CN113653645A

CN113653645A - Pump body and compressor

Info

Publication number: CN113653645A
Application number: CN202111117644.5A
Authority: CN
Inventors: 魏琪青; 钟志锋; 高斌
Original assignee: Guangdong Meizhi Compressor Co Ltd; Guangdong Meizhi Precision Manufacturing Co Ltd
Current assignee: Guangdong Meizhi Compressor Co Ltd; Guangdong Meizhi Precision Manufacturing Co Ltd
Priority date: 2021-09-23
Filing date: 2021-09-23
Publication date: 2021-11-16
Also published as: WO2023045270A1

Abstract

The utility model is suitable for a compressor technical field provides a pump body and compressor, this pump body includes bent axle and first bearing, the bent axle has eccentric portion, first bearing is equipped with the shaft hole, the bent axle assembles in the shaft hole, one side of first bearing towards eccentric portion is equipped with first thrust portion, one side of bent axle towards first bearing is equipped with second thrust portion, first thrust portion includes first sclerosis region, the hardness value in first sclerosis region is greater than the hardness value in other regions on the first bearing, second thrust portion includes second sclerosis region, the hardness value in second sclerosis region is greater than the hardness value in other positions on the bent axle, first sclerosis region and second sclerosis region looks butt, the wearability of eccentric portion and first bearing improves, both all difficult wearing and tearing take place, can guarantee the structure of pump body and the reliability of working process; the compressor with the pump body has the advantages that the wear resistance of the eccentric part of the crankshaft and the first bearing is improved, the eccentric part and the first bearing are not easy to wear, and the structure and the working reliability are high.

Description

Pump body and compressor

Technical Field

The application relates to the technical field of compressors, in particular to a pump body and a compressor.

Background

In the compressor, a crankshaft connected to a rotor has an eccentric portion for driving a piston to eccentrically rotate in a cylinder to form a compression chamber with a variable volume in the cylinder. In the axial direction of the crankshaft, two side end faces of the eccentric part are respectively abutted with end faces of the first bearing and the second bearing, namely, the lower end face of the eccentric part is supported by the upper end face of the first bearing, and the two are kept abutted and thrust against each other in the rotating process of the eccentric part. At present, due to the fact that the hardness of a region where the eccentric portion and the first bearing are in mutual thrust is insufficient, mutual abrasion of the eccentric portion and the first bearing is generated in the working process of the compressor, the problem of reliability of abutting between a crankshaft and the first bearing is caused, and then the compressor is caused to fail.

Disclosure of Invention

An object of the embodiment of this application is to provide a pump body, aim at solving among the current compressor because of the not enough technical problem who leads to wearing and tearing seriously each other and arouse the compressor inefficacy between bent axle and the first bearing.

The embodiment of the application is realized in such a way, a pump body comprises a crankshaft and a first bearing, wherein the crankshaft is provided with an eccentric part, the first bearing is provided with a shaft hole, one side of the first bearing, which faces the eccentric part, is provided with a first thrust part, one side of the crankshaft, which faces the first bearing, is provided with a second thrust part, and the crankshaft is assembled in the shaft hole;

the first thrust portion comprises a first hardened region, and the hardness value of the first hardened region is greater than the hardness values of other regions of the first bearing except the first hardened region; the second thrust portion includes a second hardened region having a hardness value greater than a hardness value of a location on the crankshaft other than the second hardened region, the first hardened region and the second hardened region abutting.

In one embodiment, the first hardened zone is a hardened layer having a surface hardness value in the range of 22HRC to 60HRC and an axial depth in the range of 0.05mm to 10 mm; or the first hardening area is a chromium plating layer or a diamond-like coating, the hardness value of the first hardening area ranges from 200HV to 2000HV, and the axial depth of the first hardening area ranges from 0.05 μm to 50 μm.

In one embodiment, the second hardened zone is a hardened layer having a surface hardness value in the range of 22HRC to 60HRC and an axial depth in the range of 0.05mm to 10 mm; or the second hardening area is a chromium coating or a diamond coating, the hardness value of the second hardening area ranges from 200HV to 2000HV, and the axial depth of the second hardening area ranges from 0.05 μm to 50 μm.

In one embodiment, the ratio of the hardness value of the first hardening area to the hardness value of the second hardening area ranges from 0.5 to 3.

In one embodiment, the ratio of the hardness value of the first hardening area to the hardness value of the second hardening area ranges from 0.5 to 1.

In one embodiment, the ratio of the radial width of the first hardened area to the radial width of the second hardened area ranges from 1 to 2, and the projection of the second hardened area on the radial plane of the crankshaft is covered by the projection of the first hardened area on the radial plane.

In one embodiment, the first bearing is further provided with an oil groove, and the oil groove is arranged between the first thrust portion and the crankshaft and communicated with the shaft hole.

In one embodiment, the axial depth of the oil groove ranges from 0.1mm to 15 mm.

In one embodiment, the oil groove is in a continuous ring shape surrounding the shaft hole, and a joint of an outer edge of the oil groove and the end face of the first bearing forms a chamfer or a fillet.

In one embodiment, the outer edge of the sump coincides with the inner edge of the first hardened region.

Another aim at of this application embodiment provides a compressor, including casing, motor to and as above each embodiment said pump body, the motor with the pump body all locates in the casing, the pump body still includes the cylinder, keeping away from of bent axle the one end of first bearing with the rotor of motor is connected, the bent axle passes the cylinder, the eccentric portion is located in the cavity of cylinder.

This application is implemented the pump body and the compressor that provide, its beneficial effect lies in:

according to the pump body provided by the embodiment of the application, the first thrust part of the first bearing comprises the first hardening area, the hardness value of the first hardening area is greater than that of the other areas except the first hardening area on the first bearing, the second thrust part of the eccentric part comprises the second hardening area, the hardness value of the second hardening area is greater than that of the position except the second hardening area on the crankshaft, and the first hardening area is abutted with the second hardening area; the compressor with the pump body has the advantages that the eccentric part of the crankshaft is abutted to the first bearing in the area with high hardness, the eccentric part and the first bearing are not easy to wear, the structural reliability is improved, and the working reliability is improved.

Drawings

In order to more clearly illustrate the technical solutions in the embodiments of the present application, the drawings needed to be used in the embodiments will be briefly described below, and it is obvious that the drawings in the following description are only some embodiments of the present application, and it is obvious for those skilled in the art to obtain other drawings without creative efforts.

FIG. 1 is a schematic structural diagram of a pump body provided in an embodiment of the present application;

FIG. 2 is an enlarged view at A in FIG. 1;

FIG. 3 is a side view of a crankshaft in the pump body shown in FIG. 1;

fig. 4 is a bottom view of a partial structure of the crankshaft in the pump body shown in fig. 1.

FIG. 5 is a top plan view of a first bearing in the pump body of FIG. 1;

FIG. 6 is a side view of a first bearing in the pump body of FIG. 1;

the designations in the figures mean:

100-a pump body;

1-crankshaft, 11-main shaft section, 12-eccentric section, 121-second thrust section, 122-second hardened zone, 13-auxiliary shaft section;

2-first bearing, 20-shaft hole, 21-oil groove, 22-first thrust part, 23-first hardening area;

3-a second bearing; 41-upper silencer, 42-lower silencer; 5-cylinder, 6-piston, 7-slip sheet.

Detailed Description

In order to make the objects, technical solutions and advantages of the present application more apparent, the present application is described in further detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the present application and are not intended to limit the present application.

It will be understood that when an element is referred to as being "secured to" or "disposed on" another element, it can be directly or indirectly secured to or disposed on the other element. When an element is referred to as being "connected to" another element, it can be directly or indirectly connected to the other element. The terms "upper", "lower", "left", "right", and the like, indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are only for convenience of description, but do not indicate or imply that the referred devices or elements must have a specific orientation, be constructed and operated in a specific orientation, and thus, should not be construed as limiting the patent. The terms "first", "second" and "first" are used merely for descriptive purposes and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features. The meaning of "plurality" is two or more unless specifically limited otherwise.

Referring to fig. 1 to 3, in the present embodiment, a pump body 100 is first provided, which includes a crankshaft 1 and a first bearing 2, wherein the crankshaft 1 has an eccentric portion 12, and the first bearing 2 is provided with a shaft hole 20 formed along an axial direction thereof, as shown in fig. 6; the portion of the crankshaft 1 on the side of the eccentric portion 12 is fitted into the shaft hole 20, the first bearing 2 is used to support the crankshaft 1 to rotate about its own central axis, and the eccentric portion 12 abuts against the first bearing 2. Specifically, as shown in fig. 2, a first thrust portion 22 is provided on a side of the first bearing 2 facing the eccentric portion 12, a second thrust portion 121 is provided on a side of the eccentric portion 12 facing the first bearing 2, and the first thrust portion 22 and the second thrust portion 121 are in contact with each other.

Referring to fig. 5 and 6, the first thrust portion 22 includes a first hardened region 23, and a hardness value of the first hardened region 23 is greater than a hardness value of a region of the first bearing 2 other than the first hardened region 23. Referring to fig. 4, the second thrust portion 121 includes a second hardened region 122, and a hardness value of the second hardened region 122 is greater than hardness values of regions of the eccentric portion 12 other than the second hardened region 122. The second hardened region 122 at least partially overlaps the projection of the first hardened region 23 onto the radial plane, i.e. the two at least partially abut each other.

Because the hardness values of the first hardened area 23 and the second hardened area 122 are larger, the wear resistance is better, and therefore, in the process that the eccentric part 12 is in contact with and rubs against the first bearing 2, the wear degree of the eccentric part 12 and the first bearing 2 can be smaller, and the structural reliability of the eccentric part 12 and the first bearing 2 can be further improved.

The pump body 100 that this application embodiment provided, be equipped with the second on the eccentric portion 12 of its bent axle 1 and harden regional 122, be equipped with on the first bearing 2 with the regional 122 looks butt of second hardening, the first hardening region 23 of thrust, the wearability of eccentric portion 12 and first bearing 2 all improves, can reduce the risk that takes place bent axle 1 and the wearing and tearing of first bearing 2, bent axle 1 and first bearing 2 all are difficult wearing and tearing, can guarantee the reliability of this pump body 100's structural reliability and working process.

It will be understood that the first thrust portion 22 and the second thrust portion 121 are at least partial structures of the ends of the first bearing 2 and the eccentric portion 12 that are in contact with each other, respectively. In the axial direction, the two have no definite cut-off position, namely the axial depths of the two are not limited; in the radial direction, the inner edge of the first thrust part 22 coincides with the outer edge of the shaft hole 20, and the outer edge of the first thrust part 22 may be the outer edge of the first bearing 2, or may be a position between the outer edge of the shaft hole 20 and the outer edge of the first bearing 2; in the radial direction, the outer edge of the second thrust part 121 may be the outer edge of the eccentric part 12 or may not be the outer edge of the eccentric part 12, and the inner edge of the second thrust part 121 may be the inner edge of the eccentric part 12 or may not be the outer edge of the eccentric part 12.

Based on this, for convenience of illustration and understanding, the outer edge of the first thrust part 22 is shown inside the first bearing 2, and the outer edge of the second thrust part 121 is shown inside the eccentric part 12, as shown in fig. 2 and 6, and the boundary of the first thrust part 22 inside the first bearing 2 and the boundary of the second thrust part 121 inside the eccentric part 12 are shown by dotted lines.

As shown in fig. 3, the crankshaft 1 further includes a main shaft section 11 and a secondary shaft section 13 connected to both axial sides of the eccentric portion 12 and coaxially connected, wherein the secondary shaft section 13 is configured to be fitted into the shaft hole 20 of the first bearing 2, and specifically may be fitted into the shaft hole 20 by interference fit. It is understood that the central axis of the crankshaft 1 refers to the central axis of the main shaft section 11 and the auxiliary shaft section 13, from which the center of mass of the eccentric portion 12 is offset.

As shown in fig. 4, in the eccentric portion 12, the outer edge and the inner edge of the end surface of the second thrust portion 121 are both circular arcs, and the center O thereof is located on the central axis of the crankshaft 1. That is, the second thrust portion 121 has an arc shape with a constant radial width. As shown in fig. 5, in the first bearing 2, the outer edge and the inner edge of the end surface of the first thrust portion 22 are both circular, and the first thrust portion 22 is annular with a certain radial width and also has a center O. The second thrust parts 121 can all abut against the second thrust parts 121 in the circumferential direction.

As shown in fig. 4, the outer edge of the second thrust part 121 has a radius r4, and the inner edge has a radius r 1. The radial width of the second thrust portion 121 is h2 ═ r4 to r 1. As shown in fig. 5, the radius of the outer edge of the first thrust portion 22 is R4, the radius of the inner edge is R1, and the radial width h1 of the first thrust portion 22 is R4-R1. In one embodiment, the first hardened region 23 is a hardened layer, and the difference between the hardness value of the first hardened region 23 and the hardness value of the first bearing 2 in the region other than the first hardened region 23 is greater than or equal to 2. For example, typically, the hardness value of the other region of the first bearing 2 except the first hardened region 23 is 20HRC, and the hardness value of the first hardened region 23 is greater than or equal to 22 HRC; optionally, the first hardened region 23 has a hardness value greater than or equal to 23 HRC; further optionally, the first hardened region 23 has a hardness value of greater than or equal to 25 HRC. In alternative embodiments, the first hardened region 23 may have other lower values for hardness.

The hardness value of the first hardened region 23 also exists at an upper limit value. In one embodiment, the first hardened region 23 has a hardness value less than or equal to 60 HRC. The purpose of this arrangement is that, in the manufacturing process of the first bearing 2, the end face facing the eccentric portion 12, including the surface of the first thrust portion 22, needs to be treated by a process such as grinding to achieve a desired roughness, and the higher the hardness value, the greater the difficulty of grinding, the more the wear of the grinding tool will be increased, and the treatment cost may be increased. Therefore, the hardness value of the first hardened region 23 does not exceed 60HRC, enabling good wear resistance to be obtained while ensuring a low-cost process of the first bearing 2.

In a particular embodiment, the first hardened region 23 has a hardness value of 38HRC to 42HRC, which allows for a low cost and wear resistance of the manufacturing process of the first bearing 2.

In an alternative embodiment, the axial depth of the hardened layer ranges from 0.05mm to 15 mm.

The hardened layer may be obtained by quenching and tempering at least a part of the first thrust portion 22. The material structure of the hardening layer can be tempered martensite or tempered sorbite according to different tempering temperatures and different tempering times.

In an alternative implementation, the first hardened region 23 is a chrome or diamond-like coating. The first hardened region 23 has a hardness value in the range of 200HV to 2000HV and an axial depth of the first hardened region 23 in the range of 0.05 μm to 50 μm.

Referring to fig. 5 and 6, the outer edge and the inner edge of the first hardened region 23 are both circular, so that the first hardened region 23 is a circular ring with a certain radial width. The first hardened region 23 can always be in contact with the second thrust part 121 during eccentric rotation of the eccentric portion 12 relative to the first bearing 2.

The radius of the outer edge of the first hardened region 23 is R3, and the radius of the inner edge is R2, wherein R3 is equal to or less than R4, and R2 is equal to or more than R1. When R3 is equal to R4, and R2 is equal to R1, the first hardened region 23 is the first thrust portion 22, that is, the first thrust portion 22 is entirely hardened. In other cases, the first hardened region 23 is part of the first thrust part 22.

Referring to fig. 4, the outer edge and the inner edge of the second hardened region 122 are both circular arcs, and the second hardened region 122 is a circular ring with a certain radial width. The second hardened region 122 can always be in contact with the first hardened region 23 during eccentric rotation of the eccentric portion 12 relative to the first bearing 2.

The radius of the outer edge of the second hardened region 122 is r3, and the radius of the inner edge is r2, wherein r3 is not less than r4, and r2 is not less than r 1.

When r3 is r4 and r2 is r1, the second hardened region 122 is the second thrust portion 121, that is, the second thrust portion 121 is entirely hardened. In other cases, the second hardened region 122 is part of the second thrust part 121.

In order to ensure that the first hardened region 23 and the second hardened region 122 are able to abut, R3 > R2, and R2 < R3. In an alternative embodiment, R2 ≦ R2 < R3 ≦ R3; further, R2 < R2 < R3 < R3. The width H1 of the first hardened region 23 is R3-R2, the width H2 of the second hardened region 122 is R3-R2, and the ratio of H1 to H2 is 1-2, that is, the first hardened region 23 is designed to be able to abut against the entire region of the second hardened region 122; in other words, projecting the first hardened region 23 and the second hardened region 122 onto a radial plane along the axial direction, the projection of the first hardened region 23 can cover the projection of the second hardened region 122, which includes the projection of the first hardened region 23 coinciding with exactly the edge of the projection of the second hardened region 122, as well as at least a portion of the edge of the projection of the first hardened region 23 (the inner edge or the outer edge or both) being located outside the corresponding edge of the projection of the second hardened region 122.

In one embodiment, the second hardened region 122 is a hardened layer, and the difference between the hardness value of the second hardened region 122 and the hardness value of the other regions of the eccentric portion 12 except the second hardened region 122 is greater than or equal to 2. For example, typically, the hardness value of the other region of the eccentric portion 12 except for the second hardened region 122 is 20HRC, and then the hardness value of the second hardened region 122 is greater than or equal to 22 HRC; optionally, the first hardened region 23 has a hardness value greater than or equal to 23 HRC; further optionally, the first hardened region 23 has a hardness value of greater than or equal to 25 HRC. In alternative embodiments, the first hardened region 23 may have other lower values for hardness.

The hardness value of the first hardened region 23 also exists at an upper limit value. In one embodiment, the hardness value of the second hardened region 122 is less than or equal to 60 HRC. The purpose of this arrangement is that, in the manufacturing process of the eccentric portion 12, the end face facing the first bearing 2, including the surface of the second thrust portion 121, needs to be treated by a process such as grinding to achieve a desired roughness, and the hardness value is larger, the grinding difficulty is larger, the wear of the grinding tool is increased, and the treatment cost may be increased. Therefore, the hardness value of the second hardened region 122 does not exceed 60HRC, enabling good wear resistance to be obtained while ensuring a low-cost process for the first bearing 2.

In a specific embodiment, the second hardened region 122 has a hardness value of 38HRC to 42HRC, which is compatible with low cost and wear resistance of the manufacturing process of the first bearing 2.

In this embodiment, the second thrust portion 121 of the crankshaft 1 and the first thrust portion 22 of the first bearing 2 are simultaneously at least partially hardened, optionally the second hardened region 122 of the eccentric portion 12 has a hardness value greater than the hardness value of the first hardened region 23 of the first bearing 2. Therefore, the eccentric part 12 of the crankshaft 1 is not abraded, and the structural reliability of the crankshaft 1 is more favorable for ensuring the overall structural reliability of the pump body 100 because the crankshaft 1 is also used for being structurally connected with the second bearing 3, the rotor and the like.

Of course, without being limited thereto, in other alternative embodiments it is also possible that the hardness value of the second hardened region 122 of the eccentric portion 12 is less than or equal to the hardness value of the first hardened region 23 of the first bearing 2. It is generally desirable to minimize the degree of wear of either the eccentric portion 12 or the first bearing 2 as much as is necessary.

The hardened layer may be obtained by quenching and tempering at least a part of the second thrust portion 121. The material structure of the hardening layer can be tempered martensite or tempered sorbite according to different tempering temperatures and different tempering times.

In an alternative implementation, the second hardened region 122 is a chrome-plated layer or a diamond-like carbon-plated layer. The hardness value of the second hardened region 122 ranges from 200HV to 2000HV, and the axial depth of the second hardened region 122 ranges from 0.05 μm to 50 μm.

In one implementation, the hardness value of the second hardened region 122 may be less than, equal to, or greater than the hardness value of the first hardened region 23. For example, the ratio of the hardness value of the second hardened region 122 to the hardness value of the first hardened region 23 is 0.5 or more and 3 or less.

Optionally, the hardness value of the second hardened region 122 is equal to or greater than the hardness value of the first hardened region 23, that is, the ratio of the hardness value of the second hardened region 122 to the hardness value of the first hardened region 23 is greater than or equal to 0.5 and less than or equal to 1. This is intended to make the eccentric portion 12 of the crankshaft 1 less susceptible to wear than the first bearing 2, and since the pump body 100 has a greater number of structures to which the crankshaft 1 is connected, the reliability of the structure is more important to the structural reliability of the pump body 100.

As shown in fig. 2 and 6, in the present embodiment, an oil groove 21 is further provided on a side of the first bearing 2 facing the eccentric portion 12, and the oil groove 21 is provided inside the first thrust portion 22 and communicates with the shaft hole 20. That is, the oil groove 21 is provided between the first thrust portion 22 and the shaft hole 20.

In practical use of the pump body 100, it is necessary to lubricate the surfaces of the eccentric portion 12 of the crankshaft 1 and the first bearing 2 that rub against each other with lubricating oil. The lubricating oil enters the shaft hole 20 from the side of the first bearing 2 facing away from the eccentric part 12, lubricates the inner wall of the shaft hole 20 and the outer wall of the crankshaft 1, then continues to flow upwards, flows on the end surface of the first bearing 2 facing the side of the eccentric part 12 when reaching the end surface, and then enters between the first thrust part 22 of the first bearing 2 and the second thrust part 121 on the eccentric part 12, and lubricates the surfaces of the first thrust part 22 and the second thrust part 121, so that the friction force between the first thrust part 22 and the second thrust part 121 is reduced, the friction power consumption between the two is reduced, and the risk of abrasion between the two is reduced.

In this embodiment, the oil groove 21 disposed on the first bearing 2 can store a part of the lubricating oil, and during the operation of the pump body 100, the stored lubricating oil can timely and continuously supplement the lubricating oil entering between the first thrust portion 22 and the second thrust portion 121, so that the first thrust portion 22 and the second thrust portion 121 can always keep lubricating, thereby slowing or reducing the wear degree between the first thrust portion 22 and the second thrust portion 121, and ensuring the structural reliability of the pump body 100.

Here, it should be further noted that, when the first hardened region 23 is a hardened layer, due to phase transformation of material structures involved in the quenching and tempering processes, the volume of different material structures is different, the material structures expand in volume during the extremely cold transformation process of quenching, the oil groove 21 can also be designed to make room for the volume expansion of the material, thereby avoiding deformation of the inner wall of the shaft hole 20 caused by the expansion of the material inside the first hardened region 23, and also avoiding cracking caused by thermal stress concentration and the like of the material inside the first hardened region 23.

In one embodiment, the oil groove 21 may be annularly disposed, i.e., it may be continuously disposed 360 ° around the shaft hole 20. In this way, the lubricating oil can be spread from various positions on the periphery of the oil groove 21 to between the first thrust part 22 and the second thrust part 121, and the lubricating oil stored in the oil groove 21 has better dispersibility to various positions in the circumferential direction. Of course, the present invention is not limited to this, and in other alternative embodiments, a plurality of oil grooves 21 may be arranged at intervals on the outer circumference of the shaft hole 20, or the oil grooves 21 may be arranged circumferentially intermittently as a whole, according to other requirements.

In one embodiment, the axial depth of the oil groove 21 ranges from 0.1mm to 15 mm. The purpose of this arrangement is that the oil groove 21 has a certain axial depth, which has a significant guiding effect on the lubricating oil from the shaft hole 20 to the first thrust portion 22 and the second thrust portion 121, so that the effect of reducing the relative wear between the eccentric portion 12 and the first bearing 2 is significant; the axial depth of the oil groove 21 is not too large, so that the problem that the first bearing 2 deforms after the eccentric portion 12 abuts against the first bearing 2 due to insufficient material strength of the inner side of the first thrust portion 22 can be avoided, and the problem that the pump body 100 fails due to deformation of the first bearing 2 is further avoided.

Wherein the axial depth of the hardened layer of the first hardened zone 122 and the second hardened zone 23 can be greater than, equal to, or slightly less than the axial depth of the oil groove 21. There is no particular limitation.

In addition, the axial depths of the oil grooves 21 (or the axial depths of the plurality of oil grooves 21 arranged at intervals) may or may not be equal in the circumferential direction.

The shape of the oil groove 21 in the axial section may be various. For example, the shape of the oil groove 21 in the axial section may be rectangular, that is, the bottom wall of the oil groove 21 extends in the radial direction; alternatively, the oil groove 21 may be trapezoidal in shape in axial section, with its bottom wall inclined with respect to the radial direction, either inclined in the radially outward direction toward the eccentric portion 12 or inclined in the radially outward direction away from the eccentric portion 12. In other alternative embodiments, the shape of the oil groove 21 in the axial cross section may be any other available shape, and is not described herein again in detail, particularly considering the convenience of the manufacturing process and the good oil guiding effect.

The junction of the outer edge of the oil groove 21 and the end surface of the first bearing 2 facing the eccentric portion 12, that is, the junction of the oil groove 21 and the first thrust portion 22, forms a transition structure such as a chamfer or a fillet, so as to reduce burrs, barbs, and the like formed when the oil groove 21 is manufactured.

In one embodiment, the outer edge of the oil groove 21 coincides with the inner edge of the first hardened region 23, as shown in fig. 5 and 6, and the outer edge of the oil groove 21 has a radius R0. At this time, R0 ═ R2. I.e. the oil groove 21 is directly connected to the first hardened zone 23.

As shown in fig. 1, the pump body 100 further includes a second bearing 3, an upper muffler 41, a lower muffler 42, a cylinder 5, a vane 7, a piston 6, and the like. The second bearing 3 is sleeved on the main shaft section 11 of the crankshaft 1 and is used for supporting the rotation of the crankshaft 1; the upper silencer 41 is sleeved on the second bearing 3; the lower silencer 42 is fitted over the first bearing 2. The cylinder 5 is provided with a receiving cavity (not shown), the crankshaft 1 passes through the receiving cavity of the cylinder 5, the eccentric part 12 of the crankshaft 1 is positioned in the receiving cavity, and the piston 6 is arranged in the receiving cavity and sleeved on the eccentric part 12 of the crankshaft 1, so that the piston 6 is eccentrically installed relative to the central axis of the crankshaft 1, and the piston 6 can rotate around the central axis of the crankshaft 1 along with the eccentric part 12 of the crankshaft 1. The sliding vane 7 is installed on the cylinder 5, can slide along the radial direction and is pressed on the peripheral surface of the piston 6 in a sliding way, and in the process that the piston 6 rotates and the sliding vane 7 slides, the compression cavity is divided into a sealed and independent suction cavity and a compression cavity for compressing gas. The embodiment of the present application further provides a compressor (not shown in the drawings), which includes a housing, a motor, and the pump body 100 as described in the above embodiments, wherein the motor and the pump body 100 are both disposed in the housing, and one end of the crankshaft 1 away from the first bearing 2, that is, the main shaft section 11 thereof, is connected to a rotor of the motor. The rotation of the rotor of the motor can drive the crankshaft 1 to rotate around the central axis thereof, and the eccentric portion 12 rotates eccentrically. The features of the pump body 100 can be described with reference to the above embodiments, and will not be described herein.

Since the compressor includes the pump body 100 according to the above embodiment, the compressor also has the above advantageous effects based on one or more advantageous effects of the pump body 100. No further description is given.

The compressor can be a horizontal compressor or a vertical compressor. The compressor can be used in equipment capable of temperature regulation, such as but not limited to air conditioners, refrigerators and the like.

The above description is only exemplary of the present application and should not be taken as limiting the present application, as any modification, equivalent replacement, or improvement made within the spirit and principle of the present application should be included in the protection scope of the present application.

Claims

1. A pump body comprises a crankshaft and a first bearing, wherein the crankshaft is provided with an eccentric part, the first bearing is provided with a shaft hole, one side, facing the eccentric part, of the first bearing is provided with a first thrust part, one side, facing the first bearing, of the crankshaft is provided with a second thrust part, and the crankshaft is assembled in the shaft hole; the first thrust part comprises a first hardening area, and the hardness value of the first hardening area is greater than the hardness values of other areas of the first bearing except the first hardening area; the second thrust portion comprises a second hardened region, the hardness value of the second hardened region is greater than the hardness value of a position on the crankshaft outside the second hardened region, and the first hardened region and the second hardened region are in contact.

2. The pump body of claim 1, wherein the first hardened zone is a hardened layer having a surface hardness value in a range of 22HRC to 60HRC and an axial depth in a range of 0.05mm to 10 mm; or the first hardening area is a chromium plating layer or a diamond-like coating, the hardness value of the first hardening area ranges from 200HV to 2000HV, and the axial depth of the first hardening area ranges from 0.05 μm to 50 μm.

3. The pump body of claim 1, wherein the second hardened zone is a hardened layer having a surface hardness value in a range of 22HRC to 60HRC and an axial depth in a range of 0.05mm to 10 mm; or the second hardening area is a chromium coating or a diamond coating, the hardness value of the second hardening area ranges from 200HV to 2000HV, and the axial depth of the second hardening area ranges from 0.05 μm to 50 μm.

4. The pump body according to claim 2 or 3, wherein a ratio of the hardness value of the first hardened region to the hardness value of the second hardened region ranges from 0.5 to 3.

5. The pump body according to claim 4, wherein a ratio of the hardness value of the first hardened region to the hardness value of the second hardened region ranges from 0.5 to 1.

6. The pump body according to claim 2 or 3, wherein a ratio of a radial width of the first hardened region to a radial width of the second hardened region ranges from 1 to 2, and a projection of the second hardened region on a radial plane of the crankshaft is covered by a projection of the first hardened region on the radial plane.

7. The pump body according to claim 2 or 3, wherein the first bearing is further provided with an oil groove provided between the first thrust portion and the crankshaft and communicating with the shaft hole.

8. The pump body of claim 7, wherein said oil groove has an axial depth in the range of 0.1mm to 15 mm.

9. The pump body of claim 7, wherein the oil groove is in the form of a continuous ring surrounding the axial bore, and the junction of the outer edge of the oil groove and the end face of the first bearing is chamfered or radiused.

10. The pump body of claim 7, wherein an outer edge of the oil groove coincides with an inner edge of the first hardened region.

11. A compressor comprising a housing, a motor, and a pump body according to any one of claims 1 to 10, the motor and the pump body both being disposed within the housing, the pump body further comprising a cylinder, an end of the crankshaft remote from the first bearing being connected to a rotor of the motor, the crankshaft passing through the cylinder, the eccentric portion being disposed within a chamber of the cylinder.