CN215860797U - Pump body and compressor with same - Google Patents

Abstract

The pump body comprises a crankshaft, a first bearing and a thrust plate, the crankshaft is provided with an eccentric part and an auxiliary shaft section, the first bearing is provided with a shaft hole, the auxiliary shaft section is assembled in the shaft hole, the thrust plate is arranged on one side, away from the eccentric part, of the auxiliary shaft section and the first bearing, one end, facing the thrust plate, of the auxiliary shaft section is a thrust part, the thrust part comprises a hardening part, the hardness value of the hardening part is greater than that of other areas, except the hardening part, of the auxiliary shaft section, and the surface of the hardening part is abutted to the thrust plate; the wear resistance of the crankshaft and the auxiliary shaft section of the crankshaft is improved, the auxiliary shaft section is not easy to wear when being abutted with the thrust plate, the reliability of the crankshaft and the auxiliary structure of the crankshaft can be further ensured, the working reliability of the pump body is ensured, and the service life can be further prolonged; the compressor with the pump body has the advantages that the auxiliary shaft section of the crankshaft is not easy to wear, the structural reliability is high, the working reliability is high, and the service life is long.

Description

Pump body and compressor with same

Technical Field

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

Background

In a compressor, a thrust block and a thrust plate are generally used to support an end surface of a crankshaft. The thrust bearing and the thrust plate have certain deflection, and when the thrust bearing and the thrust plate are subjected to a large load, the thrust bearing and the thrust plate can deform to buffer pressure values reacting on the end face of the crankshaft, so that abrasion and impact on the end face of the crankshaft are reduced, and compared with a mode of rigidly abutting the crankshaft through a bearing, abrasion of the crankshaft is improved to a certain extent. However, as the compressor is used, the wear on the end surface of the crankshaft abutting the thrust plate increases. Therefore, there is still room for improvement in the structural reliability of the crankshaft in the compressor and its service life.

SUMMERY OF THE UTILITY MODEL

An object of the embodiment of this application is to provide a compressor, aim at solving among the current compressor the bent axle with easy wearing and tearing on the terminal surface of thrust plate butt and lead to the technical problem that bent axle became invalid, compressor became invalid and life is short.

The embodiment of the application realizes like this, a pump body, including bent axle, first bearing and thrust plate, the bent axle has eccentric portion and countershaft section, first bearing is equipped with the shaft hole, the countershaft section assemble in the shaft hole, the thrust plate is located the countershaft section with keeping away from of first bearing one side of eccentric portion, the orientation of countershaft section the one end of thrust plate is the portion that pushes away, the thrust portion is including sclerosis portion, the hardness value of sclerosis portion is greater than the hardness value of other positions of countershaft section sclerosis portion, the surface of sclerosis portion with thrust plate looks butt.

In one embodiment, the ratio of the hardness value of the hardening part to the hardness value of the other region of the auxiliary shaft section except the hardening region ranges from 1.2 to 4.

In one embodiment, the hardened portion is a hardened layer having a hardness value in a range of 25HRC to 60 HRC.

In one embodiment, the axial depth of the hardened layer ranges from 0.1mm to 5 mm.

In one embodiment, the hardened portion is a chromium plated layer or a diamond plated layer, and the hardness value of the hardened portion ranges from 300HV to HV 2000.

In one embodiment, the axial depth range of the hardened portion is greater than or equal to 2 μm.

In one embodiment, the ratio of the hardness value of the hardened portion to the hardness value of the thrust plate ranges from 0.5 to 1.5.

In one embodiment, the hardness value range of the thrust plate is more than 500 HV.

In one embodiment, the pump body further includes a thrust block, the thrust block includes a bottom abutting sheet and a side abutting sheet, the side abutting sheet is annular and connected to the periphery of the bottom abutting sheet, the bottom abutting sheet abuts against one side of the thrust sheet, which is far away from the thrust surface, and the side abutting sheet is annularly arranged on the periphery of the first bearing and is in interference fit with the first bearing.

Another objective of the embodiments of the present application is to provide a compressor, which includes a housing, a motor, and a pump body as in the above embodiments, where the motor and the pump body are both disposed in the housing, and one end of the crankshaft far away from the first bearing is connected to a rotor of the motor.

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 thrust part used for being abutted with the thrust plate on the auxiliary shaft section comprises the hardened part, the hardness value of the hardened part is greater than that of other parts on the auxiliary shaft section, so that the wear resistance of the crankshaft and the auxiliary shaft section is improved, and the hardened part is abutted with the thrust plate; the compressor with the pump body has the advantages that the auxiliary shaft section of the crankshaft is not easy to wear, the structural reliability is high, the working reliability is high, and the service life is long.

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 cross-sectional view of a crankshaft in the pump body shown in FIG. 1;

FIG. 4 is a bottom view of the crankshaft in the pump body of FIG. 1;

FIG. 5 is a cross-sectional view of a first bearing in the pump body of FIG. 1.

The designations in the figures mean:

100-a pump body;

1-crankshaft, 10-oil supply channel, 11-main shaft section, 12-eccentric part, 13-auxiliary shaft section, 131-thrust part, 132-hardening part and 14-oiling blade;

2-a first bearing, 20-a shaft hole;

3-a second bearing; 41-first muffler, 42-second muffler; 5-cylinder, 6-piston, 7-sliding sheet, 8-thrust sheet, 9-thrust seat, 91-bottom contact sheet, 92-side contact sheet and 920-pressing 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 and 2, the present embodiment first provides a pump body 100 including a crankshaft 1, a first bearing 2, and a thrust plate 8. As shown in fig. 3, the crankshaft 1 has a main shaft section 11, an eccentric section 12, and an auxiliary shaft section 13, and the eccentric section 12 is connected between the main shaft section 11 and the auxiliary shaft section 13; as shown in fig. 5, the first bearing 2 is provided with a shaft hole 20, and the auxiliary shaft section 13 is fitted in the shaft hole 20 in an inserted manner (e.g., with an interference fit). The thrust plate 8 is provided on the first bearing 2 and the sub-shaft section 13 on the side away from the eccentric portion 12. The thrust plate 8 has a surface facing the countershaft section 13 and the first bearing 2, that is, a thrust surface thereof, and an end of the countershaft section 13 facing the thrust surface is a thrust portion 131, wherein, as shown in fig. 2, the thrust portion 131 includes a hardened portion 132, or at least a part of the thrust portion 131 is the hardened portion 132 formed by some hardening treatment, and a hardness value of the hardened portion 132 is greater than a hardness value of a portion of the countershaft section 13 other than the hardened portion 132. During rotation of the crankshaft 1 about its own central axis, the surface of the hardened portion 132 abuts, specifically, slidably abuts, the thrust surface of the thrust washer 8.

The pump body 100 provided by the embodiment of the application, on the auxiliary shaft section 13 of the crankshaft 1, at least one part of the thrust part 131 forms the hardened part 132, the hardness value of the hardened part 132 is greater than that of other areas on the auxiliary shaft section 13, the surface of the hardened part 132 is used for being abutted to the thrust plate 8, the hardened part 132 is not easily worn, and therefore the wear resistance of the area on the auxiliary shaft section 13 for being in contact with the thrust plate 8 is improved, so that the auxiliary shaft section 13 is not easily worn when being abutted to the thrust plate 8, the structural reliability of the crankshaft 1 and the auxiliary shaft section 13 thereof can be ensured, and the service life of the pump body 100 can be effectively prolonged.

As shown in fig. 3, in the present embodiment, the main shaft section 11 and the sub shaft section 13 are coaxially arranged. It will be appreciated that the above-mentioned central axis of the crankshaft 1 refers to the central axis of the primary shaft section 11 and the secondary shaft section 13. The eccentric portion 12 abuts on one end of the first bearing 2 away from the thrust plate 8.

As shown in fig. 1 to 4, the auxiliary shaft section 13 is a hollow cylinder rotationally symmetric around the central axis of the crankshaft 1, a through hole formed inside the auxiliary shaft section serves as an oil supply passage 10, an oiling blade 14 is disposed in the oil supply passage 10, the oiling blade 14 is substantially helical, and lubricating oil moves along the oil supply passage 10 under the action of the oiling blade 14 and flows out from an oil hole (not shown) in the crankshaft 1 to lubricate the connection between the crankshaft 1 and other structures. The shape of the oil supply passage 10 generally corresponds to the shape of the outer wall of the secondary shaft section 13, and is cylindrical, and the outer edge and the inner edge of the thrust portion 131, that is, the outer edge and the inner edge of the secondary shaft section 13, are both circles, and the center O of the circle is located on the central axis of the crankshaft 1.

As shown in fig. 4, the outer edge of the thrust portion 131 (the region filled with the left lower diagonal line in fig. 4) has a radius R4, and the inner edge has a radius R1. The radial width H1 of the thrust portion 131 is R4-R1. As shown in fig. 5, the hardened portion 132 has an annular shape with a certain radial width, the radius of the outer edge of the hardened portion 132 is R3, the radius of the inner edge is R2, and the radial width H2 of the hardened portion 132 is R3-R2.

In one embodiment, the thrust portion 131 may be entirely the hardened portion 132. Then, R4 ═ R3 and R2 ═ R1. This is provided for the purpose that the thrust part 131 is entirely a region of relatively large hardness in the circumferential direction and in the radial direction, so that, during the sliding abutment of the thrust part 131 with the thrust plate 8, no problem of relatively severe local wear occurs at any position on the thrust part 131.

In other embodiments, the hardened portion 132 may be a portion of the push portion 131. That is, the hardened portion 132 may have only its outer edge coinciding with the outer edge of the thrust portion 131, or only its inner edge coinciding with the inner edge of the thrust portion 131, or alternatively, the hardened portion 132 and the thrust portion 131 may not coincide on both the outer edge and the inner edge. Since the sub-shaft block 13 rotates relative to the thrust plate 8, the problem that the local wear is too heavy in the thrust portion 131 is ensured to be less likely to occur even if the hardened portion 132 is annular, and the manufacturing cost of the hardened portion 132 can be reduced.

In one embodiment, the hardened portion 132 is a hardened layer, and the ratio of the hardness value of the hardened portion 132 to the hardness value of the other region of the secondary shaft section 13 except for the hardened portion 132 is greater than or equal to 1.2. For example, in some cases, the hardness value of the other region of the secondary shaft section 13 except the hardened portion 132 is 20HRC, and the hardness value of the hardened portion 132 is greater than or equal to 25HRC, so as to ensure that the hardened portion 132 has a sufficient hardness value to prolong the time for which the secondary shaft section 13 is worn as long as possible. In other alternative embodiments, the hardness value of the hardened portion 132 may have other lower values depending on specific needs or specific materials of the secondary shaft section 13, design of hardness value.

The hardness value of the hardened portion 132 also has an upper limit value. In one embodiment, the hardness value of the hardened portion 132 and the hardness value of the other region of the secondary shaft section 13 except for the hardened portion 132 have a ratio ranging from 4 or less. For example, when the hardness value of the region of the auxiliary shaft section 13 other than the hardened portion 132 is generally 20HRC, the hardness value of the hardened portion 132 is 60HRC or less. The purpose of this arrangement is that, in the manufacturing process of the crankshaft 1 and the counter shaft section 13 thereof, the end face of the thrust portion 131, including the surface of the hardened portion 132, 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 hardened portion 132 does not exceed 60HRC, and good wear resistance can be obtained while ensuring a low-cost process of the sub-shaft section 13.

In one embodiment, the hardness value of the hardened portion 132 is 30HRC to 50HRC, which can achieve both low cost and wear resistance of the manufacturing process of the crankshaft 1 and the counter shaft section 13 thereof. Further alternatively, the hardness value of the hardened portion 132 is 38HRC to 42HRC, so that the wear resistance of the secondary shaft section 13 can be significantly improved without significantly increasing the manufacturing cost of the crankshaft 1 and the secondary shaft section 13 thereof.

In this embodiment, the axial depth h of the hardened layer ranges from 0.1mm to 5mm as shown in FIG. 2.

The hardened layer may be obtained by quenching and tempering the thrust portion 131. 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 embodiment, the hardened portion 132 is a chrome or diamond-like plated layer. The hardness value of the hardened portion 132 ranges from 300HV to 1200 HV.

In this embodiment, the axial depth h of the hardened portion 132 ranges from 0.05 μm to 50 μm. In practical applications, the specific value of the axial depth h of the hardened portion 132 can be designed by taking the specific requirements into consideration, and is not particularly limited herein.

In one embodiment, the ratio of the hardness value of the hardened portion 132 to the hardness value of the thrust plate 8 is 0.5 to 1.5. That is, the hardness value of the thrust plate 8 may be smaller than that of the hardened portion 132, so that the counter shaft section 13 is less prone to wear relative to the thrust plate 8 during the process of abutting the crankshaft 1 and the thrust plate 8, and the reliability of the structure is more important to the structural reliability and the service life of the pump body 100 because the crankshaft 1 is connected with more structural members. Of course, in other alternative embodiments, it is also possible that the hardness value of the thrust plate 8 is greater than the hardness value of the hardened portion 132 on the basis of at least partial hardening of the auxiliary shaft section 13, so as to ensure that neither the crankshaft 1 nor the thrust plate 8 is easily worn.

Alternatively, the hardness value of the thrust plate 8 ranges from greater than or equal to 500 HV. For example, the thrust plate 8 may be carbon tool steel; alternatively, thrust plate 8 may be another piece of material, depending on the specific requirements of pump body 100.

In one embodiment, referring to fig. 2, the pump body 100 further includes a thrust block 9, the thrust block 9 includes a bottom abutting sheet 91 and a side abutting sheet 92, the side abutting sheet 92 is annular and is connected to the outer periphery of the bottom abutting sheet 91, the bottom abutting sheet 91 is disposed on the side of the thrust block 8 away from the thrust surface thereof and abuts against the thrust block 8, the side abutting sheet 92 is disposed around the outer periphery of the first bearing 2 and is in interference fit with the first bearing 2 through a pressing sheet 920 disposed on the inner surface thereof, so as to connect the thrust block 8 with the first bearing 2 and the auxiliary shaft section 13 together.

As shown in fig. 2, a portion of the bottom abutment plate 91 is bent toward the thrust plate 8 to form a bent and protruded structural member, which is disposed to make the thrust block 9 have a certain flexibility, that is, when the thrust block 9 is subjected to an axial force from the thrust plate 8 and the crankshaft 1, the bent and protruded structural member can be deformed to some extent, so that the force and reaction between the thrust surface of the thrust plate 8 and the end surface of the secondary shaft section 13 can be buffered to some extent, and the wear between the secondary shaft section 13 and the thrust plate 8 can be reduced. Therefore, in the pump body 100 provided in the embodiment of the present application, the wear of the end face of the auxiliary shaft section 13 can be significantly improved, and the structural reliability of the pump body 100 can be significantly improved, and the service life of the pump body 100 can be significantly prolonged.

As shown in fig. 1, the pump body 100 further includes a second bearing 3, a first muffler 41, a second 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 first silencer 41 is sleeved on the second bearing 3; the second muffler 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.

Another object of the present embodiment is to provide a compressor (not shown) including 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 far from the first bearing 2 is connected to a rotor of the motor.

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 (10)

1. The pump body is characterized by comprising a crankshaft, a first bearing and a thrust plate, wherein the crankshaft is provided with an eccentric part and an auxiliary shaft section, the first bearing is provided with a shaft hole, the auxiliary shaft section is assembled in the shaft hole, the thrust plate is arranged on one side, far away from the eccentric part, of the auxiliary shaft section and the first bearing, one end, facing the thrust plate, of the auxiliary shaft section is a pushing part, the thrust part comprises a hardening part, the hardness value of the hardening part is greater than that of other parts, except the hardening part, of the auxiliary shaft section, and the surface of the hardening part is abutted to the thrust plate.

2. The pump body according to claim 1, wherein a ratio of the hardness value of the hardened portion to the hardness value of a region of the secondary shaft section other than the hardened portion is in a range of 1.2 to 4.

3. The pump body of claim 2, wherein the hardened portion is a hardened layer having a hardness value in a range of 25HRC to 60 HRC.

4. The pump body of claim 3, wherein the axial depth of the hardened layer ranges from 0.1mm to 5 mm.

5. The pump body of claim 2, wherein the hardened portion is a chrome or diamond plated layer, the hardened portion having a hardness value in a range of 300HV to HV 2000.

6. The pump body of claim 5, wherein the axial depth of the hardened portion ranges from greater than or equal to 2 μm.

7. The pump body according to any one of claims 1 to 6, wherein a ratio of a hardness value of the hardened portion to a hardness value of the thrust plate is in a range of 0.5 to 1.5.

8. The pump body of claim 7, wherein the thrust plate has a hardness value in a range of 500HV or greater.

9. The pump body according to any one of claims 1 to 6, further comprising a thrust block including a bottom abutment plate and a side abutment plate, the side abutment plate being annular and connected to a periphery of the bottom abutment plate, the bottom abutment plate abutting a side of the thrust plate facing away from the counter shaft section, the side abutment plate being annularly disposed on an outer periphery of the first bearing and being in interference fit with the first bearing.

10. A compressor comprising a housing, a motor, and a pump body according to any one of claims 1 to 9, the motor and the pump body being disposed in the housing, the end of the crankshaft remote from the first bearing being connected to a rotor of the motor.

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