall is provided with a thrust portion extending axially from an end surface thereof, and a top surface of the thrust portion constitutes the thrust surface.

In some examples, the thrust surface has an outer edge that is non-circular in shape.

In some examples, the compression region includes a low pressure compression region at and adjacent an air inlet of the compression mechanism, and at least a portion of the thrust surface adjacent the low pressure compression region has a constant minimum width. Since the compression pockets formed in the low pressure compression region have a low pressure (equal to or slightly greater than the suction pressure), the thrust portions adjacent the low pressure compression region may have reduced strength requirements. Accordingly, the portion of the thrust surface adjacent to the low pressure compression region may have a smaller width, whereby the overall area of the thrust surface may be further reduced and lubrication may be further improved.

In some examples, the constant width is equal to a thickness of the non-orbiting scroll blade.

In some examples, the thrust surface extends 360 degrees in a circumferential direction.

In some examples, the thrust portion has an extension height in a range of 0.1mm to 2.0 mm.

According to another aspect of the present disclosure, there is also provided a scroll compressor. The scroll compressor comprises the fixed scroll component.

In the scroll compressor according to the present disclosure, since the above-described non-orbiting scroll member is included, the same advantages as those of the above-described non-orbiting scroll member are provided.

In some examples, the non-orbiting scroll member is housed in a housing that also houses a motor in a compressed discharge environment.

In some examples, the orbiting scroll member is configured to float axially relative to the non-orbiting scroll member.

Further areas of applicability of the present invention 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 invention, are intended for purposes of illustration only and are not intended to limit the invention.

Drawings

Features and advantages of one or more embodiments of the present invention will become more readily understood from the following description with reference to the accompanying drawings, in which:

FIG. 1 is a schematic perspective cutaway view of a scroll compressor according to an embodiment of the present disclosure;

FIG. 2 is an enlarged partial schematic view of the scroll compressor of FIG. 1;

FIG. 3 is a plan view of the scroll blade side of the non-orbiting scroll member of the scroll compressor of FIG. 1;

FIG. 4 is an enlarged, fragmentary schematic view of the scroll compressor of FIG. 1;

FIG. 5A is a schematic view illustrating a thrust surface of a non-orbiting scroll member according to the present disclosure;

FIG. 5B is a schematic view showing a thrust surface of a non-orbiting scroll member of a comparative example;

FIG. 6A is an enlarged, fragmentary schematic view of an orbiting scroll member of a scroll compressor according to the present disclosure as it is being overturned; and

fig. 6B is a partially enlarged schematic view of the orbiting scroll member of the scroll compressor of the comparative example when it is overturned.

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 general structure of the scroll compressor 10 is described below with reference to FIG. 1. As shown, the scroll compressor 10 includes a housing 11, a compression mechanism CM, a motor 16, a rotary shaft (which may also be referred to as a drive shaft or crankshaft) 14, and a main bearing housing 15.

The housing 11 forms a closed space in which the compression mechanism CM, the motor 16, the rotary shaft 14, and the main bearing housing 15 are accommodated.

An intake pipe 12 for introducing a working fluid having an intake pressure into the housing 11 and an exhaust pipe 13 for discharging the working fluid having a discharge pressure compressed by the compression mechanism CM out of the housing 11 are provided on the housing 11. The intake pipe 12 is connected to an intake port 112 of the compression mechanism CM to introduce a working fluid having a suction pressure into a low-pressure chamber of the compression mechanism CM. The high-pressure working fluid discharged from the exhaust port 111 of the compression mechanism CM is discharged via the exhaust pipe 13.

In the illustrated example, the motor 16 is in a high temperature, high pressure environment of compressed working fluid. Accordingly, the illustrated scroll compressor is also referred to as a high-pressure side compressor. In addition, in the high-pressure side compressor of the present disclosure, the orbiting scroll part may be provided to be axially floatable to achieve axial flexibility of the compression mechanism. For example, a back pressure chamber is formed between the orbiting scroll member and the main bearing housing, and fluid in the back pressure chamber applies an upward axial force to the orbiting scroll member to urge the orbiting scroll member toward the non-orbiting scroll member. However, it is to be understood that the present invention is not limited to the specific examples shown in the drawings, and may be applied to, for example, a low-pressure side compressor, that is, a motor in a low-temperature and low-pressure environment with a working fluid sucked therein.

Referring to fig. 2, compression mechanism CM includes a non-orbiting scroll member 100 connected or fixed to shell 11 and/or main bearing housing 15 and an orbiting scroll member 200 supported by main bearing housing 15. The motor 16 is configured to rotate the rotary shaft 14, and then the rotary shaft 14 drives the orbiting scroll member 200 to orbit relative to the non-orbiting scroll member 100 (i.e., the central axis of the orbiting scroll moves around the central axis of the non-orbiting scroll, but the orbiting scroll does not rotate around the central axis thereof) to compress the working fluid.

The non-orbiting scroll member 100 includes a non-orbiting scroll end plate 110, a non-orbiting scroll blade 120 extending from one side of the non-orbiting scroll end plate 110, and an outer peripheral wall 130 at a radially outer side of the non-orbiting scroll blade 120. An exhaust port 111 is provided at substantially the center of the non-orbiting scroll end plate 110 to discharge the compressed high-temperature and high-pressure working fluid out of the compression mechanism CM.

Orbiting scroll member 200 includes an orbiting scroll end plate 210, an orbiting scroll blade 220 extending from one side of the orbiting scroll end plate 210, and a hub 230 extending from the other side of the driven scroll end plate 210. The non-orbiting scroll blade 120 and the orbiting scroll blade 220 can be engaged with each other such that a series of compression chambers having a gradually decreasing volume moving from a radially outer side to a radially inner side are formed between the non-orbiting scroll blade 120 and the orbiting scroll blade 220 when the scroll compressor is operated, thereby achieving compression of the working fluid. The boss 230 is engaged with an eccentric crank pin of the rotary shaft 14 and is driven by the eccentric crank pin.

A non-orbiting scroll member 100 according to an embodiment of the present application will be described in detail with reference to fig. 3 and 4.

As shown in FIG. 3, non-orbiting scroll blade 120 is spiral in shape and defines a spiral compression zone 140 from inlet port 112 to outlet port 111. In compression region 140, non-orbiting scroll blade 120 engages orbiting scroll blade 220 to form a series of compression pockets moving from the radially outer side toward the radially inner side. The portion of compression region 140 at and adjacent to air inlet 112 may be referred to as a low pressure compression region.

Referring to fig. 2 and 3, the non-orbiting scroll member 100 includes an outer peripheral wall 130 located radially outward of a compression zone 140. Outer peripheral wall 130 has an end surface 133 facing orbiting scroll end plate 210, a flange portion 137 for attachment located radially outward of end surface 133, and a thrust portion 150 supported on orbiting scroll end plate 210.

The thrust portion 150 extends in the axial direction (downward in fig. 2) from the end surface 133. The axial height h of the thrust portion 150 may be in the range of 0.1mm to 2.0mm, as shown in fig. 4. It should be understood that the axial height h of the thrust portion 150 may vary depending on the operating conditions of the scroll compressor 10, the configuration of the compression mechanism CM, etc.

Thrust portion 150 has a top surface 152 supported by orbiting scroll end plate 210. When scroll compressor 10 is in operation, orbiting scroll end plate 210 slides relative to its top surface 152 while supporting thrust feature 150. Thus, the top surface 152 of the thrust portion 150 forms a thrust surface S.

The "thrust portion of the non-orbiting scroll member" as described herein includes the outer radial portion of the non-orbiting scroll blades (i.e., the outer radial portion immediately adjacent to compression region 140), as shown in FIG. 3. In other words, a portion of the "thrust portion of the non-orbiting scroll member" described herein serves as a non-orbiting scroll blade. As used herein, a "thrust surface" refers to a surface of a thrust portion that is supported on an orbiting scroll end plate and subject to sliding friction.

The thrust portion 150 is located radially outward of the radially outermost (360 degree) portion of the compression zone 140. As shown by the hatching in fig. 3, the thrust surface S extends 360 degrees in the circumferential direction. In other words, top face 152 is in sliding contact with orbiting scroll end plate 210 in the circumferential direction 360 degrees, thereby forming a thrust surface S extending 360 degrees in the circumferential direction.

However, in an example not shown, the thrust surface S may also not extend 360 degrees in the circumferential direction. For example, top surface 152 of thrust block 150 has a notch at the inlet that does not slidingly contact orbiting scroll end plate 210.

The thrust surface S of the thrust portion 150 includes an inner edge having an inner radial dimension Ri and an outer edge having an outer radial dimension Ro. That is, the width of the thrust surface S is the difference Ro-Ri between the outer radial dimension Ro and the inner radial dimension Ri.

The inner radial dimension Ri of the thrust surface S may be determined by the helical profile of the non-orbiting scroll blade 120. Thus, the inner radial dimension Ri of the thrust surface S may vary along the circumferential direction. Similarly, the outer radial dimension Ro of the thrust surface S may also vary in the circumferential direction. In this case, the thrust surface S has a non-circular shape extending along the compression region 140. Thus, the width of the thrust surface S is variable along the circumferential direction.

In the example shown in fig. 3, the width of the thrust surface S on both sides of the air inlet 112 is different. The portion of the thrust surface S adjacent the low pressure compression region of the compression region 140 has a substantially constant width. The constant width is substantially equal to the thickness of non-orbiting scroll blade 120. The thrust surface S has a greater width on the side opposite the low pressure compression region of the compression region 140 due to, for example, the oil groove 132 thereon. It will be appreciated that the thrust surface S may have a substantially constant width in the circumferential direction throughout, in the absence of external factors.

To ensure stable support, the width of the thrust surface S may be equal to or greater than the thickness of the non-orbiting scroll blade 120. That is, the minimum width of the thrust surface S may be the thickness of the non-orbiting scroll blade 120. For example, the portion of the thrust surface S adjacent the low pressure compression region has a minimum width. Since the compression chamber formed in the low pressure compression region is at a low pressure (equal to or slightly greater than the suction pressure), the strength requirement of the portion of the thrust surface S adjacent to the low pressure compression region is low and can therefore have a minimum width. It should be understood that the width of the thrust surface S may also be less than the thickness of the non-orbiting scroll blade 120, provided that the bearing and strength requirements are met.

In accordance with the non-orbiting scroll member 100 of the present disclosure, the outer radial dimension Ro of the thrust surface S is equal to or less than the radius R of the orbiting scroll end plate 210_{Movable part}And the radius of rotation R_{Wound around}A difference of (i.e., Ro ≦ R_{Movable part}-R_{Wound around}. In other words, the maximum outer radial dimension Rmax of the thrust surface S may be equal to the radius R of the orbiting scroll end plate 210 at any portion in the circumferential direction_{Movable part}And the radius of rotation R_{Wound around}I.e. Rmax-R_{Movable part}-R_{Wound around}. In this way, the thrust surface S is always in sliding contact with the orbiting scroll end plate 210 during operation of the compressor. I.e. the thrust surface S as a whole is an effective bearing surface.

FIG. 5A is a schematic view illustrating a thrust surface of a non-orbiting scroll member according to the present disclosure; fig. 5B is a schematic view showing a thrust surface of a non-orbiting scroll member of a comparative example. As shown in FIG. 5A, the non-orbiting scroll member 100 according to the present disclosure has a thrust surface S (shown in phantom). The thrust surface S is in sliding contact with the orbiting scroll end plate at all times during operation of the scroll compressor. As shown in fig. 5B. The non-orbiting scroll member 100 'of the comparative example has a thrust surface S' (shown in phantom). The thrust surface S' includes a first portion that is in sliding contact with the orbiting scroll end plate at all times during operation of the scroll compressor and a second portion that is in intermittent sliding contact with the orbiting scroll end plate. As can be seen by comparing fig. 5A and 5B, the thrust surface S of the non-orbiting scroll member of the present disclosure corresponds to the first portion of the thrust surface S' of the comparative example. Therefore, the area of the thrust surface S' of the comparative example is larger than that of the thrust surface S of the present disclosure, specifically, the area of the second portion. In other words, the area of the thrust surface S is reduced relative to the area of the thrust surface S', for example by 35% to 40%.

As described above, the thrust surface S of the non-orbiting scroll member according to the present disclosure has a significantly reduced bearing area while effectively securing a bearing force. The thrust surface S with a reduced area may reduce the lubrication requirements, i.e. ease of solving the lubrication problem, especially in heavy load conditions. Therefore, the failure probability of the scroll part can be reduced, and the overall performance and reliability of the compressor can be improved.

Further, the non-orbiting scroll member 100 according to the present disclosure can significantly improve its lubrication problem only by changing the structure (outer radial dimension) of the thrust surface without providing an additional oil supply structure or the like. Accordingly, the non-orbiting scroll member 100 is simple in structure, reliable in operation, and easy to machine.

Further, the non-orbiting scroll member 100 according to the present disclosure may also solve or mitigate lubrication and wear problems when the orbiting scroll member overturns, as will be described below with reference to fig. 6A and 6B. FIG. 6A is an enlarged, fragmentary schematic view of an orbiting scroll member of a scroll compressor according to the present disclosure as it is being overturned; fig. 6B is a partially enlarged schematic view of the orbiting scroll member of the scroll compressor of the comparative example when it is overturned.

As shown in fig. 6A, when the orbiting scroll end plate 210 of the orbiting scroll member is overturned, the thrust surface S of the non-orbiting scroll member 100 comes into point contact with the orbiting scroll end plate 210 at a contact point P, thereby forming a wedge W. The contact point P is defined by the outer edge of the thrust surface S.

As shown in fig. 6B, when the orbiting scroll end plate 210 'of the orbiting scroll member is overturned, the thrust surface S' of the non-orbiting scroll member 100 'comes into point contact with the orbiting scroll end plate 210' at a contact point P ', thereby forming a wedge area W'. Contact point P 'is defined by the outer edge of the thrust surface of orbiting scroll end plate 210'.

The contact point P in fig. 6A is much closer to the central axis than the contact point P' in fig. 6B. Thus, wedge W in FIG. 6A is much smaller than wedge W' in FIG. 6B. In contrast, for the non-orbiting scroll member 100 shown in FIG. 6A, it is advantageous to create oil pressure in the wedge W to assist in load bearing and lubrication, thereby improving wear (scuffing) issues.

In addition, in the comparative example, when the orbiting scroll member overturns, the thrust surface of the orbiting scroll member defining the wedge W 'moves away from the contact point P' (i.e., moves to the right in fig. 6B), which is disadvantageous in that oil pressure is formed in the wedge to assist in bearing and lubrication, resulting in wear. In contrast, in the example of the present disclosure as shown in fig. 6A, since the groove is formed at the radially outer side of the protruding thrust portion 150 and the contact point P is determined by the outer edge of the thrust surface S, the thrust surface of the orbiting scroll member defining the wedge W may move toward the contact point (i.e., to the left in fig. 6A) when the orbiting scroll member topples, which facilitates the formation of oil pressure at the wedge to assist in bearing and lubrication, thereby improving wear.

While the present invention has been described with reference to exemplary embodiments, it is to be understood that the invention is not limited to the specific embodiments described and illustrated in detail herein. Various modifications may be made to the exemplary embodiments by those skilled in the art without departing from the scope defined by the claims. For example, the outer peripheral wall 130 of the non-orbiting scroll member 100 may omit the flange portion 137 and have only the thrust portion 150. 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

1. A compression mechanism for a scroll compressor, the compression mechanism comprising an orbiting scroll member and a non-orbiting scroll member,

the orbiting scroll part includes:

an orbiting scroll end plate; and

an orbiting scroll blade extending from one side of the orbiting scroll end plate,

the non-orbiting scroll member includes:

a fixed scroll end plate;

a non-orbiting scroll blade extending from one side of the non-orbiting scroll end plate;

a compression region in which the non-orbiting scroll blade engages with the orbiting scroll blade to form a series of compression chambers for compressing a working fluid; and

an outer peripheral wall located radially outward of the compression region and having a thrust surface in sliding contact with the orbiting scroll end plate,

characterised in that the thrust surface has an outer radial dimension Ro is less than or equal to radius R of movable scroll end plate_{Movable part}And the radius of rotation R_{Wound around}The difference of (a).

2. The compression mechanism of claim 1, wherein the outer peripheral wall is provided with a thrust portion extending axially from an end surface thereof, a top surface of the thrust portion constituting the thrust surface.

3. The compression mechanism of claim 2, wherein the thrust surface has an outer edge with a non-circular shape.

4. The compression mechanism of claim 3, wherein the compression region comprises a low pressure compression region at and adjacent to an air inlet of the compression mechanism, and at least a portion of the thrust surface adjacent to the low pressure compression region has a constant minimum width.

5. The compression mechanism of claim 4, wherein the constant minimum width is equal to a thickness of the non-orbiting scroll vane.

6. A compression mechanism according to any one of claims 1 to 5, wherein the thrust surface extends 360 degrees in a circumferential direction.

7. The compression mechanism of any one of claims 2 to 5, wherein the extension height of the thrust portion is in the range of 0.1mm to 2.0 mm.

8. A scroll compressor comprising the compression mechanism according to any one of claims 1 to 7.

9. The scroll compressor of claim 8, wherein the compression mechanism is housed in a housing, and further wherein a motor is housed in the housing, the motor being in a compressed discharge environment.

10. The scroll compressor of claim 8 or 9, wherein the orbiting scroll member is configured to float axially relative to the non-orbiting scroll member.