CN114151344A

CN114151344A - Bearing of compressor, compressor and refrigeration equipment

Info

Publication number: CN114151344A
Application number: CN202111468627.6A
Authority: CN
Inventors: 高强; 高斌; 张里华; 刘文智
Original assignee: Guangdong Meizhi Compressor Co Ltd; Anhui Meizhi Precision Manufacturing Co Ltd
Current assignee: Guangdong Meizhi Compressor Co Ltd; Anhui Meizhi Precision Manufacturing Co Ltd
Priority date: 2021-12-03
Filing date: 2021-12-03
Publication date: 2022-03-08
Anticipated expiration: 2041-12-03
Also published as: CN114151344B

Abstract

The invention discloses a bearing of a compressor, the compressor and refrigeration equipment, wherein the bearing is arranged at the end part of an air cylinder along the axial direction, the bearing is provided with an axle hole for inserting a crankshaft, the end surface of the bearing facing the air cylinder is provided with a flexible groove, the flexible groove is arranged around the axle hole, and an annular groove wall is formed between the flexible groove and the axle hole; follow the axial of bearing, be close to in the flexible groove the lateral wall slope in shaft hole sets up, makes the cell wall is followed the radial thickness of bearing certainly the opening of flexible groove to the bottom of flexible groove increases gradually, for thickness evenly distributed's cell wall structure, can effectively reduce the face pressure of bearing, and then reduces the wearing and tearing between bearing and the bent axle, especially to bad operating mode such as liquid attack or maximum load, effectively reduces the local phenomenon that polishes of bearing, is favorable to improving the reliability of compressor operation.

Description

Bearing of compressor, compressor and refrigeration equipment

Technical Field

The invention relates to the technical field of compressors, in particular to a bearing of a compressor, the compressor and refrigeration equipment.

Background

The upper bearing and the lower bearing of the rotary compressor are used as pressure-bearing parts for crankshaft motion, and the surface pressure born by the upper bearing and the lower bearing directly influences the performance of an oil film and the wear resistance of a crankshaft. In the related technology, the upper bearing and the lower bearing adopt a flexible groove structure to improve the bearing surface pressure and the minimum oil film thickness, but under the working conditions of liquid impact or maximum load and the like, the surface of a bearing hole corresponding to the bottom of the flexible groove still can be polished, and the operation reliability is reduced.

Disclosure of Invention

The present invention is directed to solving at least one of the problems of the prior art. Therefore, the bearing of the compressor provided by the invention can effectively reduce the abrasion between the crankshaft and the bearing aiming at the working conditions of liquid impact, maximum load and the like, and is beneficial to improving the operation reliability of the compressor.

The invention also provides a compressor and refrigeration equipment comprising the bearing.

According to the bearing of the compressor provided by the embodiment of the first aspect of the invention, the bearing is arranged at the end part of the cylinder of the compressor along the axial direction, the bearing is provided with a shaft hole for inserting a crankshaft, the end surface of the bearing facing the cylinder is provided with a flexible groove, the flexible groove is arranged around the shaft hole, and an annular groove wall is formed between the flexible groove and the shaft hole;

and along the axial direction of the bearing, the side wall of the flexible groove, which is close to the shaft hole, is obliquely arranged, so that the thickness of the groove wall along the radial direction of the bearing is gradually increased from the opening of the flexible groove to the bottom of the flexible groove.

The bearing of the compressor provided by the embodiment of the invention has at least the following beneficial effects:

through set up the flexible groove on the terminal surface of bearing orientation cylinder, form annular cell wall between flexible groove and the shaft hole, can make cell wall position take place deformation easily through the flexible groove, reduce the structural rigidity of shaft hole and cell wall corresponding position, and in the axial of bearing, set up the lateral wall slope that is close to the shaft hole in the flexible groove, the thickness of cell wall is crescent from the opening of flexible groove to the bottom of flexible groove, make the cell wall obtain improving at the intensity of flexible groove bottom corresponding position, for the cell wall structure of thickness evenly distributed, can effectively reduce the face pressure of bearing, and then reduce the wearing and tearing between bearing and the bent axle, especially to abominable operating mode such as liquid impact or maximum load, effectively reduce the local phenomenon that appears polishing of bearing, be favorable to improving the reliability of compressor operation.

According to some embodiments of the invention, the position of the groove wall at the opening of the flexible groove is a top, the position of the groove wall at the bottom of the flexible groove is a root, the thickness of the top is t1, and the thickness of the root is t2, which satisfies: t2 is t1+ Δ t, and Δ t is 0.25mm ≦ Δ t ≦ 1 mm.

According to some embodiments of the invention, the thickness t1 of the top portion satisfies: t1 is not less than 1.25mm and not more than 3.5 mm.

According to some embodiments of the invention, the width of the bottom of the compliant groove in the radial direction of the bearing is t3, satisfying: t3 is not less than 0.5mm and not more than 2 mm.

According to some embodiments of the invention, a side wall of the flexible groove near the shaft hole is a first side wall, and a side wall opposite to the first side wall is a second side wall, and the second side wall is arranged in parallel with an axis of the shaft hole or in parallel with the first side wall.

According to some embodiments of the invention, in a section of the bearing along the axial direction, an included angle between a contour line of the first side wall and an axis of the shaft hole is α, and the following conditions are satisfied: alpha is more than or equal to 2 degrees and less than or equal to 8 degrees.

According to some embodiments of the invention, the bearing comprises a flange portion and a bearing neck portion connected to the flange portion, a side of the flange portion facing the cylinder in an axial direction of the bearing neck portion is a flange surface, and the flexible groove is provided on the flange surface.

According to some embodiments of the invention, the distance between the flange face and the bottom of the compliant groove is h1, and the distance between the flange face and the end face of the bearing neck portion remote from the flange face is h, satisfying: h1 is more than or equal to 0.15h and less than or equal to 0.17h or h1 is more than or equal to 0.38h and less than or equal to 0.40 h.

According to some embodiments of the invention, the groove wall is located at the opening of the flexible groove at a top, the distance between the top and the flange face being smaller than the distance between the flange face and the bottom of the flexible groove.

According to some embodiments of the invention, the distance between the top part and the flange surface is h2, the crankshaft is provided with an undercut groove, the width of the undercut groove along the axial direction of the crankshaft is h3, and the following conditions are met: h 2-h 3.

A compressor according to an embodiment of the second aspect of the present invention includes the bearing of the embodiment of the first aspect.

The compressor provided by the embodiment of the invention has at least the following beneficial effects:

the bearing of the embodiment is adopted as a pressure-bearing part for crankshaft movement, the bearing can enable the groove wall part to be easily deformed through the flexible groove, the structural rigidity of the corresponding position of the shaft hole and the groove wall is reduced, the thickness of the groove wall is gradually increased from the opening of the flexible groove to the bottom of the flexible groove, the strength of the groove wall at the corresponding position of the bottom of the flexible groove is improved, the surface pressure of the bearing can be effectively reduced compared with the groove wall structure with uniformly distributed thickness, the abrasion between the bearing and the crankshaft is further reduced, particularly, the phenomenon that the bearing is locally polished is effectively reduced aiming at severe working conditions such as liquid impact or maximum load, and the operation of the compressor is more reliable.

The refrigeration equipment provided by the embodiment of the third aspect of the invention comprises the compressor provided by the embodiment of the second aspect.

The refrigeration equipment adopts all the technical solutions of the compressor of the above embodiments, and therefore has at least all the advantages brought by the technical solutions of the above embodiments.

Additional features and advantages of the invention will be set forth in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention.

Drawings

The above and/or additional aspects and advantages of the present invention will become apparent and readily appreciated from the following description of the embodiments, taken in conjunction with the accompanying drawings of which:

FIG. 1 is a schematic cross-sectional view of an upper bearing according to an embodiment of the present invention;

FIG. 2 is an enlarged schematic view of the structure at A in FIG. 1;

FIG. 3 is a schematic cross-sectional view of a lower bearing according to an embodiment of the present invention;

FIG. 4 is a schematic cross-sectional view of an upper bearing according to another embodiment of the present invention;

FIG. 5 is a cross-sectional view of a lower bearing according to another embodiment of the present invention;

FIG. 6 is a schematic cross-sectional view of a pump block assembly according to an embodiment of the present invention;

FIG. 7 is an enlarged schematic view of the structure at B in FIG. 6;

FIG. 8 is a schematic cross-sectional view of a pump block assembly according to another embodiment of the present invention;

FIG. 9 is a schematic cross-sectional view of a pump block assembly according to another embodiment of the present invention;

fig. 10 is a schematic sectional view of a pump body assembly according to another embodiment of the present invention.

Reference numerals:

an upper bearing 1000;

a lower bearing 2000;

a bearing body 100; a flange portion 110; a flange face 111; a bearing neck 120; a shaft hole 121; an oil sump 122; a valve seat 130; an exhaust port 131; a flexible slot 140; a first sidewall 141; a second sidewall 142; a slot wall 150; a top portion 151; a root portion 152; the third side wall 153;

an upper cylinder 200; an upper roller 210;

a lower cylinder 300; a lower roller 310;

a separator 400;

a crankshaft 500; the relief groove 510.

Detailed Description

Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the accompanying drawings are illustrative only for the purpose of explaining the present invention, and are not to be construed as limiting the present invention.

In the description of the present invention, it is to be understood that the terms "axial," "radial," "upper," "lower," and the like refer to an orientation or positional relationship based on that shown in the drawings, which is for convenience and simplicity of description only, and does not indicate or imply that the referenced device or element must have a particular orientation, be constructed and operated in a particular orientation, and thus, should not be considered as limiting the present invention.

In the description of the present invention, greater than, less than, etc. are understood as not including the essential numbers. If the first and second are described for the purpose of distinguishing technical features, they are not to be understood as indicating or implying relative importance or implicitly indicating the number of technical features indicated or implicitly indicating the precedence of the technical features indicated.

In the description of the present invention, it should be noted that the terms such as setting, installing, connecting, etc. should be understood in a broad sense, and those skilled in the art can reasonably determine the specific meanings of the terms in the present invention by combining the specific contents of the technical solutions.

The compressor is a driven fluid machine that raises low-pressure gas to high-pressure gas, and is the heart of a refrigeration system. The rotary compressor drives a crankshaft to rotate by utilizing a motor assembly, a roller is driven to rotate in a cylinder by the crankshaft, an upper bearing and a lower bearing are generally adopted as pressure-bearing parts for the crankshaft to move, and the surface pressure born by the upper bearing and the lower bearing directly influences the performance of an oil film and the abrasion resistance of the crankshaft.

In the correlation technique, most rotary compressors set up the flexible groove at last bearing and lower bearing, and the flexible groove is the annular and is close to the shaft hole setting, also is called the ring channel, can reduce the rigidity that shaft hole inner wall and flexible groove correspond the position through the flexible groove, can improve the bearing surface and press, increase minimum oil film thickness, and the flexible groove structure has been widely used on rotary compressor. However, for severe working conditions such as liquid impact or maximum load, the surface pressure borne by the bearing is increased, the surface of the bearing hole corresponding to the bottom of the annular groove is easily abraded, the polishing phenomenon occurs, and the operation reliability of the compressor is reduced.

According to the embodiment provided by the invention, the strength of the corresponding position of the bottom of the flexible groove is increased, and compared with the existing annular groove structure, the surface pressure of the bearing can be effectively reduced, so that the abrasion between the bearing and the crankshaft is reduced, particularly the phenomenon that the local part of the pressure-bearing component is polished is effectively reduced under the severe working conditions such as liquid impact or maximum load, and the operation reliability of the compressor is improved.

A bearing according to an embodiment of the present invention is described with reference to fig. 1 to 5, which is applicable to a rotary compressor, and the bearing will be described below with a specific example.

Referring to fig. 1, a bearing according to an embodiment of the present invention includes a bearing body 100, the bearing body is substantially circular, a shaft hole 121 is disposed at a central position of the bearing body 100, and the shaft hole 121 axially penetrates through the bearing body 100. The bearing of the embodiment is installed at the end of the cylinder of the compressor in the axial direction, and may be provided at the upper end or the lower end of the cylinder for the upper bearing 1000 or the lower bearing 2000 of the compressor, or may be provided at both the upper end and the lower end of the cylinder.

Referring to fig. 1, in detail, the bearing body 100 includes a flange portion 110 and a bearing neck portion 120, the bearing neck portion 120 is substantially cylindrical, the flange portion 110 is substantially circular disk-shaped, the bearing neck portion 120 is connected to a central position of the flange portion 110, the flange portion 110 is located at a bottom end of the bearing neck portion 120, a shaft hole 121 axially penetrates through the bearing neck portion 120 and the flange portion 110, and the bearing neck portion 120 and the flange portion 110 are integrally formed.

Fig. 1 is a schematic cross-sectional structure diagram of a bearing body 100, in which the bottom surface of the flange portion 110 is a flange surface 111, the bearing neck portion 120 is disposed away from the flange surface 111, after the bearing is assembled in place, the flange surface 111 faces the cylinder, and the bearing neck portion 120 faces the outside of the cylinder. The flange 110 is provided with a valve seat 130 and an exhaust port 131 opened on the valve seat 130, and the cylinder exhausts through the exhaust port 131, which is not described in detail. As shown in fig. 1, a flexible groove 140 is formed on the flange surface 111 near the shaft hole 121, and the flexible groove 140 is disposed around the shaft hole 121 such that the flexible groove 140 forms an annular groove. It can be understood that the flexible groove 140 is spaced apart from the shaft hole 121, a groove wall 150 having a certain thickness is formed between the flexible groove 140 and the shaft hole 121, and the groove wall 150 has a ring shape.

Referring to fig. 1 and 2, the opening of the flexible groove 140 faces downward, and the flexible groove 140 extends in the axial direction to a certain depth, it can be understood that, compared to a bearing structure without the flexible groove 140, the rigidity of the corresponding positions of the shaft hole 121 and the groove wall 150 can be reduced by the flexible groove 140, and when the side of the groove wall 150 facing the shaft hole 121 is pressed in contact with the crankshaft 500, the part of the groove wall 150 is easily deformed, so that the surface pressure of the bearing at the position of the groove wall 150 can be reduced, the minimum oil film thickness is increased, which is beneficial to reducing the wear between the crankshaft 500 and the bearing, and the compressor operation is more stable.

In consideration of the fact that the surface pressure of the bearing is increased under severe working conditions such as liquid impact or maximum load, the side wall of the flexible groove 140 is arranged with a certain inclination, the strength of the corresponding position of the groove wall 150 and the bottom of the flexible groove 140 is improved, and the surface pressure of the bearing can be further reduced aiming at the severe working conditions, so that the abrasion between the bearing and the crankshaft 500 is reduced, the phenomenon that the pressure-bearing part is partially polished is reduced, and the reliability of the operation of the compressor is improved.

Specifically, referring to fig. 2, in the radial direction of the shaft hole 121, a side wall of the flexible groove 140 close to the shaft hole 121 is a first side wall 141, and a side wall opposite to the first side wall 141 is a second side wall 142, wherein the first side wall 141 is inclined in the axial direction, so that the thickness of the groove wall 150 gradually increases from the opening of the flexible groove 140 to the bottom of the flexible groove 140.

It is understood that the groove wall 150 is annular as a whole, the first sidewall 141 is located on a side of the groove wall 150 facing the flexible groove 140, the third sidewall 153 is located on a side of the groove wall 150 facing the shaft hole 121, and the third sidewall 153 is parallel to the axis of the shaft hole 121, and the first sidewall 141 and the third sidewall 153 are not parallel by inclining the first sidewall 141. As shown in fig. 2, in the case that the first side wall 141 and the third side wall 153 are disposed in non-parallel with each other, the thickness of the groove wall 150 is non-uniformly distributed along the axial direction, in the embodiment, the closer to the bottom of the flexible groove 140, the greater the thickness of the groove wall 150 is, that is, the groove wall 150 becomes thicker gradually from the opening to the bottom, and the thickness of the groove wall 150 at the bottom of the flexible groove 140 is greater than the thickness at the notch. It should be noted that the thickness of the groove wall 150 can be understood as the distance between the first side wall 141 and the third side wall 153 along the radial direction of the bearing body 100.

Referring to fig. 1 and 2, the opening of flexible slot 140 on slot wall 150 is located at the top 151 of slot wall 150, the bottom of flexible slot 140 on slot wall 150 is located at the root 152 of slot wall 150, the thickness of slot wall 150 increases from top 151 to root 152, the thickness of top 151 of slot wall 150 is the smallest, and the thickness of root 152 is the largest.

In the related art, the side wall of the flexible groove is axially and straightly arranged, that is, the thickness of the groove wall is uniformly distributed along the axial direction, and the thickness of the root part and the top part of the groove wall is consistent. When the load is too large, the bearing bears large surface pressure, the deformation amount of the groove wall is also large, the friction between the connecting position of the groove wall and the bearing body and the crankshaft is increased, and further the abrasion between the bearing and the crankshaft is improved.

It can be understood that, compared with the groove wall structure with uniform thickness distribution, the embodiment of the present invention increases the thickness of the groove wall 150 from the top 151 to the root 152, so that the root 152 of the groove wall 150 is thickened, thereby increasing the strength of the root 152, that is, the rigidity of the inner wall of the shaft hole 121 corresponding to the bottom of the flexible groove 140 is enhanced. When the compressor meets severe working conditions such as liquid impact or maximum load, the strength of the root 152 of the groove wall 150 is improved under the condition of certain flexibility through the flexible groove 140, deformation is not easy to occur, and the surface pressure can be effectively reduced, so that the abrasion between the bearing and the crankshaft 500 is reduced, the phenomenon that the bearing is located on the inner wall of the shaft hole 121 and is locally polished is reduced, and the operation reliability of the compressor is improved.

It should be noted that the bearing neck 120 is located at the center of the flange portion 110, and the central axis of the bearing neck 120 coincides with the central axis of the flange portion 110, and in the embodiment, the axial direction may be understood as the central axis direction of the bearing neck 120, and the radial direction may be understood as the radial direction of the bearing neck 120. Fig. 1 is a schematic sectional view of an upper bearing 1000, in which the upper bearing 1000 is provided with a valve seat 130 and an exhaust port 131, and a flexible groove 140 is provided on a flange surface 111. Fig. 3 is a schematic cross-sectional view illustrating the lower bearing 2000, and it can be understood that the height of the bearing neck 120 of the lower bearing 2000 is less than the height of the bearing neck 120 of the upper bearing 1000.

Referring to fig. 3, an upper end surface of the lower bearing 2000 is a flange surface 111, and a flexible groove 140 is disposed on the upper end surface of the lower bearing 2000, wherein the upper bearing 1000 is connected to an upper end of the cylinder, the lower bearing 2000 is connected to a lower end of the cylinder, and an opening of the flexible groove 140 of the upper bearing 1000 and an opening of the flexible groove 140 of the lower bearing 2000 are both directed toward the cylinder. The specific structure of the flexible groove 140 of the lower bearing 2000 can refer to the description of the embodiment shown in fig. 1, and is not described herein again.

It can be understood that by providing the flexible grooves 140 on the upper bearing 1000 and the lower bearing 2000, respectively, the upper bearing 1000 and the lower bearing 2000 can improve the surface pressure to be borne, increase the minimum oil film thickness, and more effectively reduce the wear of the crankshaft 500 and the pressure-bearing member; and the strength of the groove wall 150 of the flexible groove 140 of the upper bearing 1000 and the lower bearing 2000 is enhanced by adopting the structure of the embodiment, especially for severe working conditions, the bearing surface pressure can be reduced by 3% -15%, the occurrence of the polishing phenomenon is effectively reduced, and the reliability of the compressor in operation under the severe working conditions is improved.

Referring to fig. 1, 2 and 3, in the embodiment, the second sidewall 142 is disposed parallel to the third sidewall 153, the second sidewall 142 is not parallel to the first sidewall 141, that is, the first sidewall 141 is disposed obliquely in the axial direction, and the second sidewall 142 is disposed straightly, so that the opening width of the flexible groove 140 is greater than the width of the bottom. It can be understood that the flexible groove 140 is annular, the cross sections of the flexible groove 140 are symmetrically distributed along the central axis, and both the symmetrical cross sections of the flexible groove 140 are substantially trapezoidal; the cross-sections of the slot walls 150 are also symmetrically distributed on both sides of the central axis, and the symmetrical cross-sections are also substantially trapezoidal. Taking the cross section shown in fig. 2 as an example, the width of the flexible groove 140 gradually decreases from bottom to top, and the thickness of the groove wall 150 gradually increases from bottom to top, thereby increasing the strength of the root portion 152 of the groove wall 150.

Referring to fig. 4 and 5, in some embodiments, the second sidewall 142 and the first sidewall 141 are parallel to each other, that is, the second sidewall 142 is inclined in the axial direction, and the width of the flexible groove 140 does not change from the opening to the bottom. Fig. 4 is a schematic cross-sectional view of the upper bearing 1000, in which the opening of the flexible groove 140 is inclined downward in the axial direction, and the second sidewall 142 is inclined from straight to inclined in the axial direction, i.e. the second sidewall 142 and the third sidewall 153 are not parallel to each other, relative to the embodiment shown in fig. 1. It should be noted that in the embodiment shown in fig. 1 and 4, the dimensions of slot wall 150 may be the same, for example, the slope of first sidewall 141 is the same, and the thickness of top 151 and root 152 of slot wall 150 is the same. Fig. 5 is a schematic cross-sectional view of the lower bearing 2000, in which the first sidewall 141 and the second sidewall 142 are parallel to each other and are inclined in the axial direction, and the opening of the flexible groove 140 is inclined upward in the axial direction.

Specifically, taking the upper bearing 1000 shown in fig. 1 and 2 as an example, the thickness of the root 152 of the groove wall 150 is the largest, and the thickness of the top 151 of the groove wall 150 is the smallest, where the thickness of the top 151 is t1, the thickness of the root 152 is t2, t2 is t1+ Δ t, and 0.25mm ≦ Δ t ≦ 1mm, that is, the thickness of the root 152 is greater than the thickness of the top 151, and the difference between the two is in the range of 0.25mm-1mm (millimeter). As shown in fig. 2, as the first sidewall 141 is inclined from the opening to the bottom, the thickness of the groove wall 150 is gradually increased such that the root portion 152 is thicker than the top portion 151. For example, when the top portion 151 is 2mm, the thickness of the root portion 152 may be 2.25mm, 2.5mm, 3mm, etc., according to the above-mentioned formula t2 ═ t1+ Δ t.

The smaller the thickness of the top portion 151, the lower the rigidity, and the more likely it is to be deformed, and the larger the thickness of the root portion 152, the higher the rigidity. If the thickness of the top 151 is too small, the top 151 of the groove wall 150 can form a thin-wall structure, so that the flexibility is increased, the groove wall is easy to deform, and the stability of the oil film thickness is not facilitated to be kept; if the thickness of the root 152 is too large, the rigidity of the root 152 of the groove wall 150 is large, so that the groove wall is not easy to deform, the surface pressure of the bearing is not improved, and the abrasion is easy to increase.

Under the condition that the bearing rigidity can be reduced by the flexible groove 140, the thickness of the root 152 and the top 151 of the groove wall 150 can be further limited to meet the conditions that t2 is t1+ Δ t and 0.25mm is not less than Δ t and not more than 1mm under severe working conditions, the overlarge thickness deviation of the root 152 and the top 151 can be avoided, and thus when the thickness of the top 151 meets a certain strength requirement, the thickness of the root 152 also meets the requirement of rigidity, the condition that the root 152 is too thick or too thin is reduced, the bearing surface pressure can be effectively reduced, and the phenomenon that the surface of the shaft hole 121 corresponding to the bottom of the flexible groove 140 is polished is also favorably reduced.

Referring to FIG. 2, in some embodiments, the thickness t1 of the top 151 of the slot wall 150 satisfies the condition of 1.25mm ≦ t1 ≦ 3.5mm, it being understood that the thickness of the top 151 of the slot wall 150 is the smallest, and thus the smallest thickness ranges from 1.25mm to 3.5mm, and by combining the above-mentioned conditions of t2 ≦ t1+ Δ t, and 0.25mm ≦ Δ t ≦ 1mm, the largest thickness of the slot wall 150 ranges from 1.5mm to 4.5 mm. For example, when the thickness t1 of the top portion 151 is 1.25mm, as obtained according to t2 t1+0.5, the thickness t2 of the root portion 152 is 1.75 mm; as another example, when the thickness t1 of the top portion 151 is 2.5mm, as obtainable according to t2 t1+1, the thickness t2 of the root portion 152 is 3.5 mm; as another example, when the thickness t1 of the top portion 151 is 3.5mm, as can be obtained from t2 t1+1, the thickness t2 of the root portion 152 is 4.5 mm. The top 151 of the slot wall 150 preferably has a thickness in the range of 1.5mm to 2.5mm, depending on the application, to maintain the top 151 suitably rigid.

Referring to fig. 2, in the embodiment, the width of the opening position of the flexible groove 140 is greater than that of the bottom position, and the width of the flexible groove 140 decreases from the opening to the bottom direction, the width of the bottom of the flexible groove 140 is t3, and it satisfies 0.5mm ≦ t3 ≦ 2mm, that is, the minimum width of the flexible groove 140 ranges from 0.5mm to 2mm, for example, the width of the bottom of the flexible groove 140 may be 0.5mm, 1mm, 2mm, and so on. It will be appreciated that the greater the width of the flexible groove 140, the lower the effective sealing distance of the roller from the bearing plane; while too small a width of the flexible channel 140 may affect the structural rigidity of the channel wall 150. The bottom width of the flexible groove 140 is set to meet the condition that t3 is more than or equal to 0.5mm and less than or equal to 2mm, so that the effective sealing distance between the roller and the bearing plane can be ensured, and the structural reliability is improved.

It should be noted that the width of the flexible groove 140 is the distance between the first side wall 141 and the second side wall 142 along the radial direction of the shaft hole 121, and in the embodiment shown in fig. 2, the width of the opening position of the flexible groove 140 may be set to be slightly larger than the width of the bottom position, for example, the width of the opening may be 2mm, and the width of the bottom may be 1.5 mm. In the embodiment shown in fig. 3, since the first side wall 141 and the second side wall 142 are arranged in parallel, the width of the opening of the flexible groove 140 corresponds to the width of the bottom position, for example, the width of the opening is 1 mm.

In the embodiment shown in fig. 2, in the cross section of the upper bearing 1000, the contour line of the first sidewall 141 is an oblique line, the contour line of the second sidewall 142 is a vertical line, and the contour line of the second sidewall 142 is parallel to the central axis. It is understood that, with a vertical line as a reference line, the angle between the contour line of the first sidewall 141 and the reference line can be understood as the opening angle of the flexible groove 140, and the angle between the contour line of the first sidewall 141 and the reference line is α, and satisfies 2 ° ≦ α ≦ 8 °.

Referring to fig. 2, when the first sidewall 141 is not parallel to the second sidewall 142 and the angle of the second sidewall 142 in the axial direction is constant, the opening of the flexible groove 140 is larger and the thickness of the groove wall 150 is smaller as the included angle α is larger. Therefore, to ensure that the slot wall 150 has the proper flexibility and strength, the angle α of the flexible slot 140 is selected to be in the range of 2 ° to 8 °, and is specifically selected according to the practical application requirements, and is preferably between 3 ° and 6 °.

Referring to fig. 4 and 5, the first sidewall 141 and the second sidewall 142 are parallel to each other, the included angles between the first sidewall 141 and the central axis of the second sidewall 142 are equal, and the vertical line is taken as a reference line, and the included angle α between the first sidewall 141 and the vertical line satisfies the requirement that α is greater than or equal to 2 ° and less than or equal to 8 °.

It can be understood that, referring to fig. 1, the height of the bearing body 100 is the distance between the flange surface 111 and the upper end surface of the bearing neck 120, the depth of the flexible groove 140 is the distance between the flange surface 111 and the bottom of the flexible groove 140, and the depth of the flexible groove 140 is proportional to the height of the bearing body 100, that is, the higher the bearing body 100 is, the deeper the flexible groove 140 is, and the depth of the flexible groove 140 is set within a certain range, so that the flexible groove 140 has sufficient flexibility and meets the requirement of strength.

Specifically, as shown in fig. 1 and 2, the height of the bearing body 100 of the upper bearing 1000 is h, the depth of the flexible groove 140 is h1, and in the embodiment, 0.15h ≦ h1 ≦ 0.17h is satisfied, for example, when the height of the upper bearing 1000 is 20mm, the depth of the flexible groove 140 may be h1 ═ 0.15h ≦ 3 mm. The height of the bearing body 100 and the depth of the flexible groove 140 can be set according to the requirements of the actual application, and are not further limited herein.

Referring to fig. 3, the height of the bearing body 100 of the lower bearing 2000 is h, and the depth of the flexible groove 140 is h 1. since the height of the lower bearing 2000 is less than the height of the upper bearing 1000, in the embodiment, the size of the flexible groove 140 of the lower bearing 2000 is different from the flexible groove 140 of the upper bearing 1000. Specifically, the height h of the bearing body 100 and the depth h1 of the flexible groove 140 satisfy 0.38 h-1-0.40 h. For example, when the height of the lower bearing 2000 is 10mm, the depth of the flexible groove 140 may be 0.38h 3.8mm in h 1.

It will be appreciated that, with reference to fig. 1 and 3, in an embodiment, the top 151 of the slot wall 150 is spaced axially from the flange face 111 by a gap, that is, the distance between the root 152 and the flange face 111 is less than the depth of the flexible slot 140. It should be noted that, during the manufacturing process of the crankshaft 500, the relief grooves 510 are formed on the outer side wall of the crankshaft 500, and as shown in fig. 6 and 7, after the crankshaft 500 and the bearing are assembled in place, the relief grooves 510 correspond to the top portions 151 of the groove walls 150, and by forming a gap by spacing the top portions 151 from the flange surface 111, the contact between the relief grooves 510 and the groove walls 150 can be reduced, which affects the thickness of the oil film.

In some embodiments, the axial distance between the top 151 of the groove wall 150 and the flange surface 111 is h2, and the width of the relief groove 510 in the axial direction of the crankshaft 500 is h3, which satisfies h 2-h 3. Specifically, the distance h2 between the top 151 and the flange surface 111 may be set equal to the width h3 of the relief groove 510, so that the top 151 of the groove wall 150 can abut against the edge of the relief groove 510, reducing the influence of the relief groove 510 on the groove wall 150.

It should be noted that, for the rotary compressor, the bearing structure of the above embodiment may be applied to a single-cylinder rotary compressor, and may also be applied to a double-cylinder rotary compressor, and the specific size of the slot wall 150 may be set according to practical application requirements, for example, the depth of the flexible slot 140, the thickness of the top 151 and the root 152 of the slot wall 150, and the like are respectively adjusted according to the upper bearing 1000 and the lower bearing 2000, so as to meet the installation requirements of the upper bearing 1000 and the lower bearing 2000. It can be understood that, by enhancing the strength of the groove wall 150 at the corresponding position at the bottom of the flexible groove 140 of the upper bearing 1000 and the lower bearing 2000, compared with the groove wall structure with uniformly distributed thickness, especially for severe working conditions, the bearing surface pressure can be reduced by 3% -15%, and the abrasion between the crankshaft 500 and the bearing can be effectively reduced, so that the occurrence of the polishing phenomenon can be effectively reduced, and the reliability of the operation of the compressor under severe working conditions can be further improved.

Referring to fig. 1 and 3, in some embodiments, the inner walls of the bearing necks 120 of the upper bearing 1000 and the lower bearing 2000 are respectively provided with an oil groove 122, the oil grooves 122 are spirally arranged along the axial direction, oil is supplied through the oil grooves 122, so that lubricating oil is uniformly distributed, friction between the crankshaft 500 and the bearings is effectively reduced, and the reliability of the operation of the compressor is improved.

A compressor according to an embodiment of the present invention will be described with reference to fig. 6 to 10, which is a rotary compressor, particularly, a twin-cylinder rotary compressor, and the compressor will be described below with reference to a specific example.

Referring to fig. 6, fig. 6 is a schematic sectional view of a pump body assembly in a compressor, the pump body assembly including an upper cylinder 200 and a lower cylinder 300, wherein an upper bearing 1000 is provided at an upper end of the upper cylinder 200, an upper roller 210 is provided in the upper cylinder 200, the upper cylinder 200 is located at an upper end of the lower cylinder 300, and a partition plate 400 is provided between the upper cylinder 200 and the lower cylinder 300; a lower roller 310 is disposed in the lower cylinder 300, a lower bearing 2000 is disposed at the bottom end of the lower cylinder 300, the crankshaft 500 passes through the upper cylinder 200 and the lower cylinder 300, the crankshaft 500 is supported by the upper bearing 1000 and the lower bearing 2000, and the upper end of the crankshaft 500 is connected to a motor assembly (not shown in the drawing). An upper compression cavity is formed in the upper cylinder 200 through the cooperation of the upper bearing 1000 and the partition plate 400 with the upper cylinder 200, and the upper roller 210 is located in the upper compression cavity. The lower bearing 2000 and the partition 400 are matched with the lower cylinder 300, a lower compression cavity is formed in the lower cylinder 300, the lower roller 310 is located in the lower compression cavity, and the structures of the shell, the motor assembly and other parts of the compressor are omitted in the drawing.

Referring to fig. 6 and 7, it can be understood that the flange surfaces 111 of the upper bearing 1000 and the lower bearing 2000 are respectively provided with a flexible groove 140, where the flexible groove 140 of the upper bearing 1000 adopts the structure of the embodiment shown in fig. 1, and the flexible groove 140 of the lower bearing 2000 adopts the structure of the embodiment shown in fig. 3, and specific reference may be made to the description of the above embodiment, and details are not repeated here.

The groove walls 150 of the upper bearing 1000 and the lower bearing 2000 are gradually increased from the opening to the bottom along the axial direction, the strength of the groove wall 150 at the corresponding position at the bottom of the flexible groove 140 is enhanced, the supporting capability of the upper bearing 1000 and the lower bearing 2000 can be further improved relative to the groove wall structure with uniformly distributed thickness, especially for severe working conditions, the surface pressure of the upper bearing 1000 and the lower bearing 2000 can be effectively reduced to 3% -15%, the abrasion between the crankshaft 500 and the upper bearing 1000 and the lower bearing 2000 is effectively reduced, the occurrence of the polishing phenomenon is reduced, and the reliability of the compressor in operation under the severe working conditions is further improved.

Referring to fig. 8, in some embodiments, the flexible groove 140 of the upper bearing 1000 adopts the structure of the embodiment shown in fig. 4, and the flexible groove 140 of the lower bearing 2000 adopts the structure of the embodiment shown in fig. 5, which may specifically refer to the description of the embodiment shown in fig. 4 and 5, and will not be described again here.

Referring to fig. 9, in some embodiments, the flexible groove 140 of the upper bearing 1000 adopts the structure of the embodiment shown in fig. 1, and the flexible groove 140 of the lower bearing 2000 adopts the structure of the embodiment shown in fig. 5, which may specifically refer to the description of the embodiment shown in fig. 1 and 5, and will not be described again here.

Referring to fig. 10, in some embodiments, the flexible groove 140 of the upper bearing 1000 adopts the structure of the embodiment shown in fig. 4, and the flexible groove 140 of the lower bearing 2000 adopts the structure of the embodiment shown in fig. 3, which may specifically refer to the description of the embodiment shown in fig. 3 and 4, and will not be described again here.

In some embodiments, the flexible groove 140 of the upper bearing 1000 adopts the structure of the embodiment shown in fig. 1, the flexible groove of the lower bearing 2000 is a conventional straight annular groove structure, and the thickness of the groove wall is uniformly distributed, that is, the groove wall 150 at the corresponding position at the bottom of the flexible groove 140 of the upper bearing 1000 is reinforced without reinforcing the lower bearing 2000. Alternatively, the flexible groove 140 of the lower bearing 2000 may adopt the structure of the embodiment shown in fig. 3; the flexible groove of the upper bearing 1000 is a conventional straight annular groove structure, the thickness of the groove wall is uniformly distributed, and the groove wall 150 at the corresponding position of the bottom of the flexible groove of the lower bearing 2000 is reinforced without reinforcing the upper bearing 1000.

The embodiment of the invention also provides a refrigeration device (not shown in the attached drawing), wherein the refrigeration device can be an air conditioner, a refrigerator and other household appliances, and the refrigeration device is applied to the compressor of the embodiment. Since the refrigeration equipment adopts all technical solutions of the compressor of the above embodiment, at least all the beneficial effects brought by the technical solutions of the above embodiments are achieved, and no further description is given here.

The embodiments of the present invention have been described in detail with reference to the accompanying drawings, but the present invention is not limited to the above embodiments, and various changes can be made within the knowledge of those skilled in the art without departing from the gist of the present invention.

Claims

1. The bearing of the compressor is characterized in that the bearing is arranged at the axial end part of a cylinder of the compressor, the bearing is provided with a shaft hole for inserting a crankshaft, the end surface of the bearing facing the cylinder is provided with a flexible groove, the flexible groove is arranged around the shaft hole, and an annular groove wall is formed between the flexible groove and the shaft hole;

2. The bearing of claim 1, wherein the slot wall is located at the opening of the flexible slot at a top, the slot wall is located at the bottom of the flexible slot at a root, the top has a thickness of t1, and the root has a thickness of t2, such that: t2 is t1+ Δ t, and Δ t is 0.25mm ≦ Δ t ≦ 1 mm.

3. The bearing of claim 2, wherein the top portion has a thickness t1 satisfying: t1 is not less than 1.25mm and not more than 3.5 mm.

4. The bearing of claim 1, wherein the compliant groove bottom has a width t3 in the radial direction of the bearing, satisfying: t3 is not less than 0.5mm and not more than 2 mm.

5. The bearing of claim 1, wherein a side wall of the flexible groove adjacent to the shaft hole is a first side wall, and a side wall opposite to the first side wall is a second side wall, and the second side wall is disposed parallel to an axis of the shaft hole or parallel to the first side wall.

6. The bearing of claim 5, wherein on the section of the bearing along the axial direction, the included angle between the contour line of the first side wall and the axis of the shaft hole is alpha, and the following conditions are satisfied: alpha is more than or equal to 2 degrees and less than or equal to 8 degrees.

7. The bearing of claim 1, wherein the bearing comprises a flange portion and a bearing neck portion connected to the flange portion, a side of the flange portion facing the cylinder in an axial direction of the bearing neck portion is a flange surface, and the flexible groove is provided on the flange surface.

8. The bearing of claim 7, wherein the distance between the flange face and the bottom of the compliant groove is h1, and the distance between the flange face and the end face of the bearing neck away from the flange face is h, such that: h1 is more than or equal to 0.15h and less than or equal to 0.17h or h1 is more than or equal to 0.38h and less than or equal to 0.40 h.

9. The bearing of claim 7, wherein the slot wall is located at a top of the flexible slot opening, the top being a distance from the flange face that is less than a distance from the flange face to the flexible slot bottom.

10. The bearing of claim 9, wherein the distance between the top portion and the flange surface is h2, and the crankshaft is provided with an undercut having a width in the axial direction of the crankshaft of h3, such that: h 2-h 3.

11. Compressor, characterized in that it comprises a bearing according to any one of claims 1 to 10.

12. Refrigeration appliance, characterized in that it comprises a compressor as claimed in claim 11.