Pump body assembly for compressor and compressor

Abstract

The utility model relates to the technical field of compressors, and discloses a pump body assembly for a compressor. The pump body assembly used for the compressor comprises a crankshaft, a pump body and a pump body, wherein the crankshaft comprises a long shaft and a short shaft; the main bearing sleeves the outer side of the long shaft; the auxiliary bearing sleeves the outer side of the short shaft; wherein the contact length of the main bearing and the long shaft is M, the contact length of the auxiliary bearing and the short shaft is N, and N / M is larger than or equal to 0.6. Compared with the height of the auxiliary bearing in a conventional scheme, the height of the auxiliary bearing is relatively increased due to the fact that the ratio of N / M is larger than or equal to 0.6. By increasing the height of the auxiliary bearing and adjusting the actual contact length ratio of the long shaft and the main bearing and the actual contact length ratio of the short shaft and the auxiliary bearing, the rigidity of the whole bearing system can be improved, the swing amplitude of the crankshaft during high-rotating-speed operation is reduced, and therefore the gaps between the crankshaft and the main bearing and the auxiliary bearing are adjusted, and the minimum oil film thickness is increased; and the risk of oil film breakage caused by crankshaft swinging is reduced. N / M is greater than or equal to 0.6, and the stability of the oil film thickness can be improved when the compressor runs at a high rotating speed. The utility model further discloses the compressor.

Description

Technical Field

[0001] The present application relates to the technical field of compressors, and in particular to a pump body assembly for a compressor and a compressor. Background Art

[0002] At present, with the upgrade of compressors, miniaturization and high speed have become the development direction of compressors. Increasing the maximum operating frequency of the compressor can achieve a smaller displacement and higher cooling capacity. However, when the compressor speed is increased, the oil discharge rate will also increase. The increase in oil discharge rate will lead to a decrease in the refrigerant oil in the compressor, and the lubrication of the friction pair of the pump body cannot be guaranteed, resulting in wear of the friction pair of the pump body.

[0003] The related technology sets a concave annular groove on the long axis portion of the compressor crankshaft, and sets an oil path oil hole in the concave annular groove, so that the main bearing and the crankshaft are fully lubricated during the rotation process. In order to ensure the reliability of the operation of the compressor pump body, the ratio of the height of the concave annular groove to the total height of the shaft diameter of the main bearing is limited, the oil film thickness between the shaft diameter and the long axis portion of the main bearing is increased, the wear between the shaft diameter and the long axis portion due to operation is reduced, and the oil discharge of the compressor is improved.

[0004] In the process of implementing the embodiments of the present disclosure, it is found that there are at least the following problems in the related art:

[0005] Related technologies can introduce oil into the space between the main bearing and the crankshaft through the design of concave ring grooves and oil holes, which can increase the thickness of the oil film to a certain extent and improve the oil discharge of the compressor. However, the stability of the oil film thickness will still be affected when running at high speeds.

[0006] It should be noted that the information disclosed in the above background technology section is only used to enhance the understanding of the background of the present application, and therefore may include information that does not constitute the prior art known to ordinary technicians in the field. Utility Model Content

[0007] In order to provide a basic understanding of some aspects of the disclosed embodiments, a brief summary is given below. The summary is not an extensive review, nor is it intended to identify key / critical components or delineate the scope of protection of these embodiments, but rather serves as a prelude to the detailed description that follows.

[0008] The embodiments of the present disclosure provide a pump body assembly for a compressor and a compressor, so as to improve the stability of the oil film thickness during high-speed operation.

[0009] According to the first aspect of the embodiment of the utility model, a pump body assembly for a compressor is provided, comprising: a crankshaft, including a long shaft and a short shaft; a main bearing, sleeved on the outside of the long shaft; a secondary bearing, sleeved on the outside of the short shaft; wherein the contact length between the main bearing and the long shaft is M, the contact length between the secondary bearing and the short shaft is N, and N / M≥0.6.

[0010] Optionally, the ratio of the contact length M between the main bearing and the major shaft to the contact length N between the secondary bearing and the minor shaft further satisfies: N / M≤0.8.

[0011] Optionally, a contact length M between the main bearing and the major shaft and a contact length N between the secondary bearing and the minor shaft satisfy: M≥35 mm, N≥20 mm.

[0012] Optionally, the contact length M between the main bearing and the major shaft and the contact length N between the secondary bearing and the minor shaft also satisfy: 35 mm ≤ M ≤ 55 mm, 20 mm ≤ N ≤ 30 mm.

[0013] Optionally, the ratio of the contact length M between the main bearing and the major shaft to the contact length N between the secondary bearing and the minor shaft also satisfies: N / M=0.7.

[0014] Optionally, the diameter of the major axis is less than or equal to 15 mm; and / or the diameter of the minor axis is less than or equal to 15 mm.

[0015] According to a second aspect of an embodiment of the utility model, a compressor is provided, comprising a pump body assembly for a compressor as described in any one of the above items.

[0016] Optionally, the compressor comprises a high speed compressor having an operating frequency greater than or equal to 140 Hz.

[0017] Optionally, the compressor also includes: a rotor core, which is sleeved on the outside of the long shaft, located on the side of the main bearing away from the auxiliary bearing, and has a first end face close to the main bearing; wherein the main bearing includes a main bearing neck extending toward the first end face, and the first end face is provided with a clearance groove that is recessed away from the main bearing, the clearance groove is arranged corresponding to the main bearing neck, and the cross-sectional area of ​​the clearance groove is larger than the radial cross-sectional area of ​​the main bearing neck, so that the end of the main bearing neck facing the first end face can be located in the clearance groove.

[0018] Optionally, the main bearing also includes a main bearing base, which is connected to the main bearing neck and extends radially, and is located at one end of the main bearing neck away from the rotor core. The compressor also includes: a shell, which encloses an internal space, including a shell top cover arranged at the end, the rotor core, crankshaft, main bearing and auxiliary bearing are all arranged in the internal space, the crankshaft extends in a direction perpendicular to the shell top cover, and the rotor core, main bearing and auxiliary bearing are sequentially sleeved on the outside of the crankshaft in a direction away from the shell top cover; a stator core, which is arranged in the internal space and sleeved on the outside of the rotor core, includes a second end face arranged toward the shell top cover and a third end face arranged toward the main bearing; wherein the main bearing base has a fourth end face arranged toward the third end face, the distance value between the second end face of the stator core and the inner surface of the shell top cover is A, the distance value between the third end face of the stator core and the fourth end face of the main bearing base is B, the compressor displacement value is Q, 0.11≤A / B / Q≤0.22.

[0019] The pump body assembly for a compressor and the compressor provided in the embodiments of the present disclosure can achieve the following technical effects:

[0020] The disclosed embodiment limits the ratio of the contact length between the secondary bearing and the minor shaft and the contact length between the main bearing and the major shaft to N / M≥0.6. Compared with the height of the secondary bearing in the conventional scheme, the limitation of this ratio relatively increases the height of the secondary bearing. By increasing the height of the secondary bearing and adjusting the actual contact length ratio between the major shaft and the main bearing and between the minor shaft and the secondary bearing, the rigidity of the entire bearing system can be improved and the swing amplitude of the crankshaft when running at high speed can be reduced. By controlling the swing amplitude of the crankshaft, the clearance between the crankshaft and the main bearing and the secondary bearing can be adjusted, thereby increasing the minimum oil film thickness and reducing the risk of oil film rupture caused by crankshaft swing. N / M≥0.6, when the compressor is running at high speed, it can more effectively improve the oil film thickness between the crankshaft and the main bearing and the secondary bearing, improve the stability of the oil film thickness, meet the reliability requirements of the compressor, reduce wear, and extend service life.

[0021] The above general description and the following description are exemplary and explanatory only and are not intended to limit the present application. BRIEF DESCRIPTION OF THE DRAWINGS

[0022] One or more embodiments are exemplarily described by corresponding drawings, which do not limit the embodiments. Elements with the same reference numerals in the drawings are shown as similar elements, and the drawings do not constitute a scale limitation, and wherein:

[0023] Figure 1 is a structural schematic diagram of a pump assembly for a compressor provided by an embodiment of the present disclosure;

[0024] Figure 2 is a schematic structural diagram of a main bearing provided by an embodiment of the present disclosure;

[0025] Figure 3 is a schematic structural diagram of a secondary bearing provided by an embodiment of the present disclosure;

[0026] Figure 4 is a structural schematic diagram of a compressor provided by an embodiment of the present disclosure;

[0027] Figure 5 is a schematic structural diagram of a rotor core provided by an embodiment of the present disclosure;

[0028] Figure 6 is a schematic structural diagram of another main bearing provided by an embodiment of the present disclosure;

[0029] Figure 7 yes Figure 6 An enlarged schematic diagram of section A is shown;

[0030] Figure 8 It is a schematic structural diagram of another auxiliary bearing provided in an embodiment of the present disclosure.

[0031] Reference numerals:

[0032] 10: crankshaft; 11: long shaft; 12: short shaft;

[0033] 20: main bearing; 21: main bearing neck; 22: main bearing base; 221: fourth end surface; 23: first oil guide groove;

[0034] 30: auxiliary bearing; 31: second oil guide groove;

[0035] 40: rotor core; 41: first end surface; 411: clearance groove;

[0036] 50: housing; 51: internal space; 52: housing top cover;

[0037] 60: stator core; 61: second end surface; 62: third end surface;

[0038] 70: Pump body assembly. DETAILED DESCRIPTION

[0039] In order to be able to understand the features and technical contents of the embodiments of the present disclosure in more detail, the implementation of the embodiments of the present disclosure is described in detail below in conjunction with the accompanying drawings. The attached drawings are for reference only and are not used to limit the embodiments of the present disclosure. In the following technical description, for the convenience of explanation, a full understanding of the disclosed embodiments is provided through multiple details. However, one or more embodiments can still be implemented without these details. In other cases, to simplify the drawings, well-known structures and devices can be simplified for display.

[0040] The terms "first", "second", etc. in the specification and claims of the disclosed embodiments and the above-mentioned drawings are used to distinguish similar objects, and are not necessarily used to describe a specific order or sequence. It should be understood that the terms used in this way can be interchanged where appropriate for the disclosed embodiments described herein. In addition, the terms "including" and "having" and any variations thereof are intended to cover non-exclusive inclusions.

[0041] In the embodiments of the present disclosure, the terms "upper", "lower", "inside", "middle", "outside", "front", "back" and the like indicate directions or positional relationships based on the directions or positional relationships shown in the accompanying drawings. These terms are mainly intended to better describe the embodiments of the present disclosure and their embodiments, and are not intended to limit the indicated devices, elements or components to have a specific direction, or to be constructed and operated in a specific direction. Moreover, in addition to being used to indicate directions or positional relationships, some of the above terms may also be used to indicate other meanings. For example, the term "upper" may also be used to indicate a certain dependency or connection relationship in certain circumstances. For those of ordinary skill in the art, the specific meanings of these terms in the embodiments of the present disclosure can be understood according to specific circumstances.

[0042] In addition, the terms "disposed", "connected", and "fixed" should be understood in a broad sense. For example, "connected" can be a fixed connection, a detachable connection, or an integral structure; it can be a mechanical connection, or an electrical connection; it can be a direct connection, or an indirect connection through an intermediate medium, or it can be an internal connection between two devices, elements, or components. For those of ordinary skill in the art, the specific meanings of the above terms in the embodiments of the present disclosure can be understood according to specific circumstances.

[0043] Unless otherwise stated, the term "plurality" means two or more.

[0044] In the embodiment of the present disclosure, the character " / " indicates that the preceding and following objects are in an "or" relationship. For example, A / B indicates: A or B.

[0045] The term "and / or" is a description of the association relationship between objects, indicating that three relationships can exist. For example, A and / or B means: A or B, or, A and B.

[0046] It should be noted that, in the absence of conflict, the embodiments and features in the embodiments of the present disclosure may be combined with each other.

[0047] When the compressor runs at high speed, the crankshaft usually swings. A large swing amplitude will affect the stability of the oil film thickness between the main bearing and the long shaft, and between the secondary bearing and the short shaft.

[0048] In the conventional pump assembly, the contact length between the main bearing and the long shaft is usually set to 40mm, and the contact length between the secondary bearing and the short shaft is usually set to 20mm, with a ratio of 2:1. There are gaps between the main bearing and the long shaft, and between the secondary bearing and the short shaft for oil film flow lubrication. Under high speed conditions, the long shaft portion at the upper end of the crankshaft will swing. The greater the swing amplitude of the upper end of the crankshaft, the stronger the oil film pressure on the gap. For example, the gap between the main bearing and the long shaft or between the secondary bearing and the short shaft is 1mm, that is, the oil film is 1mm. When the crankshaft swings, the crankshaft rotates crookedly, which will reduce the minimum gap to less than 1mm, and the thickness of the minimum oil film will also decrease accordingly. When the swing amplitude increases to 1mm, the oil film becomes 0, and at this time, the main bearing and the long shaft or the secondary bearing and the short shaft form direct metal-to-metal contact, causing wear.

[0049] Combination Figure 1-3 As shown, the embodiment of the present disclosure provides a pump assembly 70 for a compressor, including a crankshaft 10, a main bearing 20 and a secondary bearing 30. The crankshaft 10 includes a long shaft 11 and a short shaft 12; the main bearing 20 is sleeved on the outside of the long shaft 11; the secondary bearing 30 is sleeved on the outside of the short shaft 12; wherein the contact length between the main bearing 20 and the long shaft 11 is M (as shown in FIG. Figure 2 As shown), the contact length between the secondary bearing 30 and the short shaft 12 is N (as shown Figure 3 As shown), N / M ≥ 0.6.

[0050] The embodiment of the present disclosure defines a ratio of the contact length between the secondary bearing 30 and the short shaft 12 and the contact length between the main bearing 20 and the long shaft 11 of N / M≥0.6. Compared with the height of the secondary bearing in conventional solutions, this ratio definition relatively increases the height of the secondary bearing 30.

[0051] By adopting the pump body assembly 70 for a compressor provided by the embodiment of the present disclosure, by increasing the height of the secondary bearing 30 and adjusting the actual contact length ratio between the long shaft 11 and the main bearing 20 and between the short shaft 12 and the secondary bearing 30, the rigidity of the entire bearing system can be improved, and the swing amplitude of the crankshaft 10 during high speed operation can be reduced. By controlling the swing amplitude of the crankshaft 10, the clearance between the crankshaft 10 and the main bearing 20 and the secondary bearing 30 can be adjusted, thereby increasing the minimum oil film thickness and reducing the risk of oil film rupture caused by the swing of the crankshaft 10.

[0052] The embodiments of the present disclosure are mainly aimed at high-speed compressor models.

[0053] When the ratio range of N / M is limited to greater than or equal to 0.6, the contact length between the secondary bearing 30 and the short shaft 12 can be increased, or the contact length between the main bearing 20 and the long shaft 11 can be reduced. Compared with the contact length M between the main bearing 20 and the long shaft 11, the contact length N between the secondary bearing 30 and the short shaft 12 is increased, and the supporting area that the secondary bearing 30 can provide for the short shaft 12 is increased, thereby improving the rigidity and stability of the overall structure. Compared with the contact length N between the secondary bearing 30 and the short shaft 12, the contact length M between the main bearing 20 and the long shaft 11 is reduced, which can prevent the long shaft 11 from deformation or swinging during high-speed operation, thereby ensuring the normal operation of the compressor.

[0054] The disclosed embodiment controls the ratio N / M of the contact length N between the secondary bearing 30 and the short shaft 12 and the contact length M between the main bearing 20 and the long shaft 11 to be ≥0.6. When the compressor is running at a high speed, the swing of the long shaft 11 can be slowed down, and the oil film thickness between the crankshaft 10 and the main bearing 20 and the secondary bearing 30 can be more effectively improved, and the stability of the oil film thickness can be improved, so as to meet the reliability requirements of the compressor, reduce wear, and extend the service life. It can also form a favorable support for the short shaft 12 and improve the overall rigidity of the pump body assembly 70.

[0055] The contact length between the main bearing 20 and the long shaft 11 remains unchanged, and after the contact length between the auxiliary bearing 30 and the short shaft 12 is lengthened, the swing of the crankshaft 10 can be reduced, thereby improving the stability of the oil film thickness. Taking the contact length M between the main bearing 20 and the long shaft 11 as 40 mm as an example, when N / M≥0.6, the contact length between the auxiliary bearing 30 and the short shaft 12 has a value range of N≥24 mm, which can limit the entire crankshaft 10 to have a better swing effect, reduce the swing amplitude, and establish a good oil film between the main bearing 20 and the long shaft 11, and between the auxiliary bearing 30 and the short shaft 12.

[0056] Optionally, combined Figure 1-3 As shown, the ratio of the contact length M between the main bearing 20 and the major shaft 11 and the contact length N between the auxiliary bearing 30 and the minor shaft 12 also satisfies: N / M≤0.8.

[0057] When the ratio range of N / M is limited to less than or equal to 0.8, it is possible to avoid the contact length between the secondary bearing 30 and the short shaft 12 being too long, or to avoid the contact length between the main bearing 20 and the long shaft 11 being too short, thereby ensuring the structural strength of the pump body assembly 70 and enhancing the stability and reliability of the entire bearing system under high-speed operation. It is also possible to make the force distribution of the crankshaft 10 uniform during operation, avoid local excessive stress, thereby reducing wear and fatigue, and extending the service life of the crankshaft 10. Under high-speed operation, it is also possible to avoid heat accumulation at the contact point between the secondary bearing 30 and the short shaft 12.

[0058] Taking the contact length M of the main bearing 20 and the long shaft 11 as 40 mm as an example, when N / M≤0.8, the contact length of the secondary bearing 30 and the short shaft 12 is in the range of N≤32 mm, which can ensure the structural strength of the pump body assembly 70 and reduce the swing amplitude to a certain extent. A good oil film can be established between the main bearing 20 and the long shaft 11, and between the secondary bearing 30 and the short shaft 12.

[0059] The embodiment of the present disclosure limits the oil film thickness to 0.6≤N / M≤0.8, so that the oil film thickness between the main bearing 20 and the major shaft 11 and between the auxiliary bearing 30 and the minor shaft 12 can meet the reliability requirements of the compressor.

[0060] It will be appreciated that the ratio of N / M may be 0.6, 0.65, 0.7, 0.75 and 0.8.

[0061] Optionally, combined Figure 1-3 As shown, the contact length M between the main bearing 20 and the major shaft 11 and the contact length N between the auxiliary bearing 30 and the minor shaft 12 satisfy: M≥35mm, N≥20mm.

[0062] When the ratio of the contact length M between the main bearing 20 and the long shaft 11 and the contact length N between the auxiliary bearing 30 and the short shaft 12 satisfies 0.6≤N / M≤0.8, the contact length values ​​of the main bearing 20 and the long shaft 11 and the contact length values ​​of the auxiliary bearing 30 and the short shaft 12 also reach a certain range, which will achieve a better control effect of oil film stability. If the contact length M between the main bearing 20 and the long shaft 11 or the contact length N between the auxiliary bearing 30 and the short shaft 12 is too small, the contact area is reduced, which will cause the load-bearing capacity of the main bearing 20 or the auxiliary bearing 30 to decrease. The smaller contact area may cause local stress concentration, increasing the risk of damage to the main bearing 20, the auxiliary bearing 30 or the crankshaft 10.

[0063] The contact length M between the main bearing 20 and the major axis 11 provided in the embodiment of the present disclosure is ≥35 mm, the contact length N between the secondary bearing 30 and the minor axis 12 is ≥20 mm, and the ratio of the contact length between the main bearing 20 and the major axis 11 to the contact length between the secondary bearing 30 and the minor axis 12 is 0.6≤N / M≤0.8. The contact length M between the main bearing 20 and the major axis 11 is ≥35 mm, which can increase the contact area between the main bearing 20 and the major axis 11, and the contact length N between the secondary bearing 30 and the minor axis 12 is ≥20 mm, which can increase the contact area between the secondary bearing 30 and the minor axis 12. The increase in the contact area can improve the stability between the two in contact, reduce vibration and noise, and the load can be more evenly distributed on the contact surface, reducing local stress concentration and making the force evenly distributed, thereby extending the service life and improving the reliability of the compressor. A larger support area can also improve the load-bearing capacity and improve the overall performance of the compressor. When M≥35mm and N≥20mm, and 0.6≤N / M≤0.8 is satisfied at the same time, the relative length relationship between the contact length M between the main bearing 20 and the major shaft 11 and the contact length N between the secondary bearing 30 and the minor shaft 12 can be limited, thereby improving the stability of the oil film thickness.

[0064] Optionally, combined Figure 1-3 As shown, the contact length M between the main bearing 20 and the major shaft 11 and the contact length N between the auxiliary bearing 30 and the minor shaft 12 also satisfy: 35 mm ≤ M ≤ 55 mm, 20 mm ≤ N ≤ 30 mm.

[0065] When the contact length M between the main bearing 20 and the long shaft 11 is less than or equal to 55 mm, the friction area between the main bearing 20 and the long shaft 11 can be reduced, so that the contact length between the main bearing 20 and the long shaft 11 is appropriate, which can control the friction resistance during operation, reduce mechanical energy consumption, and reduce the risk of damage to the main bearing 20.

[0066] When the contact length N between the secondary bearing 30 and the short shaft 12 is less than or equal to 30 mm, the friction area between the secondary bearing 30 and the short shaft 12 can be reduced, so that the contact length between the secondary bearing 30 and the short shaft 12 is appropriate, which can control the friction resistance during operation, reduce mechanical energy consumption, and reduce the risk of damage to the secondary bearing 30.

[0067] When 0.6≤N / M≤0.8, 35mm≤M≤55mm can make the contact length between the main bearing 20 and the major shaft 11 within a balanced range of providing good load-bearing capacity and good oil film thickness stability. 20mm≤N≤30mm can make the contact length between the secondary bearing 30 and the minor shaft 12 within a balanced range of providing good load-bearing capacity and good oil film thickness stability.

[0068] It can be understood that the contact length M between the main bearing 20 and the major shaft 11 can be 35mm, 36mm, 40mm, 45mm, 50mm, 54mm and 55mm; the contact length N between the secondary bearing 30 and the minor shaft 12 can be 20mm, 21mm, 23mm, 25mm, 28mm, 29mm and 30mm.

[0069] Optionally, combined Figure 1-3 As shown, the ratio of the contact length M between the main bearing 20 and the major shaft 11 and the contact length N between the auxiliary bearing 30 and the minor shaft 12 also satisfies: N / M=0.7.

[0070] When M≥35mm, N≥20mm, and N / M=0.7, the oil film thickness between the main bearing 20 and the major shaft 11 and between the auxiliary bearing 30 and the minor shaft 12 are relatively uniform and both can be in a fluid lubrication state.

[0071] Optionally, the diameter of the major axis 11 is less than or equal to 15 mm; and / or the diameter of the minor axis 12 is less than or equal to 15 mm.

[0072] The lightweight and miniaturized design of the pump body assembly 70 can adapt to the high-speed operation of the compressor. Setting the diameter of the major axis 11 or the minor axis 12 to be less than or equal to 15 mm can reduce the overall mass of the crankshaft 10. When rotating at high speed, the reduced mass will reduce the centrifugal force, thereby possibly reducing the stress of the crankshaft 10. At the same time, the lighter crankshaft 10 has a smaller moment of inertia, which can change the speed more quickly at high speeds and improve the response speed. This application takes the example that the diameter of the major axis 11 and the diameter of the minor axis 12 are both less than or equal to 15 mm.

[0073] It can be understood that the diameter of the major axis 11 can be 10mm, 11mm, 12mm, 13mm, 14mm, 15mm, etc.; the diameter of the minor axis 12 can be 10mm, 11mm, 12mm, 13mm, 14mm, 15mm, etc.

[0074] Optionally, combined Figure 2 and Figure 6-7 As shown, the main bearing 20 is provided with a first oil guide groove 23 , and the first oil guide groove 23 extends along the axial direction of the main bearing neck 21 .

[0075] The first oil guide groove 23 is provided in the main bearing 20 so that the lubricating oil can be evenly distributed on the entire contact surface of the main bearing 20 , thereby improving the lubrication effect on the main bearing 20 and reducing the risk of wear caused by friction between the main bearing 20 and the crankshaft 10 .

[0076] Optionally, the first oil guiding groove 23 extends in a spiral shape along the axial direction of the main bearing neck 21 .

[0077] The first oil guide groove 23 extends in a spiral shape, which can more effectively guide the lubricating oil to move along a specific path, thereby ensuring that the lubricating oil is evenly distributed to various parts of the main bearing 20 that need lubrication.

[0078] It can be understood that the first oil guiding groove 23 may also extend vertically along the axial direction of the main bearing neck 21 , and the present application does not limit the shape of the first oil guiding groove 23 .

[0079] Optionally, combined Figure 3 and Figure 8 As shown, the auxiliary bearing 30 is provided with a second oil guiding groove 31 , and the second oil guiding groove 31 extends along the axial direction of the auxiliary bearing 30 .

[0080] The second oil guide groove 31 is provided in the auxiliary bearing 30 so that the lubricating oil can be evenly distributed on the entire contact surface of the auxiliary bearing 30 , thereby improving the lubrication effect on the auxiliary bearing 30 and reducing the risk of wear caused by friction between the auxiliary bearing 30 and the crankshaft 10 .

[0081] Optionally, the second oil guiding groove 31 extends vertically along the axial direction of the auxiliary bearing 30 .

[0082] The vertically extending oil guide groove is relatively simple in design and easy to process and maintain. The second oil guide groove 31 extends vertically along the axial direction of the auxiliary bearing 30 and can more directly transport the lubricating oil to the part of the auxiliary bearing 30 that needs lubrication.

[0083] It can be understood that the second oil guiding groove 31 may also extend in a spiral shape along the axial direction of the auxiliary bearing 30 , and the present application does not limit the shape of the second oil guiding groove 31 .

[0084] Combination Figure 4 As shown, an embodiment of the present disclosure provides a compressor, comprising a pump body assembly 70 for a compressor as described in any one of the above items.

[0085] The compressor provided in the embodiment of the present disclosure includes the pump body assembly 70 for the compressor as described in any one of the above items, and thus has all the beneficial effects of the pump body assembly 70 for the compressor as described in any one of the above items, which will not be repeated here.

[0086] Optionally, the compressor comprises a high speed compressor having an operating frequency greater than or equal to 140 Hz.

[0087] The compressor mentioned in the above disclosed embodiment is suitable for a compressor running at a high speed. The operating frequency of the compressor is limited to be greater than or equal to 140 Hz, which can achieve a high speed environment.

[0088] Optionally, the compressor displacement is greater than 12 cm 3 The compressor mentioned in the above disclosed embodiment is suitable for compressors with a displacement greater than 12 cm 3 compressor.

[0089] When the maximum speed of the compressor is greater than or equal to 140Hz and the compressor displacement is greater than 12cm 3 When the diameters of the major axis 11 and the minor axis 12 of the crankshaft 10 are both less than 15 mm, and the ratio of the contact length N between the secondary bearing 30 and the minor axis 12 to the contact length M between the main bearing 20 and the major axis 11 is 0.6≤N / M≤0.8, the oil film thickness of the main bearing 20 and the secondary bearing 30 can be effectively improved, so that the oil film thickness between the main bearing 20 and the major axis 11 and between the secondary bearing 30 and the minor axis 12 can meet the reliability requirements of the compressor, thereby reducing wear and extending service life.

[0090] Under the same test conditions, a simulation experiment was conducted on the compressor using the original scheme and the scheme provided by the embodiment of the present disclosure, and the operating frequency of the compressor was 140Hz. Among them, in the original scheme, the contact length M between the main bearing 20 and the long shaft 11 is 40mm, the contact length N between the secondary bearing 30 and the short shaft 12 is 20mm, and N / M is 0.5. In the scheme provided by the embodiment of the present disclosure, the contact length M between the main bearing 20 and the long shaft 11 is 40mm, the contact length N between the secondary bearing 30 and the short shaft 12 is 25mm, and N / M is 0.625. The specific test data are shown in the following table.

[0091] Test items Original plan Embodiments of the present disclosure Main bearing oil film thickness / mm 0.002 0.005 Auxiliary bearing oil film thickness / mm 0.004 0.006

[0092] It can be seen from the above test data that after adopting the embodiment of the present disclosure, the oil film thickness of the main bearing and the oil film thickness of the auxiliary bearing are effectively increased, thereby improving the lubrication effect of the main bearing and the auxiliary bearing when the compressor runs at a high frequency.

[0093] Optionally, combined Figure 2 and Figure 4-5 As shown, the compressor also includes a rotor core 40, which is sleeved on the outside of the long shaft 11, located on the side of the main bearing 20 away from the auxiliary bearing 30, and has a first end face 41 close to the main bearing 20; wherein the main bearing 20 includes a main bearing neck 21 extending toward the first end face 41, and the first end face 41 is provided with a clearance groove 411 recessed away from the main bearing 20, the clearance groove 411 is arranged corresponding to the main bearing neck 21, and the cross-sectional area of ​​the clearance groove 411 is larger than the radial cross-sectional area of ​​the main bearing neck 21, so that the end of the main bearing neck 21 facing the first end face 41 can be located in the clearance groove 411.

[0094] One end of the main bearing neck 21 facing the first end face 41 is located in the clearance groove 411, which can reduce the space between the main bearing 20 and the rotor core 40, thereby increasing the pressure in the space, improving the flow effect of the refrigerant gas, and thus improving the energy efficiency of the compressor. At the same time, the reduction in the space between the main bearing 20 and the rotor core 40 also helps to achieve the miniaturization of the compressor. The cross-sectional area of ​​the clearance groove 411 is larger than the radial cross-sectional area of ​​the main bearing neck 21, so that there is a gap between the clearance groove 411 and the main bearing neck 21 for the normal operation of the two, thereby avoiding interference between the main bearing neck 21 and the rotor core 40, so that the compressor can operate normally.

[0095] Optionally, combined Figure 2 and Figure 4 As shown, the main bearing 20 also includes a main bearing base 22, which is connected to the main bearing neck 21 and extends radially, and is located at one end of the main bearing neck 21 away from the rotor core 40, a compressor housing 50 and a stator core 60, the housing 50 encloses an internal space 51, including a housing top cover 52 arranged at the end, the rotor core 40, the crankshaft 10, the main bearing 20 and the auxiliary bearing 30 are all arranged in the internal space 51, the crankshaft 10 extends in a direction perpendicular to the housing top cover 52, and the rotor core 40, the main bearing 20 and the auxiliary bearing 30 are sequentially sleeved on the crankshaft 10 in a direction away from the housing top cover 52. Outside; the stator core 60 is arranged in the internal space 51, and is sleeved on the outside of the rotor core 40, including a second end face 61 arranged toward the shell top cover 52 and a third end face 62 arranged toward the main bearing 20; wherein, the main bearing base 22 has a fourth end face 221 arranged toward the third end face 62, the distance value between the second end face 61 of the stator core 60 and the inner surface of the shell top cover 52 is A, the distance value between the third end face 62 of the stator core 60 and the fourth end face 221 of the main bearing base 22 is B, the compressor displacement value is Q, 0.11≤A / B / Q≤0.22.

[0096] The distance between the second end face 61 of the stator core 60 and the inner surface of the housing top cover 52 is as follows: Figure 4 As shown in FIG. 1A , the distance between the third end face 62 of the stator core 60 and the fourth end face 221 of the main bearing base 22 is as shown in FIG. Figure 4 The distance value A between the second end face 61 and the inner surface of the housing top cover 52 and the distance value B between the third end face 62 and the fourth end face 221 are both in mm, and the unit of the compressor displacement value Q is mm 3 .

[0097] The stator core 60 and the rotor core 40 belong to the motor assembly of the compressor, and the main bearing 20 belongs to the pump assembly 70 of the compressor. The compressor is usually placed vertically, and the pump assembly 70, the motor assembly, and the housing top cover 52 are arranged in sequence from bottom to top, and there is space between the three. After the refrigerant gas is discharged from the pump assembly 70, it first flows into the space with a distance value of B between the third end face 62 and the fourth end face 221, and then passes through the air gap of the motor assembly and flows into the space with a distance value of A between the second end face 61 of the upper part of the motor assembly and the inner surface of the housing top cover 52. The volume of these two spaces will affect the circulation effect of the gas in the air gap of the motor assembly.

[0098] The distance value A between the second end face 61 and the inner surface of the housing top cover 52 is used as the spatial distance between the housing top cover 52 and the motor assembly. The distance value B between the third end face 62 and the fourth end face 221 is used as the spatial distance between the motor assembly and the pump body assembly 70.

[0099] Since the cross-sectional areas of the internal space 51 located at the stator core 60 and the main bearing 20 are the same, the ratio of the distance value A between the second end face 61 of the stator core 60 and the inner surface of the shell top cover 52 and the distance value B between the third end face 62 of the stator core 60 and the fourth end face 221 of the main bearing base 22 can be used to represent the volume ratio of the upper and lower spaces of the motor assembly. The larger the volume of the space, the smaller the gas pressure. The ratio of A and B can be used to measure the pressure ratio of the gas flow paths in the two spaces, thereby measuring the smoothness of the fluid flow in the space. In order to make the gas flow smoother, A is made greater than B, so that the gas flows from the lower space of the motor assembly into the air gap of the motor assembly, and then flows into the upper space of the motor assembly, which is equivalent to enlarging the gas flow space, enabling the gas to flow from high pressure to low pressure, reducing flow resistance and improving flow smoothness.

[0100] The displacement value Q of the compressor can be used to represent the volume of the compression chamber of the pump assembly 70, and A / B / Q can be used to measure the volume ratio of the key space passed through the entire refrigerant gas flow path. Within a certain range, the larger the ratio of A / B / Q, the smaller the fluid resistance loss, the smaller the loss, and the higher the energy efficiency of the compressor.

[0101] The housing top cover 52 is provided with an exhaust pipe for the refrigerant gas to flow out. The distance between the second end face 61 and the inner surface of the housing top cover 52 can ensure that the refrigerant gas flows smoothly from the pump body assembly 70 into the air gap of the motor assembly and flows into the upper space of the motor assembly, while also requiring a certain pressure to allow the refrigerant gas to flow from the upper space into the exhaust pipe and thus flow out of the internal space 51 of the housing 50. When 0.11≤A / B / Q≤0.22, the smoothness of the gas flow in the internal space 51 can be improved while ensuring the flow effect of the gas flowing out of the exhaust pipe.

[0102] It will be appreciated that the ratio of A / B / Q may be 0.11, 0.15, 0.18, 0.20 and 0.22.

[0103] The above description and the accompanying drawings sufficiently illustrate the embodiments of the present disclosure to enable those skilled in the art to practice them. Other embodiments may include structural and other changes. The embodiments represent only possible variations. Unless explicitly required, individual components and functions are optional, and the order of operations may vary. Portions and features of some embodiments may be included in or replace portions and features of other embodiments. The embodiments of the present disclosure are not limited to the structures described above and shown in the accompanying drawings, and various modifications and changes may be made without departing from the scope thereof. The scope of the present disclosure is limited only by the appended claims.

Claims

1. A pump assembly for a compressor, characterized in that: include: Crankshaft, including major and minor shafts; The main bearing is sleeved on the outside of the long shaft; Auxiliary bearing, sleeved on the outside of the short shaft; Among them, the contact length between the main bearing and the major shaft is M, the contact length between the secondary bearing and the minor shaft is N, and N / M≥0.

6.

2. The pump assembly for a compressor according to claim 1, characterized in that: The ratio of the contact length M between the main bearing and the major shaft to the contact length N between the auxiliary bearing and the minor shaft also satisfies: N / M≤0.

8.

3. The pump assembly for a compressor according to claim 2, characterized in that: The contact length M between the main bearing and the major shaft and the contact length N between the secondary bearing and the minor shaft satisfy: M ≥ 35 mm, N ≥ 20 mm.

4. The pump assembly for a compressor according to claim 3, characterized in that: The contact length M between the main bearing and the major shaft and the contact length N between the auxiliary bearing and the minor shaft also satisfy: 35mm≤M≤55mm, 20mm≤N≤30mm.

5. The pump assembly for a compressor according to claim 3, characterized in that: The ratio of the contact length M between the main bearing and the major shaft to the contact length N between the secondary bearing and the minor shaft also satisfies: N / M=0.

7.

6. The pump assembly for a compressor according to any one of claims 1 to 5, characterized in that: The diameter of the major axis is less than or equal to 15 mm; and / or, The diameter of the minor axis is less than or equal to 15 mm.

7. A compressor, characterized in that: The invention comprises a pump body assembly for a compressor according to any one of claims 1 to 6.

8. The compressor according to claim 7, characterized in that The compressor includes a high speed compressor that can operate at a frequency greater than or equal to 140 Hz.

9. The compressor according to any one of claims 7 or 8, characterized in that: Also includes: The rotor core is sleeved on the outside of the long shaft, located on the side of the main bearing away from the auxiliary bearing, and has a first end surface close to the main bearing; Among them, the main bearing includes a main bearing neck extending toward the first end face, and the first end face is provided with a clearance groove recessed away from the main bearing. The clearance groove is arranged corresponding to the main bearing neck, and the cross-sectional area of ​​the clearance groove is larger than the radial cross-sectional area of ​​the main bearing neck, so that the end of the main bearing neck facing the first end face can be located in the clearance groove.

10. The compressor according to claim 9, characterized in that The main bearing further includes a main bearing base body connected to the main bearing neck and extending radially, and located at an end of the main bearing neck away from the rotor core. The compressor further includes: The housing encloses an internal space, including a housing top cover arranged at the end, the rotor core, the crankshaft, the main bearing and the auxiliary bearing are all arranged in the internal space, the crankshaft extends in a direction perpendicular to the housing top cover, and the rotor core, the main bearing and the auxiliary bearing are sequentially sleeved on the outer side of the crankshaft in a direction away from the housing top cover; The stator core is arranged in the internal space and is sleeved on the outside of the rotor core, including a second end face arranged toward the shell top cover and a third end face arranged toward the main bearing; wherein the main bearing base has a fourth end face arranged toward the third end face, the distance value between the second end face of the stator core and the inner surface of the shell top cover is A, the distance value between the third end face of the stator core and the fourth end face of the main bearing base is B, the compressor displacement value is Q, 0.11≤A / B / Q≤0.22.

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