Compressor pump body and compressor

Abstract

The compressor pump body comprises a crankshaft and a compression mechanism, the crankshaft is provided with an eccentric section and an oil supply channel, a first oil groove and a concave part are concavely arranged on the peripheral surface, away from the axis of the crankshaft, of the eccentric section in the radial direction of the crankshaft, the first oil groove communicates with the oil supply channel, and a second oil groove communicates with the concave part in the circumferential direction of the crankshaft. The sunken part is located on at least one side of the first oil groove and communicates with the first oil groove; the compression mechanism comprises an air cylinder, a roller and a lower bearing, the lower bearing is connected to the air cylinder, one end of the crankshaft penetrates through the air cylinder and is sleeved with the lower bearing, the eccentric section is located in the air cylinder, the roller is sleeved with the eccentric section, and an oil storage space is formed by the roller, the first oil groove and the sunken part; a straight oil groove is formed in the lower bearing in the axial direction of the crankshaft in a penetrating mode, and the straight oil groove communicates with the oil storage space. The problem that the oil discharge pressure of a compressor pump body is large due to the fact that the lower bearing is difficult to have low machining cost and high oil discharge speed at the same time is solved.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of refrigeration equipment, in particular to a compressor pump body and a compressor. BACKGROUND

[0002] At present, the compressor pump body (such as the pump body of a rotary compressor) usually comprises a crankshaft, a cylinder assembly, and upper and lower bearings. Among them, the lower bearing can not only support the far end of the crankshaft penetrating through the cylinder assembly, but also is provided with an oil groove in communication with the roller inner cavity of the cylinder assembly to discharge the oil in the roller inner cavity through the oil groove. However, the existing lower bearing is difficult to have both low processing cost and high oil discharge speed, resulting in large oil discharge pressure of the compressor pump body, and low overall working performance of the rotary compressor. CONTENT OF THE UTILITY MODEL

[0003] The main purpose of the present application is to provide a compressor pump body and a compressor to solve the problem that the lower bearing in the background art is difficult to have both low processing cost and high oil discharge speed, resulting in large oil discharge pressure of the compressor pump body.

[0004] According to one aspect of the present application, a compressor pump body is provided, comprising:

[0005] a crankshaft, the crankshaft being provided with an eccentric section and an oil supply channel, along the radial direction of the crankshaft, the eccentric section being recessed with a first oil groove and a recess on the outer peripheral surface away from the crankshaft axis, the first oil groove being in communication with the oil supply channel, along the circumferential direction of the crankshaft, the recess being located on at least one side of the first oil groove and in communication with the first oil groove;

[0006] a compression mechanism, the compression mechanism comprising a cylinder, a roller, and a lower bearing, the lower bearing being connected to the cylinder, one end of the crankshaft penetrating through the cylinder and being sleeved with the lower bearing, the eccentric section being located in the cylinder, the roller being sleeved on the eccentric section and surrounding the first oil groove and the recess to form an oil storage space;

[0007] wherein, along the axial direction of the crankshaft, a straight oil groove is provided in the lower bearing, the straight oil groove being in communication with the oil storage space.

[0008] Further, the outer peripheral surface of the eccentric section is located in the region of the first oil groove and the recess as a first circular arc surface, the first circular arc surface has a first center, the radius of the first circular arc surface is R, along the radial direction of the first circular arc surface, the first distance from the surface of the recess away from the first center to the first center is L, L is less than R, and along the direction close to the first oil groove, L gradually decreases.

[0009] Further, the recess is a second circular arc surface adjacent to the first circular arc surface and the first oil groove, and the second circular arc surface is a convex arc surface protruding outward in a direction away from the first center.

[0010] Further, along the axial direction of the crankshaft, the second circular arc surface extends from one end of the eccentric section close to the lower bearing to one end away from the lower bearing.

[0011] Further, the radius of the first circular arc surface and the first distance satisfy the following relationship:

[0012] 0.5mm≤R-L≤1.5mm.

[0013] Further, along the axial direction of the crankshaft, the projected outer contour of the straight oil groove includes one of an arc shape, a trapezoidal shape, and a rectangular shape; and / or, the inner wall surface of the straight oil groove includes a first section surface, a second section surface, and a third section surface, the second section surface is located between the first section surface and the third section surface along the circumferential direction of the crankshaft, and the projected outer contour of at least one of the first section surface, the second section surface, and the third section surface is a straight line, and the projected outer contour of at least one of the other two is an arc shape.

[0014] Further, the inner surface of the straight oil groove includes:

[0015] an arc surface located on the side of the straight oil groove away from the bottom of the crankshaft along the radial direction of the crankshaft;

[0016] a first plane located on the side of the straight oil groove close to the crankshaft and on one side of the arc surface along the circumferential direction of the arc surface along the radial direction of the crankshaft;

[0017] a second plane located on the side of the straight oil groove close to the crankshaft and on the other side of the arc surface along the circumferential direction of the arc surface along the radial direction of the crankshaft.

[0018] Further, along the circumferential direction of the crankshaft, the maximum distance between the first plane and the second plane is not less than 2.0mm and not more than 2.5mm.

[0019] Further, along the radial direction of the crankshaft, the maximum depth of the straight oil groove is not less than 0.5mm and not more than 2.0mm.

[0020] Further, the cylinder is provided with a compression chamber and a sliding vane groove, the eccentric section and the roller are located in the compression chamber, and along the radial direction of the crankshaft, the sliding vane groove is located on one side of the compression chamber and communicates with the compression chamber, and the compression mechanism further comprises:

[0021] a sliding vane, which is installed in the sliding vane groove and at least partially overlies one end of the lower bearing close to the compression cavity, and which is reciprocally movable under the driving of the roller along the radial direction of the crankshaft;

[0022] the lower bearing covers the bottom of the compression cavity along the axial direction of the crankshaft and is at least partially arranged opposite to the sliding vane groove, and one end of the lower bearing close to the sliding vane groove is provided with a second oil groove, the maximum width of the second oil groove along the circumferential direction of the crankshaft is S, and the thickness of the sliding vane is V, wherein 0.4≤S / V≤0.6.

[0023] Further, the size of S is not less than 1.4 mm and not more than 1.8 mm; and / or, the groove depth of the second oil groove along the axial direction of the crankshaft is not more than 1.0 mm; and / or,

[0024] the maximum length of the second oil groove along the radial direction of the crankshaft is not more than 10 mm; and / or,

[0025] the height of the cylinder along the axial direction of the crankshaft is not less than 15 mm and not more than 25 mm; and / or,

[0026] the maximum width of the compression cavity along the radial direction of the crankshaft is not less than 40 mm and not more than 50 mm.

[0027] Further, the lower bearing comprises:

[0028] a flange connected with the cylinder;

[0029] a shaft handle protruding from the flange away from the cylinder along the axial direction of the crankshaft;

[0030] wherein the maximum width of the flange along the radial direction of the crankshaft is not less than 60 mm and not more than 70 mm; and / or,

[0031] the thickness of the flange along the axial direction of the crankshaft is not less than 5 mm and not more than 10 mm; and / or,

[0032] the distance between the end face of the flange close to the cylinder and the end face of the shaft handle away from the cylinder along the axial direction of the crankshaft is not less than 10 mm and not more than 20 mm.

[0033] In another aspect, the present application also provides a compressor, which comprises:

[0034] a shell, wherein an installation cavity is arranged in the shell;

[0035] the compressor pump body;

[0036] A motor is installed in the mounting cavity, and the motor is connected to the crankshaft away from the lower bearing. The crankshaft can rotate around its own axis under the drive of the motor.

[0037] The maximum width of the mounting cavity along the radial direction of the crankshaft is not less than 102 mm and not more than 112 mm; and / or the height of the shell along the axial direction of the crankshaft is not less than 220 mm and not more than 230 mm.

[0038] In the present application, the compressor pump body includes a crankshaft and a compression mechanism. The eccentric section of the crankshaft is provided with a first oil groove and a recess on the outer circumferential surface away from the crankshaft axis. The first oil groove is in communication with the oil supply channel, and the recess is located on at least one side of the first oil groove along the circumferential direction of the crankshaft. The roller of the compression mechanism is sleeved on the eccentric section and forms an oil storage space with the first oil groove and the recess. The straight oil groove is provided in the lower bearing along the axial direction of the crankshaft and is in communication with the oil storage space. Thus, since the lower bearing in the present application can be a powder metallurgy part formed by powder metallurgy pressing and sintering, the straight oil groove provided in the lower bearing facilitates the ejection after powder metallurgy pressing, reduces the machining process of the oil groove of the lower bearing, and thus reduces the machining cost of the lower bearing. Secondly, when the lower bearing is a cast part, the corresponding straight oil groove can be directly formed during the casting of the lower bearing, and the straight oil groove does not need to be additionally machined, which can reduce the production cost of the lower bearing and improve the production efficiency. At the same time, under the high-speed rotation of the crankshaft, the oil from the oil supply channel continuously enters the rotor inner cavity along the oil storage space, and the oil flows into the straight oil groove of the lower bearing under the action of gravity. Since the outer circumferential surface of the eccentric section is provided with a recess, the recess can increase the amount of oil stored in the oil storage space, and the oil film between the oil storage space and the outer circumferential surface of the eccentric section and the roller will temporarily store a part of the oil to relieve the oil discharge pressure of the straight oil groove. Therefore, the compressor pump body provided in the present application not only utilizes the advantage of fewer machining steps of the lower bearing provided with the straight oil groove to reduce the machining cost, but also utilizes the recess provided in the eccentric section to reduce the oil discharge pressure of the lower bearing, which reduces the oil discharge pressure of the compressor pump body, and thus improves the overall working performance of the compressor. BRIEF DESCRIPTION OF DRAWINGS

[0039] The drawings described herein are used to provide further understanding of the present application, constitute a part of the present application, and the illustrative embodiments of the present application and their descriptions are used to explain the present application and do not constitute an improper limitation on the present application. In the drawings:

[0040] Figure 1 A structural schematic diagram of the compressor pump body disclosed in the present application;

[0041] Figure 2 A structural schematic diagram of the compressor pump body disclosed in the present application; Figure 1 An enlarged schematic diagram of part A in FIG. 6;

[0042] Figure 3 Fig. 1 is a structural schematic diagram of a crankshaft;

[0043] Figure 4 Fig. 2 is a sectional view of an eccentric section of the crankshaft in Fig. 1;

[0044] Figure 5 Fig. 3 is a structural schematic diagram of a lower bearing;

[0045] Figure 6 Fig. 4 is a structural schematic diagram of a straight oil groove of the lower bearing; Figure 5 Fig. 5 is an enlarged schematic diagram of part B in Fig. 4;

[0046] Figure 7 Fig. 6 is a structural schematic diagram of a straight oil groove of the lower bearing;

[0047] Figure 8 Fig. 7 is a structural schematic diagram of a compressor.

[0048] In the above drawings, the following reference signs are used:

[0049] 10, crankshaft; 11, eccentric section; 110, first arc surface; 111, first oil groove; 112, recess; 121, second arc surface; 12, oil supply passage; 13, oil discharge hole; 20, compression mechanism; 21, cylinder; 211, compression chamber; 212, sliding vane groove; 213, mounting recess; 22, roller; 23, lower bearing; 230, connecting hole; 231, straight oil groove; 311, arc surface; 312, first plane; 313, second plane; 232, second oil groove; 233, flange; 234, shaft handle; 24, sliding vane; 30, housing; 31, mounting cavity; 40, motor; 50, upper bearing; 60, muffler. DETAILED DESCRIPTION

[0050] It should be noted that the embodiments and features of the embodiments in the present application can be combined with each other without conflict. The present application will be described in detail below with reference to the accompanying drawings and in combination with the embodiments.

[0051] It should be noted that the terms used herein are only intended to describe specific embodiments, and are not intended to limit the exemplary embodiments according to the present application. As used herein, the singular form is intended to include the plural form unless the context clearly indicates otherwise, and it should also be understood that when the terms "comprise" and / or "include" are used in the specification, there is a presence of a feature, step, operation, device, component and / or combination thereof.

[0052] The application is not limited by the relative positioning of parts and steps, the numerical expressions, and values set forth in the examples unless otherwise specifically indicated. It will be appreciated that the dimensions of the various parts illustrated in the drawings are not necessarily to scale, and have been shown with an emphasis on illustrating the principles of the application. Techniques, methods, and apparatus known to those of ordinary skill in the relevant art can not be discussed in detail but should be considered as though they were, where appropriate, part of the description of the application. In all examples shown and discussed herein, any specific values should be interpreted as merely exemplary and not as a limitation on the scope of the exemplary embodiments. Thus, other examples of the exemplary embodiments can have different values. It is to be noted that like reference numerals and letters refer to like items in the drawings and, as such, once an item is defined in one drawing, it is not necessary to discuss it further in subsequent drawings.

[0053] As the existing lower bearing is difficult to have lower processing cost and higher oil discharge speed, to solve the above problems, the inventor of the utility model finds that the oil groove of the lower bearing is usually set as a spiral oil groove in the pump body of the rotor compressor (such as the rotor compressor with a power of 1.5 HP, HP is the power unit of horsepower), no matter whether the lower bearing with the spiral oil groove is obtained by powder metallurgy pressing or casting, the shape of the oil groove needs to be additionally processed, and the processing procedure is more and the cost is higher. To this end, to reduce the processing cost of the lower bearing, the lower bearing 23 of the compressor pump body provided in the first embodiment of the utility model can be a powder metallurgy part or a casting part. The straight oil groove 231 is arranged in the lower bearing 23, the straight oil groove 231 can reduce the processing steps of the lower bearing and improve the drawing efficiency in the pressing process of the lower bearing 23, thereby reducing the processing cost of the lower bearing. As the oil discharge speed of the straight oil groove 231 is slower than that of the spiral oil groove, in the process that the oil discharge hole 13 on the eccentric section 11 of the crankshaft 10 continuously discharges oil and the sliding vane 24 continuously brings oil into the lower bearing 23 at high speed, there can be a problem that too much oil is accumulated near the junction between the straight oil groove 231 and the inner cavity of the roller 22, and the embodiment further provides an oil storage space capable of storing more oil, thereby relieving the oil discharge pressure of the straight oil groove 231 through the oil storage space and improving the oil discharge efficiency.

[0054] Please refer to Figures 1 to 8, the embodiment is to ensure that the production cost of the lower bearing can be reduced while the oil discharge efficiency of the compressor pump body is improved, the compressor pump body in the embodiment specifically comprises a crankshaft 10 and a compression mechanism 20. The crankshaft 10 is provided with an eccentric section 11 and an oil supply channel 12, and the oil supply channel 12 is specifically a channel arranged along the axis of the crankshaft 10. Along the radial direction of the crankshaft 10, the outer peripheral surface of the eccentric section 11 away from the axis of the crankshaft 10 is recessed to be provided with a first oil groove 111 and a recessed portion 112, the first oil groove 111 is communicated with the oil supply channel 12, and specifically, an oil discharge hole (as shown in Figure 3 and Figure 4 ) for communicating the first oil groove 111 and the oil supply channel 12 can be arranged on the eccentric section 11. Along the circumferential direction of the crankshaft 10, the recessed portion 112 is located on at least one side of the first oil groove 111 and is communicated with the first oil groove 111. The compression mechanism 20 comprises a cylinder 21, a roller 22 and a lower bearing 23, the lower bearing 23 is connected to the cylinder 21, one end of the crankshaft 10 penetrates through the cylinder 21 and is sleeved with the lower bearing 23. The eccentric section 11 is located in the cylinder 21, the roller 22 is sleeved on the eccentric section 11 and forms an oil storage space with the first oil groove 111 and the recessed portion 112, that is, the oil storage space is formed by the inner wall surface of the roller 22 and the inner surface of the first oil groove 111 and the recessed portion 112. The eccentric section 11 is a part deviating from the center of the shaft body of the crankshaft 10, and the eccentric section 11 can convert the rotary motion of the roller 22 into the reciprocating motion of the sliding vane 24. Specifically, a connecting hole 230 (as shown in Figure 5 ) is arranged in the lower bearing 23, and the side of the crankshaft 10 penetrating out of the cylinder 21 is matched with the connecting hole 230 and is sleeved in the connecting hole 230. A straight oil groove 231 is recessed on the inner wall surface of the connecting hole 230 along the radial direction of the crankshaft 10.

[0055] Among them, along the axial direction of the crankshaft 10, the straight oil groove 231 is arranged through the lower bearing 23, the straight oil groove 231 is communicated with the oil storage space, and the straight oil groove 231 is specifically communicated with the oil storage space through the installation gap among the roller 22, the crankshaft 10 and the lower bearing 23. Therefore, in the process of obtaining the lower bearing 23 by adopting the powder metallurgy pressing forming method, after the powder is sent into the mold for pressing, the mold pulling operation needs to be carried out, the mold pulling (also called demolding) is to take out the pressed lower bearing (i.e. the obtained lower bearing 23) in the mold, the oil groove structure of the straight oil groove 231 not only facilitates the mold pulling operation, but also can reduce the process of additional machining oil groove. Because the straight oil groove 231 is a straight line type groove structure, the pulling direction of the mold is straight line type, so moving the mold from up to down or from left to right can complete the pulling. The oil groove structure of the straight oil groove 231 can also simplify the structure design difficulty of the mold, reduce the machining cost of the mold and the lower bearing 23, and the pulling process is stable and reliable. The straight oil groove 231 can also reduce the friction and resistance during pulling, so that the pulling is more smooth, improves the production efficiency of the lower bearing 23 while ensuring the product quality.

[0056] At the same time, due to the presence of the recess 112 increases the oil storage capacity of the oil storage space, the crankshaft 10 oil supply channel 12 in the part of the oil can be temporarily in the oil storage space, avoid the compressor pump body in the oil in the straight oil groove 231 and the intersection near the inner cavity of the roller 22 accumulation too much, reduce the lower bearing 23 oil pressure, in turn, reduce the oil pressure of the compressor pump body.

[0057] It can be seen that in the embodiment, the compressor pump body includes a crankshaft 10 and a compression mechanism 20, the eccentric section 11 of the crankshaft 10 is provided with a first oil groove 111 and a recess 112 on the outer periphery away from the axis of the crankshaft 10, the first oil groove 111 is in communication with the oil supply channel 12, along the circumference of the crankshaft 10, the recess 112 is located at least one side of the first oil groove 111. The roller 22 of the compression mechanism 20 is sleeved on the eccentric section 11 and is surrounded by the first oil groove 111 and the recess 112 to form an oil storage space. Wherein, along the axial direction of the crankshaft 10, the lower bearing 23 is provided with a straight oil groove 231 penetrating through the inside, the straight oil groove 231 is in communication with the oil storage space. Thus, since the lower bearing 23 in the embodiment can be a powder metallurgy part formed by powder metallurgy pressing and sintering, the straight oil groove 231 provided on the lower bearing 23 facilitates the ejection after powder metallurgy pressing, reducing the oil groove machining process of the lower bearing 23. Secondly, when the lower bearing 23 is a cast part, the corresponding straight oil groove 231 can be directly formed during the casting of the lower bearing 23, and the straight oil groove 231 does not need to be additionally processed, which can reduce the production cost of the lower bearing 23 and improve the production efficiency. At the same time, under the high-speed operation of the crankshaft 10, the oil from the oil supply channel 12 continuously enters the inner cavity of the roller 22 along the oil storage space, and the oil flows into the straight oil groove 231 of the lower bearing 23 under the action of gravity. Since the outer periphery of the eccentric section 11 is provided with the recess 112, the recess 112 can increase the oil storage capacity of the oil storage space, and the oil film between the oil storage space and the outer periphery of the eccentric section 11 and the roller 22 will temporarily store a part of the oil to relieve the oil pressure of the straight oil groove 231. Therefore, the compressor pump body provided in the embodiment not only takes advantage of the less machining steps of the lower bearing 23 provided with the straight oil groove 231 to reduce the machining cost, but also takes advantage of the recess 112 provided on the eccentric section 11 to reduce the oil pressure of the lower bearing 23, which in turn reduces the oil pressure of the compressor pump body, thereby improving the overall working performance of the compressor.

[0058] After verifying the oil discharge pressure of the compressor pump body provided in the embodiment with and without the recess 112, the experimental data as shown in Table 1 is obtained:

[0059]

[0060] Table 1

[0061] As can be seen from the data in Table 1, after the recess 112 is provided, the oil flow of the straight oil groove 231 of the lower bearing 23 is increased by 0.011 g / s, which is increased by 5.88% compared with the same period, and the oil discharge pressure of the lower bearing 23 is reduced. Moreover, after the recess 112 is provided, the oil flow at other oil discharge positions of the compressor except the lower bearing 23 is higher than the oil flow when the recess 112 is not provided, which greatly reduces the overall oil discharge pressure of the compressor.

[0062] Please refer to Figure 4 The outer circumferential surface of the eccentric section 11 in the region of the first oil groove 111 and the recess 112 is a first circular arc surface 110, the first circular arc surface 110 has a first center (indicated by the symbol O in the figure), the radius of the first circular arc surface 110 is R, and along the radial direction of the first circular arc surface 110, the first distance from the surface of the recess 112 away from the first center to the first center is L, L is less than R, and along the direction close to the first oil groove 111, L gradually decreases. That is, the surface of the recess 112 at the position adjacent to the first circular arc surface 110 has L that can be equal to R, but the surface of the recess 112 close to the first oil groove 111 has L that is smaller than the L of the surface close to the first circular arc surface 110, thereby further increasing the amount of oil that the recess 112 can store, so that the oil discharge pressure of the straight oil groove 231 is lower.

[0063] The recess 112 in the present embodiment is specifically a groove recessed on the outer circumferential surface of the eccentric section 11, and the inner surface of the groove (i.e., the surface of the recess 112 away from the first center) can be at least one of a plane and an arc surface 311. In the present embodiment, the surface of the recess 112 away from the first center is a second circular arc surface 121 adjacent to the first circular arc surface 110 and the first oil groove 111, and the second circular arc surface 121 is a convex arc surface 311 that protrudes outward in a direction away from the first center, and the first distance is the distance between the second circular arc surface 121 and the first center. Thus, the present embodiment can directly machine the second circular arc surface 121 closer to the first center on the side of the first circular arc surface 110 close to the first oil groove 111, which not only can obtain the recess 112 that can store more oil, thereby reducing the oil discharge pressure of the straight oil groove 231, but also can improve the lubrication effect between the roller 22 and the eccentric section 11. When the eccentric section 11 rotates with the crankshaft 10, the second circular arc surface 121 can better guide the captured lubricating oil to the parts that need to be lubricated, thereby reducing the wear of the roller 22. The second circular arc surface 121 can also disperse the load, reduce the local contact pressure of the eccentric section 11, and reduce the risk of pitting and other forms of surface damage.

[0064] Along the axial direction of the crankshaft 10, the second arc surface 121 extends from the end of the eccentric section 11 close to the lower bearing 23 to the end away from the lower bearing 23. That is, the second arc surface 121 is arranged to extend along the axial direction of the crankshaft 10, further increasing the amount of oil temporarily stored in the oil storage space, and facilitating processing, further reducing the local contact point with a large contact pressure between the eccentric section 11 and the roller 22, and improving the service life of the eccentric section 11 and the roller 22.

[0065] In the present embodiment, the radius of the first arc surface 110 and the first distance satisfy the following relationship:

[0066] 0.5mm≤R-L≤1.5mm.

[0067] Therefore, by making the difference R-L≥0.5mm, it is ensured that the second arc surface 121 can effectively increase the amount of oil in the oil storage space, thereby achieving the purpose of reducing the oil discharge pressure of the straight oil groove 231. By making the difference R-L≤1.5mm, it is avoided that the oil stored in the recess 112 is too much to affect the overall oil discharge efficiency of the compressor pump body. The difference R-L can be one of 0.5mm, 0.6mm, 0.7mm, 0.8mm, 0.9mm, 1.0mm, 1.1mm, 1.2mm, 1.3mm, 1.4mm, 1.5mm, etc., or any other value between 0.5 and 1.5, which is not limited in the present embodiment.

[0068] Along the axial direction of the crankshaft 10, the projection outer contour of the straight oil groove 231 includes one of an arc shape, a trapezoidal shape, and a rectangular shape. The straight oil groove 231 with such a structure is easy to design and process.

[0069] In other embodiments, the inner wall surface of the straight oil groove 231 includes a first section, a second section, and a third section. Along the circumferential direction of the crankshaft 10, the second section is located between the first section and the third section, i.e., the second section is located away from the groove bottom of the straight oil groove 231 along the axial direction of the crankshaft 10. The projection outer contour of at least one of the first section, the second section, and the third section is a straight line, and the corresponding section is a plane when it is a straight line. The projection outer contour of at least one of the first section, the second section, and the third section is an arc, and the corresponding section is an arc surface when it is an arc. For example, the second section is an arc surface (i.e., the arc surface 311 mentioned below), and at least one of the first section and the second section is a plane, such as both the first section and the second section being planes or one being a plane and the other being an arc surface. Alternatively, at least one of the first section and the second section is an arc surface, and the second section is a plane, such as both the first section and the second section being arc surfaces or one being an arc surface and the other being a plane. That is, the shape of the straight oil groove 231 in the present embodiment can be a shape formed by the combination of multiple sections of the above types.

[0070] For example, Figure 7As shown, in some embodiments, the inner surface of the straight oil groove 231 comprises an arc surface 311, a first plane 312 and a second plane 313. Along the radial direction of the crankshaft 10, the arc surface 311 is located at the side of the straight oil groove 231 away from the groove bottom of the crankshaft 10. Along the radial direction of the crankshaft 10, the first plane 312 is located at the side of the straight oil groove 231 close to the crankshaft 10 and at one side of the arc surface 311 along its own circumferential direction. Along the radial direction of the crankshaft 10, the second plane 313 is located at the side of the straight oil groove 231 close to the crankshaft 10 and at the other side of the arc surface 311 along its own circumferential direction. That is, the inner surface of the straight oil groove 231 in this embodiment is formed by the arc surface 311 and the first plane 312 and the second plane 313 located at the opposite sides of the arc surface 311 along its own axial direction. The arc surface 311 at the groove bottom of the straight oil groove 231 is beneficial to the flow of oil, and under the action of gravity, the oil can flow more smoothly and be discharged from the cylinder 21. At the same time, the first plane 312 and the second plane 313 on both sides of the arc surface 311 can reduce the risk of oil retention in the straight oil groove 231 and ensure that the excess oil can be discharged more quickly, thereby further reducing the oil discharge pressure through the reasonable design of the inner surface of the straight oil groove 231 itself.

[0071] In this embodiment, along the circumferential direction of the crankshaft 10, the second distance between the first plane 312 and the second plane 313 is smaller on the side close to the arc surface 311 than on the side away from the arc surface 311 along the radial direction of the crankshaft 10, so that the opening of the straight oil groove 231 close to the slot of the crankshaft 10 is in the shape of an outwardly expanding horn, thereby improving the oil discharge capacity of the straight oil groove 231 and further reducing the oil discharge pressure of the lower bearing 23. The maximum distance between the first plane 312 and the second plane 313 along the circumferential direction of the crankshaft 10 (i.e., the maximum value of the second distance between the first plane 312 and the second plane 313 on the side away from the arc surface 311) is d1. Figure 7 As shown, d1 is not less than 2.0 mm and not greater than 2.5 mm. The maximum distance between the first plane 312 and the second plane 313 is the maximum value of the second distance between the first plane 312 and the second plane 313 on the side away from the arc surface 311. In this embodiment, by making the maximum distance d1 not less than 2.0 mm, the oil discharge capacity of the straight oil groove 231 is ensured not to be too small to increase the oil discharge pressure, and by making the maximum distance d1 not greater than 2.5 mm, the oil discharge capacity of the straight oil groove 231 is ensured not to be too large to reduce the lubrication effect between the parts in the compressor pump body. The value of the maximum distance d1 can specifically include one of 2.0 mm, 2.1 mm, 2.2 mm, 2.3 mm, 2.4 mm, 2.5 mm, or any other value between 2.0 mm and 2.5 mm.

[0072] The maximum depth of the straight oil groove 231 along the radial direction of the crankshaft 10 is not less than 0.5 mm and not greater than 2.0 mm. The maximum depth of the straight oil groove 231 is the distance between the groove bottom of the straight oil groove 231 and the first plane 312 on the side close to the crankshaft 10 along the radial direction of the crankshaft 10. Figure 7The depth indicated by the middle symbol d2, i.e. d2 is the distance between the top of the straight oil groove 231 close to the crankshaft 10 and the bottom of the arc surface 311. Thus, the present embodiment ensures that the oil discharge amount of the straight oil groove 231 is not too small to increase the oil discharge pressure by making d2 not less than 0.5 mm, and ensures that the oil discharge amount of the straight oil groove 231 is not too large to reduce the lubrication effect between the parts in the compressor pump body by making d2 not more than 2.0 mm. The value of d2 can specifically include one of 0.5 mm, 0.6 mm, 0.7 mm, 0.8 mm, 0.9 mm, 1.0 mm, 1.1 mm, 1.2 mm, 1.3 mm, 1.4 mm, 1.5 mm, 1.6 mm, 1.7 mm, 1.8 mm, 1.9 mm, 2.0 mm, or any other value (such as 0.85 mm, 1.51 mm, 1.56 mm, etc.) between 0.5 mm and 2.0 mm.

[0073] The compression chamber 211 and the sliding vane groove 212 are arranged in the cylinder 21 in the present embodiment, the eccentric section 11 and the roller 22 are located in the compression chamber 211, the lower bearing 23 is located at the bottom of the compression chamber 211 along the axial direction of the crankshaft 10, and the sliding vane groove 212 is located at one side of the compression chamber 211 and communicates with the compression chamber 211 along the radial direction of the crankshaft 10. The compression mechanism 20 further includes a sliding vane 24, which is installed in the sliding vane groove 212 and at least partially overlies one end of the lower bearing 23 close to the compression chamber 211 along the radial direction of the crankshaft 10, and the sliding vane 24 can reciprocate under the driving of the roller 22. Specifically, the installation groove 213 is arranged at the groove bottom of the sliding vane groove 212 away from the crankshaft 10 along the radial direction of the crankshaft 10, the compression mechanism 20 further includes a spring, one end of the spring along the compression direction of the spring is fixed to the groove bottom of the installation groove 213, and the other end of the spring along the compression direction of the spring is connected with the sliding vane 24. The sliding vane 24 has a first position close to the installation groove 213 and a second position away from the installation groove 213 along the radial direction of the crankshaft 10. In the process of the rotation of the crankshaft 10 around the axis thereof under the driving of the motor 40 of the compressor, the eccentric section 11 drives the roller 22 to contact and push the sliding vane 24 to move to the first position, and at this time the spring is compressed. In the process of the roller 22 rolling to gradually move away from the sliding vane 24 under the driving of the eccentric section 11, the pushing force of the roller 22 on the sliding vane 24 is cancelled, and the sliding vane 24 will recover from the first position to the second position under the stretching action of the spring.

[0074] The lower bearing 23 covers the bottom of the compression chamber 211 along the crankshaft 10 axial direction and is at least partially opposite to the vane groove 212. A second oil groove 232 is provided at one end of the lower bearing 23 near the vane groove 212. This second oil groove 232 reduces the friction between the lower bearing 23 and the vane 24, thereby ensuring that the vane 24 moves smoothly back and forth between the first and second positions. During this process, due to the presence of the second oil groove 232, oil passes through the vane 24, the compression chamber 211, and the contact gap between the lower end face of the cylinder 21 and the lower bearing 23, entering the cavity formed by the roller 22 and the lower bearing 23, and finally exits the cylinder 21 through the straight oil groove 231.

[0075] Along the circumference of crankshaft 10, the maximum width of the second oil groove 232 is S (e.g., Figure 6 As shown, the thickness of the sliding plate 24 is V, where 0.4 ≤ S / V ≤ 0.6. Therefore, this embodiment ensures that the oil volume in the second oil groove 232 is sufficient to reduce friction between the sliding plate 24 and the lower bearing 23 by making the S / V ratio ≥ 0.4, and avoids excessive oil volume in the second oil groove 232, which would increase the oil discharge pressure of the straight oil groove 231. In this embodiment, the second oil groove 232 can be a square groove, a rectangular groove, or a groove structure with at least one arc-shaped sidewall. For example, if the second oil groove 232 is a square groove, the maximum width S along the circumference of the crankshaft 10 is the distance between the two opposite sidewalls of the square groove. If either opposite sidewall of the square groove is an arc-shaped wall, then the maximum width S along the circumference of the crankshaft 10 is the maximum distance between the inner wall surface of one side of the second oil groove 232 and the arc-shaped wall surface of the other side.

[0076] Therefore, in this embodiment, when the S / V value is between the two endpoints of 0.4 and 0.6, or any value between these two endpoints, it not only ensures the lubrication effect between the sliding vane 24 and the lower bearing 23, but also, based on the recessed portion 112 provided in the eccentric section 11, does not increase the oil discharge pressure on the straight oil groove 231 when the second oil groove 232 discharges oil to the straight oil groove 231, thereby ensuring that the oil discharge pressure of the compressor pump body does not increase due to the presence of the second oil groove 232. The S / V value may specifically include one of 0.4, 0.41, 0.42, 0.45, 0.47, 0.48, 0.50, 0.51, 0.53, 0.54, 0.56, 0.57, 0.59, 0.6, or any other value between 0.4 and 0.6.

[0077] The size of S is not less than 1.4 mm and not greater than 1.8 mm, when the size of S is in the numerical range, it can ensure that the second oil groove 232 does not affect the lubrication effect of the sliding vane 24 due to being too small, and the oil discharge pressure of the straight oil groove 231 is not increased due to the second oil groove 232 being too large, and the size of S can specifically include one of 1.4 mm, 1.42 mm, 1.43 mm, 1.46 mm, 1.48 mm, 1.50 mm, 1.51 mm, 1.53 mm, 1.56 mm, 1.58 mm, 1.60 mm, 1.63 mm, 1.65 mm, 1.67 mm, 1.7 mm, 1.71 mm, 1.72 mm, 1.74 mm, 1.75 mm, 1.78 mm, 1.8 mm, or any other value between 1.4 mm and 1.8 mm.

[0078] In the embodiment, along the axial direction of the crankshaft 10, the groove depth (such as d3 shown in the figure) of the second oil groove 232 is not greater than 1.0 mm, thereby avoiding that the d3 of the second oil groove 232 is too deep to increase the oil discharge pressure of the straight oil groove 231. Specifically, the value of d3 can include one of 1.0 mm, 0.98 mm, 0.95 mm, 0.92 mm, 0.90 mm, 0.89 mm, 0.85 mm, or any other value not greater than 1.0 mm. Figure 2 In the embodiment, along the radial direction of the crankshaft 10, the maximum length (such as C shown in the figure) of the second oil groove 232 is not greater than 10 mm, if the opposite sides of the second oil groove 232 along the radial direction of the crankshaft 10 are both flat walls, then the maximum length C is the distance between the opposite walls of the second oil groove 232 along the radial direction of the crankshaft 10, if one of the walls is an arc-shaped wall, then the maximum length C is the distance between the flat wall and the bottom of the arc-shaped wall away from the flat wall. The embodiment ensures that the oil discharge pressure of the straight oil groove 231 is not increased due to the second oil groove 232 being too long by making the maximum length C of the second oil groove 232 not greater than 10 mm. The value of C can specifically include one of 10 mm, 9.8 mm, 9.5 mm, 9.2 mm, 9 mm, 8.9 mm, 8.8 mm, 8.6 mm, or any other value not greater than 10 mm.

[0079] Figure 6 As can be seen from the above, the embodiment matches the lower bearing 23 of the straight oil groove 231 with the crankshaft 10 provided with the recessed portion 112 of the eccentric section 11, so that the straight oil groove 231 can reduce the machining steps of the lower bearing 23, thereby reducing the production cost and improving the production efficiency, and the difference between R and L of the eccentric section 11 of the crankshaft 10 can reduce the oil discharge pressure of the straight oil groove 231.

[0080] As can be seen from the above, the embodiment matches the lower bearing 23 of the straight oil groove 231 with the crankshaft 10 provided with the recessed portion 112 of the eccentric section 11, so that the straight oil groove 231 can reduce the machining steps of the lower bearing 23, thereby reducing the production cost and improving the production efficiency, and the difference between R and L of the eccentric section 11 of the crankshaft 10 can reduce the oil discharge pressure of the straight oil groove 231.

[0081] ​In the axial direction of the crankshaft 10, the height of the cylinder 21 is not less than 15 mm and not more than 25 mm. The height of the cylinder 21 is the distance between the end face of the cylinder 21 close to the upper bearing 50 and the end face close to the lower bearing 23. The height of the cylinder 21 can specifically include one of 15 mm, 16 mm, 17 mm, 18 mm, 19 mm, 20 mm, 21 mm, 22 mm, 23 mm, 24 mm, 25 mm, etc.

[0082] In the radial direction of the crankshaft 10, the maximum width of the compression chamber 211 is not less than 40 mm and not more than 50 mm. When the inner circumferential surface of the compression chamber 211 is circular, the maximum width of the compression chamber 211 is the inner diameter of the compression chamber 211. The maximum width of the compression chamber 211 can specifically include one of 40 mm, 41 mm, 43 mm, 46 mm, 48 mm, 50 mm, etc.

[0083] The lower bearing 23 in the embodiment includes a flange 233 and a shaft handle 234. The flange 233 is connected with the cylinder 21. In the axial direction of the crankshaft 10, the shaft handle 234 is protruded from the side of the flange 233 away from the cylinder 21. In the radial direction of the crankshaft 10, the maximum width of the flange 233 is not less than 60 mm and not more than 70 mm. When the flange 233 is a circular disc structure, the maximum width of the flange 233 is the outer diameter of the flange 233. In the embodiment, the maximum width of the flange 233 can include one of 60 mm, 61 mm, 62 mm, 63 mm, 64 mm, 65 mm, 66 mm, 67 mm, 68 mm, 69 mm, 70 mm, etc. In the axial direction of the crankshaft 10, the thickness of the flange 233 (i.e. the first thickness mentioned below) is not less than 5 mm and not more than 10 mm. The thickness can specifically include one of 5 mm, 6 mm, 7 mm, 8 mm, 9 mm, 10 mm, etc. In the axial direction of the crankshaft 10, the distance between the end face of the flange 233 close to the cylinder 21 and the end face of the shaft handle 234 away from the cylinder 21 is not less than 10 mm and not more than 20 mm, i.e. the height of the lower bearing 23 is not less than 10 mm and not more than 20 mm. The height of the lower bearing 23 can include one of 10 mm, 11 mm, 12 mm, 13 mm, 14 mm, 15 mm, 16 mm, 17 mm, 18 mm, 19 mm, 20 mm, etc.

[0084] The second embodiment of the utility model also provides a kind of compressor, and the compressor includes compressor pump body.The structure of compressor pump body please refer to the content provided by the first embodiment of the utility model, and this embodiment will not be described here.

[0085] As Figure 8As shown, the compressor in the embodiment further comprises a shell 30 and a motor 40, the motor 40 and the compressor pump body are both installed in a mounting cavity 31 of the shell 30, the motor 40 comprises a stator and a rotor. The rotor is rotatably arranged in the stator, and the rotor is connected to an end of the crankshaft 10 away from the lower bearing 23 of the compressor pump body to drive the crankshaft 10 to rotate. The compressor pump body further comprises an upper bearing 50 and a silencer 60. In the axial direction of the crankshaft 10, the upper bearing 50 is connected to a side of the cylinder 21 away from the lower bearing 23 and connected to the inner circumferential wall of the shell 30. The silencer 60 is arranged on a side of the upper bearing 50 away from the cylinder 21. The inner diameter of the shell 30 of the compressor in the embodiment (i.e. the diameter of the mounting cavity 31 inside the shell 30 for mounting the compressor pump body) is between 102mm and 112mm, and the inner diameter of the shell 30 can specifically include one of 102mm, 103mm, 104mm, 105mm, 106mm, 107mm, 108mm, 109mm, 110mm, 111mm, 112mm, etc. The shell height from the end face of the bottom of the shell 30 to the top end face is between 220mm and 230mm, and the shell height can specifically include one of 220mm, 221mm, 222mm, 223mm, 224mm, 225mm, 226mm, 227mm, 228mm, 229mm, 300mm, etc.

[0086] In the embodiment, the inner diameter of the compression chamber 211 of the cylinder 21 is between 40mm and 50mm (and can specifically include one of 40mm, 41mm, 43mm, 46mm, 48mm, 50mm, etc.), and the height of the cylinder 21 is between 15mm and 25mm. The height of the cylinder 21 is the distance between the end face of the end of the cylinder 21 close to the upper bearing 50 and the end face of the end close to the lower bearing 23, and the height of the cylinder 21 can specifically include one of 15mm, 16mm, 17mm, 18mm, 19mm, 20mm, 21mm, 22mm, 23mm, 24mm, 25mm, etc.

[0087] The outer diameter of the lower bearing 23 is between 60mm and 70mm, the lower bearing 23 comprises a flange 233 and a shaft handle 234 protruding from the flange 233 away from the cylinder 21, and the connecting hole 230 is arranged through the flange 233 and the shaft handle 234, wherein, along the axial direction of the crankshaft 10, the flange 233 has a first thickness, the first thickness is the distance between the end faces of the opposite ends of the flange 233, and the first thickness is between 5mm and 10mm, and the first thickness can specifically include one of 5mm, 6mm, 7mm, 8mm, 9mm and 10mm. The height of the lower bearing 23 is between 10mm and 20mm, and along the axial direction of the crankshaft 10, the height of the lower bearing 23 is the distance between the end face of the flange 233 close to the cylinder 21 and the end face of the shaft handle 234 away from the cylinder 21, and the height of the lower bearing 23 can include one of 10mm, 11mm, 12mm, 13mm, 14mm, 15mm, 16mm, 17mm, 18mm, 19mm and 20mm.

[0088] The oil discharge hole of the eccentric section 11 of the crankshaft 10 is in communication with the first oil groove 111, and the recessed portion 112 of the non-pressure area of the eccentric section 11 and the inner wall surface (also referred to as the inner circular surface) of the roller 22 form an additional oil storage area, which increases the volume of the oil storage space formed by the inner circular surface of the roller 22 and the first oil groove 111, increases the oil storage amount between the roller 22 and the eccentric section 11, and helps to reduce the oil discharge pressure of the straight oil groove 231 of the lower bearing 23. The increase of the oil amount between the eccentric section 11 and the inner circular surface of the roller 22 also helps to form more oil film and reduce the wear between the eccentric section 11 and the inner circular surface of the roller 22. Due to the presence of the recessed portion 112, the outer peripheral surface of the eccentric portion is composed of the first circular surface 110 and the connecting surface of the area where the recessed portion 112 is located, the connecting surface is the surface of the recessed portion 112 away from the first center, and the connecting surface can be an inclined surface, and in the embodiment, the shape of the connecting surface is a second circular surface 121.

[0089] The second oil groove 232 for reducing the friction between the sliding vane 24 and the lower bearing 23 is arranged on the end face of the lower bearing 23 close to the sliding vane 24 and in contact with the bottom of the sliding vane 24. When the compressor pump body is running, the eccentric section 11 of the crankshaft 10 drives the roller 22 to rotate, and the roller 22 and the spring cooperate to drive the sliding vane 24 to slide back and forth in the sliding vane groove 212 in the cylinder 21. Due to the presence of the second oil groove 232 on the end face of the lower bearing 23, the oil enters the cavity formed by the roller 22 and the lower bearing 23 through the contact gap between the sliding vane 24, the cylinder 21 and the lower bearing 23, and finally enters the straight oil groove 231 of the lower bearing 23 to flow out of the compressor pump body. Due to the presence of the recessed portion 112, the large amount of oil stored between the roller 22 and the eccentric section 11 can alleviate the oil discharge pressure of the straight oil groove 231 caused by the second oil groove 232.

[0090] The crankshaft 10 with the first arc surface 110 and the eccentric section 11 and the lower bearing 23 with the straight oil groove 231 and the second oil groove 232 are combined, the straight oil groove 231 of the lower bearing 23 can reduce the machining steps of the lower bearing 23 and reduce the machining cost. The second oil groove 232 of the lower bearing 23 can reduce the wear of the sliding vane 24 to the end surface of the lower bearing 23, and the gap (R-L) between the first arc surface 110 and the connecting surface of the eccentric section 11 of the crankshaft 10 can reduce the oil discharge pressure caused by the second oil groove 232 and the straight oil groove 231 to the compressor.

[0091] For the convenience of description, spatial relative terms such as "above", "upper", "top surface", "upper" and the like can be used herein to describe the spatial positional relationship of one device or feature with other devices or features as shown in the drawings. It should be understood that the spatial relative terms are intended to include different orientations in use or operation in addition to the orientation of the device described in the drawings. For example, if the device in the drawing is inverted, the device described as "above" or "above" other devices or structures will be positioned "below" or "below" other devices or structures. Therefore, the exemplary term "above" can include both "above" and "below". The device can also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative description used herein is interpreted accordingly.

[0092] In addition, it should be noted that the use of the words "first", "second" and the like to define parts is only for the convenience of distinguishing the corresponding parts, and the above words have no special meaning unless otherwise stated, and therefore cannot be understood as limiting the scope of protection of the present application.

[0093] The above is only a preferred embodiment of the present application and is not intended to limit the present application. Those skilled in the art can make various modifications and changes to the present application. Any modification, equivalent replacement, improvement, etc. made within the spirit and principles of the present application shall be included in the scope of protection of the present application.

Claims

1. A compressor pump body characterized by, The application relates to a crankshaft (10) provided with an eccentric section (11) and an oil supply channel (12), wherein, along the radial direction of the crankshaft (10), a first oil groove (111) and a recess (112) are arranged on the outer circumferential surface of the eccentric section (11) away from the axis of the crankshaft (10), the first oil groove (111) is communicated with the oil supply channel (12), and, along the circumferential direction of the crankshaft (10), the recess (112) is located on at least one side of the first oil groove (111) and communicated with the first oil groove (111). A compression mechanism (20) comprises a cylinder (21), a roller (22) and a lower bearing (23), the lower bearing (23) is connected to the cylinder (21), one end of the crankshaft (10) penetrates through the cylinder (21) and is sleeved with the lower bearing (23), the eccentric section (11) is located in the cylinder (21), and the roller (22) is sleeved on the eccentric section (11) and forms an oil storage space with the first oil groove (111) and the recess (112). Wherein, along the axial direction of the crankshaft (10), a straight oil groove (231) is arranged in the lower bearing (23) and communicated with the oil storage space. The outer circumferential surface of the eccentric section (11) is located in the region of the first oil groove (111) and the recess (112) and is a first circular arc surface (110), the first circular arc surface (110) has a first center, the radius of the first circular arc surface (110) is R, along the radial direction of the first circular arc surface (110), the first distance from the surface of the recess (112) away from the first center to the first center is L, L is smaller than R, and, along the direction close to the first oil groove (111), L gradually decreases.

2. The compressor pump body of claim 1, wherein, The surface of the recess (112) away from the first center is a second circular arc surface (121) adjacent to the first circular arc surface (110) and the first oil groove (111), and the second circular arc surface (121) is a convex arc surface outwardly convex in the direction away from the first center, and the first distance is the distance between the second circular arc surface (121) and the first center.

3. The compressor pump body of claim 2, wherein, Along the axial direction of the crankshaft (10), the second circular arc surface (121) extends from one end of the eccentric section (11) close to the lower bearing (23) to one end of the eccentric section (11) away from the lower bearing (23).

4. The compressor pump body of claim 3, wherein, The radius of the first circular arc surface (110) and the first distance satisfy the following relationship:

5. The compressor pump body of any of claims 2 to 4, wherein, 0.5mm<=R-L<=1.5mm. ​ 6. The compressor pump body of claim 1, wherein, The projected outer contour of the straight oil groove (231) in the axial direction of the crankshaft (10) comprises one of an arc shape, a trapezoidal shape, and a rectangular shape; and / or, the inner wall surface of the straight oil groove (231) comprises a first section surface, a second section surface, and a third section surface, the second section surface is located between the first section surface and the third section surface in the circumferential direction of the crankshaft (10), and the projected outer contour of at least one of the first section surface, the second section surface, and the third section surface is a straight line shape, and the projected outer contour of at least one of the first section surface, the second section surface, and the third section surface is an arc shape.

7. The compressor pump body of claim 1, wherein, The inner surface of the straight oil groove (231) comprises: an arc surface (311) located away from the bottom of the straight oil groove (231) in the radial direction of the crankshaft (10); a first plane (312) located on the side of the straight oil groove (231) close to the crankshaft (10) in the radial direction of the crankshaft (10) and on one side of the arc surface (311) in the circumferential direction of the arc surface (311); a second plane (313) located on the side of the straight oil groove (231) close to the crankshaft (10) in the radial direction of the crankshaft (10) and on the other side of the arc surface (311) in the circumferential direction of the arc surface (311).

8. The compressor pump body of claim 7, wherein, The maximum distance between the first plane (312) and the second plane (313) in the circumferential direction of the crankshaft (10) is not less than 2.0 mm and not greater than 2.5 mm.

9. The compressor pump body of claim 7, wherein, The maximum depth of the straight oil groove (231) in the radial direction of the crankshaft (10) is not less than 0.5 mm and not greater than 2.0 mm.

10. The compressor pump body of any of claims 1-4, 6-9, wherein, The cylinder (21) is provided with a compression chamber (211) and a sliding vane groove (212), the eccentric section (11) and the roller (22) are located in the compression chamber (211), the sliding vane groove (212) is located on one side of the compression chamber (211) and communicates with the compression chamber (211) in the radial direction of the crankshaft (10), and the compression mechanism (20) further comprises: a sliding vane (24) installed in the sliding vane groove (212) and at least partially arranged on one end of the lower bearing (23) close to the compression chamber (211), the sliding vane (24) can reciprocate under the driving of the roller (22) in the radial direction of the crankshaft (10); the lower bearing (23) is arranged on the bottom of the compression chamber (211) in the axial direction of the crankshaft (10) and at least partially arranged opposite to the sliding vane groove (212), one end of the lower bearing (23) close to the sliding vane groove (212) is provided with a second oil groove (232), the maximum width of the second oil groove (232) in the circumferential direction of the crankshaft (10) is S, and the thickness of the sliding vane (24) is V, wherein 0.4≤S / V≤0.

6.

11. The compressor pump body of claim 10, wherein, The size of S is not less than 1.4 mm and not greater than 1.8 mm; and / or, In the axial direction of the crankshaft (10), the groove depth of the second oil groove (232) is not greater than 1.0 mm; and / or, in the radial direction of the crankshaft (10), the maximum length of the second oil groove (232) is not greater than 10 mm; and / or, In the axial direction of the crankshaft (10), the height of the cylinder (21) is not less than 15 mm and not greater than 25 mm; and / or, In the radial direction of the crankshaft (10), the maximum width of the compression chamber (211) is not less than 40 mm and not greater than 50 mm.

12. The compressor pump body of any of claims 1-4, 6-9, wherein, The lower bearing (23) comprises: a flange (233) connected with the cylinder (21); a shaft handle (234) protruding from the flange (233) away from the cylinder (21) in the axial direction of the crankshaft (10); In the radial direction of the crankshaft (10), the maximum width of the flange (233) is not less than 60 mm and not greater than 70 mm; and / or, In the axial direction of the crankshaft (10), the thickness of the flange (233) is not less than 5 mm and not greater than 10 mm; and / or, In the axial direction of the crankshaft (10), the distance between the end face of the flange (233) close to the cylinder (21) and the end face of the shaft handle (234) away from the cylinder (21) is not less than 10 mm and not greater than 20 mm.

13. A compressor characterized by, The compressor comprises: a housing (30) provided with a mounting cavity (31) therein; the compressor pump body of any one of claims 1 to 12; a motor (40) and the compressor pump body are both mounted in the mounting cavity (31), the motor (40) is connected with one end of the crankshaft (10) away from the lower bearing (23), and the crankshaft (10) can rotate around its own axis under the drive of the motor (40); wherein In the radial direction of the crankshaft (10), the maximum width of the mounting cavity (31) is not less than 102 mm and not greater than 112 mm; and / or, in the axial direction of the crankshaft (10), the height of the housing (30) is not less than 220 mm and not greater than 230 mm.

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