A bearing structure, a pump body assembly and a compressor

Abstract

The utility model relates to a kind of bearing structure, pump body assembly and compressor, bearing structure includes bearing seat, one end middle part of the bearing seat extends shaft journal along its axial direction, the bearing seat and the shaft journal are opened with the bearing channel for the shaft of crankshaft to be set in along axial direction;Several lubricating oil grooves are recessed on the inner circumferential wall of the bearing channel, several the lubricating oil grooves are evenly distributed on the inner circumferential wall of the bearing channel;The two ends of the lubricating oil groove are respectively penetrated the axial both ends of the bearing channel, the groove depth of the lubricating oil groove is h, the thickness of the shaft journal is T, satisfy relationship: 0.02T≤h≤0.3T.The bearing structure, pump body assembly and compressor of the utility model, by several lubricating oil grooves evenly distributed in bearing channel, make the whole inner circumferential wall of bearing channel easily form oil film, to reduce friction, wear and tear etc., and can improve the circulation efficiency of refrigeration oil, improve the service life of part.

Description

Technical Field

[0001] This utility model relates to the field of compressor technology, and in particular to a bearing structure, a pump assembly, and a compressor. Background Technology

[0002] A rotary compressor uses a motor to drive a crankshaft, which in turn drives a piston via an eccentric part on the crankshaft to compress refrigerant gas. To ensure stable high-speed crankshaft rotation, bearings are installed at both ends of the cylinder assembly to support the cylinders. The clearance fit between the two bearings and the crankshaft ensures stable high-speed rotation. To reduce friction between the crankshaft and bearings, lubricating oil is frequently added. Traditional lubrication methods rely on injecting lubricating oil, which is simple and easy to operate. However, under high-speed operation and complex stress distribution, it is difficult to ensure a uniform distribution of the lubricating oil film across the entire contact surface between the crankshaft and bearings. This can lead to insufficient lubrication in some areas, increasing the risk of localized friction and wear, and ultimately shortening the service life of the bearings and crankshaft. Utility Model Content

[0003] Based on this, the purpose of this utility model is to overcome the shortcomings of the prior art and provide a bearing structure, pump body assembly and compressor. By evenly distributing several lubricating oil grooves in the bearing channel, an oil film can be easily formed on the entire inner circumferential wall of the bearing channel, thereby reducing friction and wear, improving the circulation efficiency of refrigeration oil and increasing the service life of the components.

[0004] To achieve the above objectives, the first aspect of this utility model provides a bearing structure, including a bearing housing, a journal extending axially from the middle of one end of the bearing housing, and a bearing channel for a crankshaft to pass through the bearing housing and the journal in the axial direction; a plurality of lubricating oil grooves are recessed on the inner peripheral wall of the bearing channel, and the plurality of lubricating oil grooves are evenly distributed on the inner peripheral wall of the bearing channel; the two ends of the lubricating oil grooves respectively penetrate the two axial ends of the bearing channel, the groove depth of the lubricating oil grooves is h, and the thickness of the journal is T, satisfying the relationship: 0.02T≤h≤0.3T.

[0005] Therefore, according to the bearing structure of this utility model, by uniformly distributing a number of lubricating oil grooves on the inner circumferential wall of the bearing channel, and ensuring that the two ends of each lubricating oil groove penetrate the axial ends of the bearing channel respectively, and by limiting the relationship between the groove depth h of each lubricating oil groove and the thickness T of the journal to 0.02T≤h≤0.3T, the rigidity and strength of the bearing part are ensured while avoiding the problem of structural fragility caused by excessively deep grooves. At the same time, by uniformly distributing a number of lubricating oil grooves on the inner circumferential wall of the bearing channel, the circulation of refrigeration oil can be promoted, and an oil film can be easily formed on the entire inner circumferential wall of the bearing channel. This effectively avoids adverse phenomena such as local friction and wear in the bearing channel, improves the lubrication effect between the bearing channel and the crankshaft, thereby reducing wear between the bearing structure and the crankshaft, extending the service life of the bearing structure, and thus improving the operating efficiency, stability and reliability of the compressor.

[0006] In one embodiment, the width of the lubricating oil groove is d, and the inner diameter of the bearing channel is D, satisfying the relationship: π*D / 1000≤d≤π*D / 50. Therefore, according to the bearing structure of this utility model, by limiting the relationship between the width d of the lubricating oil groove and the inner diameter D of the bearing channel to π*D / 1000≤d≤π*D / 50, the flow resistance of the refrigeration oil is moderate, avoiding the lubricating oil groove being too narrow, affecting its flow rate, or too wide, reducing the rigidity of the bearing channel.

[0007] In one implementation, the distance between two adjacent lubricating oil grooves is S, satisfying the relationship: 3d≤S≤8d. Therefore, according to the bearing structure of this invention, by limiting the relationship between the distance S between two adjacent lubricating oil grooves and the groove width d to 3d≤S≤8d, it prevents the two adjacent lubricating oil grooves from being too close together, leading to insufficient rigidity of the bearing channel, or too sparse, leading to insufficient lubrication.

[0008] In one embodiment, the groove depth h of the lubricating oil groove and the thickness T of the journal satisfy the following relationship: 0.1T≤h≤0.3T.

[0009] In one embodiment, the lubricating oil groove is wavy in shape, and the bearing channel is divided into a low-stress zone and a high-stress zone along the axial direction; the interval between two adjacent lubricating oil grooves in the low-stress zone is S1, satisfying the relationship: 3d≤S≤5d; the interval between two adjacent lubricating oil grooves in the high-stress zone is S2, satisfying the relationship: 5d≤S≤8d.

[0010] In one embodiment, the lubricating oil groove is spiral in shape.

[0011] In one embodiment, several of the lubricating oil grooves intersect on the inner peripheral wall of the bearing channel to form a mesh channel.

[0012] In one embodiment, the area occupied by a plurality of the lubricating oil grooves on the inner peripheral wall of the bearing channel is less than or equal to 25% of the area of ​​the inner peripheral wall of the bearing channel.

[0013] A second aspect of this utility model provides a pump body assembly, which includes the bearing structure described in any one of the preceding claims. According to the pump body assembly of this utility model, by uniformly distributing a plurality of lubricating oil grooves within the bearing channel, an oil film is easily formed on the entire inner circumferential wall of the bearing channel, thereby reducing friction and wear, improving the circulation efficiency of the refrigeration oil, and extending the service life of the component.

[0014] A third aspect of this utility model provides a compressor comprising the bearing structure described in any one of the preceding claims. According to this utility model, the compressor, by uniformly distributing a plurality of lubricating oil grooves within the bearing channel, facilitates the formation of an oil film on the entire inner circumferential wall of the bearing channel, thereby reducing friction and wear, improving the circulation efficiency of the refrigeration oil, and extending the service life of the components.

[0015] To better understand and implement this invention, the following detailed description is provided in conjunction with the accompanying drawings. Attached Figure Description

[0016] Figure 1 This is one of the structural schematic diagrams of the bearing structure according to an embodiment of the present utility model;

[0017] Figure 2 for Figure 1 A cross-sectional schematic diagram of the bearing structure shown;

[0018] Figure 3 This is a second schematic diagram of the bearing structure according to an embodiment of the present utility model;

[0019] Figure 4 for Figure 3 A cross-sectional schematic diagram of the bearing structure shown;

[0020] Figure 5 This is the third schematic diagram of the bearing structure according to an embodiment of the present utility model;

[0021] Figure 6 for Figure 5 A cross-sectional schematic diagram of the bearing structure shown;

[0022] Figure 7 This is a schematic diagram of the pump body assembly according to an embodiment of the present invention;

[0023] Figure 8 This is one of the partial cross-sectional schematic diagrams of the pump body assembly according to an embodiment of the present utility model;

[0024] Figure 9 This is a second partial cross-sectional schematic diagram of the pump body assembly according to an embodiment of the present utility model;

[0025] Figure 10 This is the third partial cross-sectional schematic diagram of the pump body assembly according to an embodiment of the present utility model.

[0026] Explanation of reference numerals in the attached drawings: 10, bearing housing; 11, journal; 12, bearing channel; 13, lubricating oil groove; 20, cylinder; 30, lower bearing; 40, crankshaft. Detailed Implementation

[0027] To make the objectives, technical solutions, and advantages of this application clearer, the present invention will be further described in detail below with reference to the accompanying drawings. It should be understood that the described embodiments are merely some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0028] The terminology used in this invention is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. The singular forms “a,” “the,” and “the” used in this invention and the appended claims are also intended to include the plural forms unless the context clearly indicates otherwise. It should also be understood that the term “and / or” as used herein refers to and includes any or all possible combinations of one or more of the associated listed items.

[0029] In the following description, when referring to the accompanying drawings, unless otherwise indicated, the same numbers in different drawings represent the same or similar elements. The embodiments described in the following exemplary embodiments do not represent all embodiments consistent with this application. Rather, they are merely examples of apparatuses and methods consistent with some aspects of this application as detailed in the appended claims. In the description of this application, it should be understood that the terms "first," "second," "third," etc., are used only to distinguish similar objects and are not necessarily used to describe a specific order or sequence, nor should they be construed as indicating or implying relative importance. Those skilled in the art can understand the specific meaning of the above terms in this application according to the specific circumstances.

[0030] In related technologies, a rotary compressor uses a motor to drive a crankshaft to rotate, and an eccentric part on the crankshaft drives a piston to compress refrigerant gas, thus achieving the effect of compressing the refrigerant gas. To ensure stable high-speed rotation of the crankshaft, bearings are installed at both ends of the cylinder assembly to support the cylinders. The clearance fit between the two bearings and the crankshaft ensures stable high-speed rotation. To reduce friction between the crankshaft and bearings, lubricating oil is frequently added. Traditional lubrication methods mainly rely on injecting lubricating oil. Although this method is simple and easy to operate, under high-speed operation and complex stress distribution, it is difficult to ensure that the lubricating oil film is evenly distributed across the entire contact surface between the crankshaft and bearings. This leads to insufficient lubrication in some areas, increasing the risk of localized friction and wear, and ultimately shortening the service life of the bearings and crankshaft.

[0031] In view of this, the present invention provides a bearing structure, a pump assembly, and a compressor. According to the bearing structure, pump assembly, and compressor of the present invention, by uniformly distributing a plurality of lubricating oil grooves 13 within the bearing channel 12, an oil film is easily formed on the entire inner circumferential wall of the bearing channel 12, thereby reducing friction and wear, improving the circulation efficiency of the refrigeration oil, and increasing the service life of the components.

[0032] Please see Figures 1 to 10 The first aspect of this utility model provides a bearing structure, including a bearing housing 10, a journal 11 extending axially from the middle of one end of the bearing housing 10, and a bearing channel 12 for a crankshaft 40 to pass through the bearing housing 10 and the journal 11 axially; a plurality of lubricating oil grooves 13 are recessed on the inner peripheral wall of the bearing channel 12, and the plurality of lubricating oil grooves 13 are evenly distributed on the inner peripheral wall of the bearing channel 12; the two ends of the lubricating oil grooves 13 respectively penetrate the two axial ends of the bearing channel 12, the groove depth of the lubricating oil grooves 13 is h, and the thickness of the journal 11 is T, satisfying the relationship: 0.02T≤h≤0.3T.

[0033] Therefore, according to the bearing structure of this utility model, by uniformly distributing a plurality of lubricating oil grooves 13 on the inner peripheral wall of the bearing channel 12, and by ensuring that the two ends of each lubricating oil groove 13 penetrate the axial ends of the bearing channel 12 respectively, and by limiting the relationship between the groove depth h of each lubricating oil groove 13 and the thickness T of the journal 11 to 0.02T≤h≤0.3T, the rigidity and strength of the bearing part are ensured while avoiding the problem of structural fragility caused by excessively deep grooves of the lubricating oil grooves 13. At the same time, by uniformly distributing a plurality of lubricating oil grooves 13 on the inner peripheral wall of the bearing channel 12, the circulation of refrigeration oil can be promoted, and an oil film can be easily formed on the entire inner peripheral wall of the bearing channel 12. This effectively avoids adverse phenomena such as local friction and wear in the bearing channel 12, improves the lubrication effect between the bearing channel 12 and the crankshaft 40, thereby reducing the wear between the bearing structure and the crankshaft 40, extending the service life of the bearing structure, and thus improving the operating efficiency, stability and reliability of the compressor.

[0034] Furthermore, in this embodiment of the present invention, the width of the lubricating oil groove 13 is d, and the inner diameter of the bearing channel 12 is D, satisfying the relationship: π*D / 1000≤d≤π*D / 50. This can be understood as follows: according to the bearing structure of this embodiment of the present invention, by limiting the relationship between the width d of the lubricating oil groove 13 and the inner diameter D of the bearing channel 12 to π*D / 1000≤d≤π*D / 50, the flow resistance of the refrigeration oil is moderate, preventing the lubricating oil groove 13 from being too narrow and affecting its flow rate, or too wide and reducing the rigidity of the bearing channel 12.

[0035] Furthermore, in this embodiment of the present invention, the area occupied by the plurality of lubricating oil grooves 13 on the inner peripheral wall of the bearing channel 12 is less than or equal to 25% of the area of ​​the inner peripheral wall of the bearing channel 12. It can be understood that, according to the bearing structure of this embodiment of the present invention, by limiting the area ratio of the plurality of lubricating oil grooves 13 to 25% or less, the adverse phenomenon of stress concentration inside the bearing channel 12 can be prevented.

[0036] Optionally, in some embodiments of this utility model, the groove depth h of the lubricating oil groove 13 and the thickness T of the journal 11 satisfy the relationship: 0.1T≤h≤0.3T. This can be understood as follows: in these embodiments, by further limiting the relationship between the groove depth h of the lubricating oil groove 13 and the thickness T of the journal 11 to 0.1T≤h≤0.3T, the rigidity and strength of the bearing portion are ensured while avoiding the problem of structural fragility caused by excessively deep grooves in the lubricating oil groove 13.

[0037] Optionally, in some embodiments of this utility model, the distance between two adjacent lubricating oil grooves 13 is S, satisfying the relationship: 3d≤S≤8d. Therefore, according to the bearing structure of this utility model, by limiting the relationship between the distance S between two adjacent lubricating oil grooves 13 and the groove width d to 3d≤S≤8d, it prevents the two adjacent lubricating oil grooves 13 from being too close together, leading to insufficient rigidity of the bearing channel 12, or too sparse, leading to insufficient lubrication effect.

[0038] Optionally, in some embodiments of this utility model, the distance between two adjacent lubricating oil grooves 13 is S, satisfying the relationship: 3d≤S≤8d. This can be understood as follows: in these embodiments, by limiting the relationship between the distance S between two adjacent lubricating oil grooves 13 and the groove width d to 3d≤S≤8d, it prevents the two adjacent lubricating oil grooves 13 from being too close together, resulting in insufficient rigidity of the bearing channel 12, or too sparse, resulting in insufficient lubrication.

[0039] Optionally, in some embodiments of this utility model, the lubricating oil groove 13 is wavy in shape, and the bearing channel 12 is divided into a low-stress area and a high-stress area along the axial direction; the interval between two adjacent lubricating oil grooves 13 in the low-stress area is S1, satisfying the relationship: 3d≤S≤5d; the interval between two adjacent lubricating oil grooves 13 in the high-stress area is S2, satisfying the relationship: 5d≤S≤8d.

[0040] Optionally, in some embodiments of this utility model, the lubricating oil groove 13 is spiral in shape.

[0041] Optionally, in some embodiments of the present invention, a plurality of lubricating oil grooves 13 intersect on the inner peripheral wall of the bearing channel 12 to form a mesh channel.

[0042] The following is combined Figure 1 and Figure 2 The following is a detailed description of a specific embodiment of the bearing structure according to the present invention. It is worth understanding that the following is merely an illustrative description and should not be construed as limiting the present invention.

[0043] This embodiment provides a bearing structure, including a bearing housing 10, with a journal 11 extending axially from the middle of one end of the bearing housing 10. A bearing channel 12 for a crankshaft 40 to pass through is formed through the bearing housing 10 and the journal 11 axially. A plurality of lubricating oil grooves 13 are recessed on the inner peripheral wall of the bearing channel 12, and the plurality of lubricating oil grooves 13 are evenly distributed on the inner peripheral wall of the bearing channel 12. The two ends of the lubricating oil grooves 13 respectively penetrate the two axial ends of the bearing channel 12. The groove depth of the lubricating oil grooves 13 is h, and the thickness of the journal 11 is T, satisfying the relationship: 0.02T≤h≤0.3T.

[0044] Furthermore, in this embodiment, the width of the lubricating oil groove 13 is d, and the inner diameter of the bearing channel 12 is D, satisfying the relationship: π*D / 1000≤d≤π*D / 50; in addition, in this embodiment, the area occupied by the lubricating oil grooves 13 on the inner peripheral wall of the bearing channel 12 is less than or equal to 25% of the area of ​​the inner peripheral wall of the bearing channel 12.

[0045] In this embodiment, the lubricating oil groove 13 is spiral in shape. The distance between two adjacent lubricating oil grooves 13 is S, which satisfies the relationship: 3d≤S≤8d.

[0046] The following is combined Figure 3 and Figure 4 The following is a detailed description of a specific embodiment of the bearing structure according to the present invention. It is worth understanding that the following is merely an illustrative description and should not be construed as limiting the present invention.

[0047] This embodiment provides a bearing structure, including a bearing housing 10, with a journal 11 extending axially from the middle of one end of the bearing housing 10. A bearing channel 12 for a crankshaft 40 to pass through is formed through the bearing housing 10 and the journal 11 axially. A plurality of lubricating oil grooves 13 are recessed on the inner peripheral wall of the bearing channel 12, and the plurality of lubricating oil grooves 13 are evenly distributed on the inner peripheral wall of the bearing channel 12. The two ends of the lubricating oil grooves 13 respectively penetrate the two axial ends of the bearing channel 12. The groove depth of the lubricating oil grooves 13 is h, and the thickness of the journal 11 is T, satisfying the relationship: 0.02T≤h≤0.3T.

[0048] Furthermore, in this embodiment, the width of the lubricating oil groove 13 is d, and the inner diameter of the bearing channel 12 is D, satisfying the relationship: π*D / 1000≤d≤π*D / 50; in addition, in this embodiment, the area occupied by the lubricating oil grooves 13 on the inner peripheral wall of the bearing channel 12 is less than or equal to 25% of the area of ​​the inner peripheral wall of the bearing channel 12.

[0049] In this embodiment, the lubricating oil groove 13 is wavy in shape, and the bearing channel 12 is divided into a low-stress area and a high-stress area along the axial direction; the interval between two adjacent lubricating oil grooves 13 in the low-stress area is S1, which satisfies the relationship: 3d≤S≤5d; the interval between two adjacent lubricating oil grooves 13 in the high-stress area is S2, which satisfies the relationship: 5d≤S≤8d.

[0050] The following is combined Figure 5 and Figure 6 The following is a detailed description of a specific embodiment of the bearing structure according to the present invention. It is worth understanding that the following is merely an illustrative description and should not be construed as limiting the present invention.

[0051] This embodiment provides a bearing structure, including a bearing housing 10, with a journal 11 extending axially from the middle of one end of the bearing housing 10. A bearing channel 12 for a crankshaft 40 to pass through is formed through the bearing housing 10 and the journal 11 axially. A plurality of lubricating oil grooves 13 are recessed on the inner peripheral wall of the bearing channel 12, and the plurality of lubricating oil grooves 13 are evenly distributed on the inner peripheral wall of the bearing channel 12. The two ends of the lubricating oil grooves 13 respectively penetrate the two axial ends of the bearing channel 12. The groove depth of the lubricating oil grooves 13 is h, and the thickness of the journal 11 is T, satisfying the relationship: 0.02T≤h≤0.3T.

[0052] Furthermore, in this embodiment, the width of the lubricating oil groove 13 is d, and the inner diameter of the bearing channel 12 is D, satisfying the relationship: π*D / 1000≤d≤π*D / 50; in addition, in this embodiment, the area occupied by the lubricating oil grooves 13 on the inner peripheral wall of the bearing channel 12 is less than or equal to 25% of the area of ​​the inner peripheral wall of the bearing channel 12.

[0053] In this embodiment, a plurality of lubricating oil grooves 13 intersect on the inner peripheral wall of the bearing channel 12 to form a mesh channel, and the mesh of the mesh channel is diamond-shaped.

[0054] like Figures 7 to 10 As shown, a second aspect of this utility model provides a pump body assembly, which includes the bearing structure of any of the above-mentioned components, and further includes a cylinder 20, a lower bearing 30, and a crankshaft 40. The bearing structure and the lower bearing 30 are respectively disposed on both axial ends of the cylinder 20, and the crankshaft 40 is sequentially disposed through the bearing structure, the cylinder 20, and the lower bearing 30. According to the pump body assembly of this utility model, by uniformly distributing a plurality of lubricating oil grooves 13 within the bearing channel 12, an oil film is easily formed on the entire inner circumferential wall of the bearing channel 12, thereby reducing friction and wear, improving the circulation efficiency of the refrigeration oil, and increasing the service life of the component.

[0055] A third aspect of this utility model provides a compressor that includes the bearing structure described above. According to this utility model, by uniformly distributing a plurality of lubricating oil grooves 13 within the bearing channel 12, an oil film is easily formed on the entire inner circumferential wall of the bearing channel 12, thereby reducing friction and wear, improving the circulation efficiency of the refrigeration oil, and extending the service life of the components.

[0056] The above embodiments only illustrate several implementation methods of this utility model, and their descriptions are relatively specific and detailed. However, they should not be construed as limiting the scope of the bearing structure, pump body assembly, and compressor of this utility model. It should be noted that those skilled in the art can make several modifications and improvements without departing from the concept of this utility model, and these all fall within the protection scope of this utility model.

Claims

1. A bearing structure, characterized in that: The bearing includes a bearing housing, with a journal extending axially from the middle of one end of the bearing housing. A bearing channel is formed through the bearing housing and the journal in the axial direction for the crankshaft to pass through. A plurality of lubricating oil grooves are recessed on the inner peripheral wall of the bearing channel, and these grooves are evenly distributed on the inner peripheral wall. The two ends of each lubricating oil groove penetrate the axial ends of the bearing channel. The groove depth is h, and the thickness of the journal is T, satisfying the relationship: 0.02T≤h≤0.3T.

2. The bearing structure according to claim 1, characterized in that: The width of the lubricating oil groove is d, and the inner diameter of the bearing channel is D, satisfying the relationship: π*D / 1000≤d≤π*D / 50.

3. The bearing structure according to claim 2, characterized in that: The distance between two adjacent lubricating oil grooves is S, which satisfies the relationship: 3d≤S≤8d.

4. The bearing structure according to claim 1, characterized in that: The groove depth h of the lubricating oil groove and the thickness T of the journal satisfy the following relationship: 0.1T≤h≤0.3T.

5. The bearing structure according to claim 3, characterized in that: The lubricating oil groove is wavy in shape, and the bearing channel is divided into a low-stress zone and a high-stress zone along the axial direction; the interval between two adjacent lubricating oil grooves in the low-stress zone is S1, satisfying the relationship: 3d≤S≤5d; the interval between two adjacent lubricating oil grooves in the high-stress zone is S2, satisfying the relationship: 5d≤S≤8d.

6. The bearing structure according to claim 1, characterized in that: The lubricating oil groove is spiral in shape.

7. The bearing structure according to claim 1, characterized in that: Several of the aforementioned lubricating oil grooves intersect on the inner peripheral wall of the bearing channel to form a mesh-like channel.

8. The bearing structure according to claim 7, characterized in that: The area occupied by several of the lubricating oil grooves on the inner peripheral wall of the bearing channel is less than or equal to 25% of the area of ​​the inner peripheral wall of the bearing channel.

9. A pump body assembly, characterized in that: The bearing structure includes any one of claims 1 to 8, and further includes a crankshaft passing through the bearing channel.

10. A compressor, characterized in that: Includes the pump body assembly as shown in claim 9.

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