CN215949828U

CN215949828U - Thrust structure of compressor and compressor

Info

Publication number: CN215949828U
Application number: CN202122304392.9U
Authority: CN
Inventors: 刘利涛; 李斌
Original assignee: Emerson Climate Technologies Suzhou Co Ltd
Current assignee: Copeland Suzhou Co Ltd
Priority date: 2021-09-23
Filing date: 2021-09-23
Publication date: 2022-03-04
Anticipated expiration: 2031-09-23

Abstract

The present invention relates to a thrust structure of a compressor and a compressor, and in one aspect, provides a thrust structure of a compressor including a drive shaft, the thrust structure including a thrust surface for axially supporting the drive shaft, and an insert attached to the drive shaft to integrally rotate with the drive shaft, the insert being arranged between the drive shaft and the thrust surface and in contact with the thrust surface such that the drive shaft is axially thrust by the thrust surface via the insert. The abrasion to the thrust surface can be effectively reduced through the thrust structure.

Description

Thrust structure of compressor and compressor

Technical Field

The utility model relates to a thrust structure of a compressor and the compressor.

Background

The statements in this section merely provide background information related to the present disclosure and may not constitute prior art.

In a compressor, a scroll compressor is taken as an example, and a scroll compressor generally includes a compression mechanism including a fixed scroll member and a movable scroll member. In a conventional scroll compressor, a motor assembly and a compressor assembly are generally provided inside a casing. The compressor unit is operated by a driving force of the motor unit, and absorbs and compresses a refrigerant, and then discharges the refrigerant. In order to lubricate the respective parts, particularly the compression parts, in the compressor, a lubricating oil supply device, such as an oil pump or an oil fork, etc., is provided at the lower end of the driving shaft, and lubricating oil from the lubricating oil supply device is pumped to the upper end of the driving shaft through the central hole of the driving shaft to be discharged to lubricate the respective parts.

In the above-described lubricating oil supply device, taking the oil pump as an example, the lower end of the drive shaft is attached to the oil pump to drive the oil pump, and the drive shaft is axially thrust by the thrust washer by being supported on the oil pump housing by the thrust washer. Thus, the oil pump is driven by the drive shaft to rotate in the internal cavity formed by the oil pump housing for pumping the lubricating oil. The driveshaft and the thrust washer are generally made of metal, and the driveshaft and the thrust washer initially come into surface contact with each other at a plurality of rough points (contact surfaces are generally uneven, microscopically convexo-concave, and particularly, in the case where roughness is high), which cause friction and wear. In particular, in the case of high contact pressures (axial loads), the rough spots are plastically deformed and finally welded (cold-welded) together. As the drive shaft and thrust washer continue to slide, the weld asperities break, resulting in a cavity on one surface and a depression on the other surface. At the same time, the abraded particles separate and rub against the surface, thereby exacerbating the abrasion of the surface.

Accordingly, it is desirable to provide a thrust structure that reduces wear of the thrust surface.

SUMMERY OF THE UTILITY MODEL

It is an object of the present invention to provide a thrust structure capable of reducing wear by providing an insert between the drive shaft and the thrust surface.

The utility model provides a thrust structure of a compressor, the compressor including a drive shaft, the thrust structure including a thrust surface for axially supporting the drive shaft and an insert attached to the drive shaft to integrally rotate with the drive shaft, the insert being arranged between the drive shaft and the thrust surface and in contact with the thrust surface such that the drive shaft is axially thrust by the thrust surface via the insert.

Preferably, the insert and the drive shaft are attached together by a form-fit and/or interference fit.

Preferably, the form-fitting manner is implemented as:

providing a square recess at one of the insert and the shaft end of the drive shaft and a square protrusion at the other adapted to form fit with the square recess; or

Providing a truncated circular recess at one of the insert and a shaft end of the drive shaft and a truncated circular protrusion at the other adapted to form fit with the truncated circular recess; or

A circular recess having one or more radial extensions is provided at one of the insert and the axial end of the drive shaft and a circular protrusion having one or more radial extensions adapted to form fit with the circular recess is provided at the other.

Preferably, in the case where the insert and the drive shaft are attached together by the interference fit, a circular recess is provided at one of the axial ends of the insert and the drive shaft and a circular protrusion adapted to be interference fitted with the circular recess is provided at the other.

Preferably, the insert is an engineered plastic part.

Preferably, the insert has a hardness between that of the drive shaft and that of the thrust surface.

Preferably, the insert has a hardness substantially the same as the hardness of the thrust surface.

Preferably, the insert includes a radially extending flange portion including a first surface facing the axial end of the drive shaft and a second surface opposite the first surface, the second surface being in contact with the thrust surface.

The utility model also provides a compressor, which comprises the thrust structure.

Preferably, the compressor includes an oil pumping mechanism including a pump member attached to a bottom end of the drive shaft and including a shaft portion extending axially from a flange portion of the insert, the pump member being attached to the shaft portion so as to be driven by the drive shaft via the insert.

Preferably, the oil pumping mechanism comprises a housing defining an inner space of the oil pumping mechanism, and an upper surface of the housing facing the insert serves as the thrust surface, or a spacer is provided between the housing and the insert and provides the thrust surface.

Preferably, the flange portion of the insert extends radially beyond the outer periphery of the drive shaft.

Preferably, a gap is provided between a first surface of the flange portion of the insert facing the bottom end of the drive shaft and the bottom end of the drive shaft.

Preferably, the gap is greater than 0.5 mm.

The thrust structure of the present invention is constructed by providing an insert between the driveshaft and the thrust surface, the insert being attached to the driveshaft in a circumferentially constrained, non-rotational manner to rotate integrally with the driveshaft, and the insert being in contact with the thrust surface such that the driveshaft is axially thrust by the thrust surface via the insert. The above-described construction of the present application creates a transition in hardness between the driveshaft and the thrust surface such that wear to the thrust surface is reduced. Meanwhile, the hardness is adjustable, only the hardness of the insert is required to be adjusted, and the hardness of the thrust surface or the thrust washer is not required to be changed, so that the thrust structure is easily compatible with the existing thrust structure, the cost is reduced, and the applicability is wider.

Drawings

The 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 longitudinal sectional view of a scroll compressor including a thrust feature according to the present invention;

FIG. 2 is an enlarged view of the thrust feature at position A in the scroll compressor shown in FIG. 1;

FIG. 3 is an exploded perspective view of a thrust feature in the scroll compressor shown in FIG. 1;

FIG. 4 is an exploded perspective view of an insert and a partial drive shaft of a thrust feature according to one embodiment of the present invention;

FIG. 5 is an exploded perspective view of an insert and a partial drive shaft of a thrust feature according to another embodiment of the present invention;

FIG. 6 is an exploded perspective view of an insert and a partial drive shaft of a thrust feature according to yet another embodiment of the present invention; and

fig. 7 is an assembled state view of an insert of a thrust structure and a part of a drive shaft according to an embodiment of the present invention.

Detailed Description

The following description of various embodiments of the utility model is merely exemplary in nature and is in no way intended to limit the utility model, its application, or uses. The same reference numerals are used to designate the same components in the respective drawings, and thus the configurations of the same components will not be described repeatedly. The dimensional relationships of the various configurations in the drawings are merely exemplary and do not represent actual dimensional relationships.

The general construction and operating principle of the scroll compressor will first be described with reference to fig. 1. As shown in fig. 1, a scroll compressor 100 (hereinafter sometimes referred to as a compressor) generally includes a housing 110, a top cover 112 disposed at one end of the housing 110, a bottom cover 114 disposed at the other end of the housing 110, and a partition 116 disposed between the top cover 112 and the housing 110 to partition an internal space of the compressor into a high pressure side and a low pressure side. The space between the diaphragm 116 and the top cover 112 constitutes a high pressure side, at which a discharge connection (not shown) for discharging compressed fluid is provided. And the space between the partition 116, the housing 110, and the bottom cover 114 constitutes a low pressure side. A motor 120 composed of a stator and a rotor is provided in the housing 110. A drive shaft 130 is provided in the rotor to drive a compression mechanism consisting of a non-orbiting scroll member 150 and an orbiting scroll member 160. Orbiting scroll member 160 includes an end plate 164, a hub 162 formed on one side of the end plate, and a spiral vane 166 formed on the other side of the end plate. The non-orbiting scroll member 150 includes an end plate 154, a spiral vane 156 formed at one side of the end plate, and an exhaust port 152 formed at a substantially central position of the end plate. A series of compression chambers, the volume of which gradually decreases from the radially outer side to the radially inner side, are formed between the spiral vane 156 of the non-orbiting scroll 150 and the spiral vane 166 of the orbiting scroll 160.

Orbiting scroll member 160 will be rotated in translation relative to non-orbiting scroll member 150 (i.e., the axis of orbiting scroll member 160 rotates about the axis of non-orbiting scroll member 150, but orbiting scroll member 160 does not itself rotate about its axis) by the actuation of motor 120 to effect compression of the fluid. The fluid compressed by the non-orbiting scroll part 150 and the orbiting scroll part 160 is discharged to a high pressure side through the discharge port 152.

The lubrication process of each component in the compressor will be described below. In the example of the scroll compressor shown in fig. 1, lubricating oil is stored in the bottom of the compressor housing. Accordingly, a passage extending substantially in the axial direction thereof, i.e., a center hole 136 formed at the lower end of the drive shaft 130 and an eccentric hole 134 extending upward from the center hole 136 to the end surface of the eccentric crank pin 132, is formed in the drive shaft 130. The end of the central bore 136 is submerged in or otherwise supplied with lubricant at the bottom of the compressor housing. In one example, a lubrication supply device, which is shown as an oil pump in FIG. 1, may be provided in or near the central bore 136, or may be an oil fork or the like. During operation of the compressor, one end of the central bore 136 is supplied with lubricating oil by the lubricating oil supply, and the lubricating oil entering the central bore 136 is pumped or thrown into the eccentric bore 134 by centrifugal force during rotation of the drive shaft 130 and flows up the eccentric bore 134 to the end face of the eccentric crank pin 132. Lubricating oil is discharged from the end face of eccentric crank pin 132, and a portion of the lubricating oil is agitated by boss 162 to move up to the lower side of end plate 164 of orbiting scroll member 160 and spread over the thrust surface between orbiting scroll member 160 and the main bearing housing supporting orbiting scroll member 160 as orbiting scroll member 160 rotates in translation. During operation of the compressor, the lubricating oil supplied to various moving parts in the compressor is thrown and splashed to form droplets or mist. These lubricant droplets or mist will be mixed in the working fluid (or refrigerant). The working fluid mixed with lubricant droplets is then drawn into the compression chambers between non-orbiting scroll member 150 and orbiting scroll member 160 to effect lubrication, sealing and cooling of the interior of these scroll members. This lubrication between the orbiting and non-orbiting scroll members is commonly referred to as oil mist lubrication.

Next, a thrust structure in the lubricating oil supply arrangement of the present application will be described with reference to fig. 1 to 7.

Referring to fig. 1 to 3, fig. 1 is a longitudinal sectional view of a scroll compressor including a thrust structure according to the present invention; FIG. 2 is an enlarged view of the thrust feature at position A in the scroll compressor shown in FIG. 1; FIG. 3 is an exploded perspective view of the thrust feature of the scroll compressor shown in FIG. 1. Although the compressor of the present application is exemplified by a scroll compressor, the thrust structure of the present application is also applicable to other types of compressors including an axial thrust structure.

The thrust structure of the compressor includes a thrust surface S for axially supporting the drive shaft 130, and an insert 140 attached to the drive shaft to integrally rotate with the drive shaft, the insert 140 being disposed between the drive shaft 130 and the thrust surface S and in contact with the thrust surface S such that the drive shaft is axially thrust by the thrust surface via the insert.

In contrast to the prior art, the thrust structure of the present application prevents the insert and the driveshaft from rotating relative to each other in the circumferential direction while being in contact with and axially thrust by the thrust surface by providing an insert (e.g., an insert pin) between the driveshaft and the thrust surface, the insert being attached to the driveshaft in a circumferentially restrained, non-rotating manner to rotate integrally with the driveshaft. Since the wear of the thrust surface is related to the difference in hardness between the two contact parts, the prior art drive shaft and thrust surface (thrust washer) are typically made of metal and are mass produced, making it difficult to adjust the difference in hardness between the two parts, the above described structure of the present application provides a transition in hardness between the drive shaft and thrust surface, thereby reducing wear to the thrust surface. Meanwhile, only the hardness of the insert needs to be adjusted, and the hardness of the thrust surface does not need to be changed, so that the thrust structure is easily compatible with the existing thrust structure, the cost is reduced, and the applicability is wider.

The compressor further includes an oil pumping mechanism (exemplified by an oil pump) including a pump member 171, the insert 140 being attached to a bottom end of the drive shaft 130 and including a shaft portion 144 axially extending from the flange portion 142 of the insert 140, the pump member 171 being attached to the shaft portion 144 so as to be driven by the drive shaft via the insert. The oil pumping mechanism further comprises a housing 175 defining an inner space of the oil pumping mechanism, a spacer 170 is provided between the housing 175 and the insert 140 and the spacer 170 provides a thrust surface S.

In one aspect of an embodiment, the upper surface of the housing 175 facing the insert (i.e., without the provision of a washer) may also serve as a thrust surface. In the figures, the housing 175 includes a split bottom cap 173 and cylinder 172, and in other aspects of the embodiments, the thrust surface may be provided by the bottom cap or the cylinder itself. Of course, the bottom cover 173 and the cylinder 172 may be integrated.

Next, the attachment of the insert of the thrust structure to the drive shaft is described with reference to fig. 4 to 6, fig. 4 being an exploded perspective view of the insert of the thrust structure and a part of the drive shaft according to an embodiment of the utility model; FIG. 5 is an exploded perspective view of an insert and a partial drive shaft of a thrust feature according to another embodiment of the present invention; fig. 6 is an exploded perspective view of an insert and a partial drive shaft of a thrust structure according to yet another embodiment of the present invention. The insert and the drive shaft may be attached together by a form fit and/or an interference fit.

With reference to fig. 4-6, the insert 140 may include a radially extending flange portion 142, the flange portion 142 including a first surface facing the axial end (bottom end) of the drive shaft 130 and a second surface opposite the first surface for contacting the thrust surface S.

In one embodiment, referring to fig. 4, a circular recess having one radial extension is provided at the bottom end of the drive shaft 130, and a circular protrusion having one radial extension adapted to form fit with the circular recess is provided at the insert 140. Of course, a circular recess could also be provided at the insert, while a corresponding circular protrusion is provided at the bottom end of the drive shaft. One radial extension of the circular recess is shown in the figures to prevent circumferential rotation of the drive shaft and the insert relative to each other, it being understood that the circular recess of the drive shaft may be provided with a plurality of radial extensions, while the circular protrusion of the insert is provided with a corresponding plurality of radial extensions of a form fit.

In another embodiment, referring to fig. 5, a truncated circular recess is provided at the insert 140 and a truncated circular protrusion adapted to form fit with the truncated circular recess is provided at the bottom end of the drive shaft 130. The "cut circle" may be formed by cutting a cylindrical body into a flat surface, for example. Of course, the rounded recess could also be provided at the bottom end of the drive shaft, while the corresponding rounded protrusion is provided at the insert.

In yet another embodiment, referring to fig. 6, a square recess is provided at the bottom end of the drive shaft 130 and a square protrusion adapted to form fit with the square recess is provided at the insert 140. Of course, a square recess could also be provided at the insert, while a corresponding square projection is provided at the bottom end of the drive shaft.

In one aspect according to an embodiment, the insert is attached to the drive shaft by an interference fit, in particular a circular recess is provided at one of the insert and the shaft end of the drive shaft and a circular protrusion adapted to interference fit with the circular recess is provided at the other.

In another aspect according to embodiments, the insert may be an engineered plastic part. The engineering plastic part can replace metal parts, has excellent comprehensive performance, high rigidity, small creep, high mechanical strength, high heat resistance and high electric insulating property, and can be used in harsh chemical and physical environments for a long time.

In one advantageous aspect according to embodiments, the hardness of the insert may be between the hardness of the driveshaft and the hardness of the thrust surface, preferably the hardness of the insert may be less than the hardness of the driveshaft and greater than the hardness of the thrust surface (thrust washer). And/or the hardness of the insert may be approximately the same as the hardness of the thrust surface such that the difference in hardness between the insert and the thrust surface is approximately zero to further reduce wear between the insert and the thrust surface. This allows the insert to be less stiff to accommodate the spacer for ease of handling and reduced cost, as the spacer and drive shaft are typically mass produced. The existing gasket can be produced in a large scale without changing the hardness of the gasket, so that the cost is saved. The difference in hardness between the two (insert and shim, i.e. thrust surface) is reduced, reducing wear.

In another advantageous aspect according to an embodiment, the flange portion 142 of the insert 140 extends radially beyond the outer circumference of the drive shaft. The outer diameter of the radial flange portion of the insert (bearing on the thrust surface S) may be greater than the outer diameter of the drive shaft. This configuration enables an increase in the contact area with the thrust surface, without being limited to the outer diameter dimension of the drive shaft, and thus reduces wear.

In still another advantageous aspect according to an embodiment, referring to fig. 7, fig. 7 is an assembled state view of an insert of a thrust structure and a part of a driving shaft according to an embodiment of the present invention, a gap G may be further provided between a first surface of the flange portion 142 of the insert 140 facing the bottom end of the driving shaft 130 and the bottom end of the driving shaft 130. The gap structure can weaken eccentric wear caused by shaft end inclination of the driving shaft, and the insert can normally contact with the thrust surface, so that the effective contact area is increased, and the limit contact stress is reduced. The size of the gap is not particularly critical and a limit deviation can be obtained by the gap between the shaft and the bearing block, preferably the gap G can be greater than 0.5 mm. The gap can also advantageously be provided at a radially outer circumferential edge position.

While various embodiments and modifications of the present invention have been specifically described above, it will be understood by those skilled in the art that the present invention is not limited to the specific embodiments and modifications described above but may include other various possible combinations and combinations.

Claims

1. A thrust structure of a compressor, the compressor including a drive shaft, the thrust structure including a thrust surface for axially supporting the drive shaft, and an insert attached to the drive shaft to rotate integrally with the drive shaft, characterized in that the insert is arranged between the drive shaft and the thrust surface and is in contact with the thrust surface such that the drive shaft is axially thrust by the thrust surface via the insert.

2. The thrust structure of claim 1, wherein the insert and the drive shaft are attached together by a form fit and/or an interference fit.

3. The thrust structure of claim 2, wherein the form-fitting is implemented as:

4. The thrust structure of claim 2, wherein, with the insert and the drive shaft attached together by the interference fit, a circular recess is provided at one of the axial ends of the insert and the drive shaft and a circular protrusion adapted to interference fit with the circular recess is provided at the other.

5. The thrust structure of any of claims 1 to 4, wherein the insert is an engineered plastic piece.

6. The thrust structure of any of claims 1 to 4, wherein the hardness of the insert is between the hardness of the drive shaft and the hardness of the thrust surface.

7. The thrust structure of any of claims 1 to 4, wherein the hardness of the insert is substantially the same as the hardness of the thrust surface.

8. The thrust structure of any of claims 1 to 4, wherein the insert includes a radially extending flange portion including a first surface facing an axial end of the drive shaft and a second surface opposite the first surface, the second surface being in contact with the thrust surface.

9. A compressor, characterized in that the compressor comprises a thrust structure according to any one of claims 1 to 8.

10. The compressor of claim 9, comprising an oil pumping mechanism including a pump member, the insert being attached to a bottom end of the drive shaft and including a shaft portion extending axially from a flange portion of the insert, the pump member being attached to the shaft portion so as to be driven by the drive shaft via the insert.

11. The compressor of claim 10, wherein:

the oil pumping mechanism includes a housing defining an inner space of the oil pumping mechanism, and

the upper surface of the housing facing the insert serves as the thrust surface, or a spacer is provided between the housing and the insert and provides the thrust surface.

12. The compressor of any one of claims 9 to 11, wherein the flange portion of the insert extends radially beyond the outer periphery of the drive shaft.

13. The compressor of any one of claims 9 to 11, wherein a gap is provided between a first surface of the flange portion of the insert facing the bottom end of the drive shaft and the bottom end of the drive shaft.

14. The compressor of claim 13, wherein the clearance is greater than 0.5 mm.