CN216044298U - Pump body subassembly and compressor - Google Patents

Abstract

The pump body assembly comprises a crankshaft and a crankcase, the crankcase comprises a box body, a crankshaft hole is formed in the box body, the crankshaft comprises a main shaft, a balance block and an eccentric shaft which are sequentially connected, the balance block is provided with a thrust surface, and the box body is provided with a supporting surface; the supporting surface is concavely provided with a first oil groove which is communicated with the crankshaft hole; the main shaft is provided with a main oil way, the peripheral surface of the main shaft is concavely provided with a second oil groove, the second oil groove is annularly arranged along the circumferential direction of the main shaft, and the second oil groove penetrates through the thrust surface and the main oil way; when the thrust surface is abutted to the supporting surface, the second oil groove can guide the lubricating oil of the main oil way to the first oil groove, and the lubricating oil in the first oil groove is diffused between the thrust surface and the supporting surface, so that the friction power consumption of the main shaft relative to the rotation of the box body is reduced, and the abrasion of the crankshaft and the box body is improved; the thrust surface and the supporting surface do not need to be provided with a supporting sheet, a ball bearing and the like, so that the assembly difficulty of the crankshaft and the crankcase is reduced, and the material cost of the pump body assembly is reduced.

Description

Pump body subassembly and compressor

Technical Field

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

Background

The efficiency of the compressor is mainly mechanical, electrical and volumetric. At present, a main research direction in the aspect of improving the mechanical efficiency is to reduce friction between various parts, because excessive friction power increases the overall power consumption of the compressor, and finally the energy efficiency ratio of the compressor is significantly reduced.

In the reciprocating compressor, the mechanical structure mainly includes: the piston comprises a crankcase, a crankshaft, a piston, a connecting rod and a piston pin for connecting the piston and the connecting rod. The crankshaft comprises a main shaft, a balance block and an auxiliary shaft which are sequentially connected, the main shaft penetrates out of the crankcase, and the balance block is abutted to the crankcase. In order to reduce the friction between the crankcase and the balance block, an upper support sheet, a lower support sheet and a ball bearing are arranged between the support surface of the crankcase and the thrust surface of the balance block, so that the sliding friction between the crankcase and the crankshaft is changed into rolling friction, the friction coefficient is reduced, and the mechanical efficiency of the compressor is improved. However, the assembly of the support plate and the ball bearing is difficult, and the manufacturing cost of the compressor is increased.

SUMMERY OF THE UTILITY MODEL

An object of the embodiment of this application is to provide a pump body subassembly, aim at solving among the current compressor and use the assembly difficulty, the with high costs that backing sheet and ball bearing exist between crankcase and the bent axle.

The pump body assembly comprises a crankshaft and a crankcase, wherein the crankcase comprises a box body, a crankshaft hole is formed in the box body, the crankshaft comprises a main shaft, a balance block and an eccentric shaft which are sequentially connected, the main shaft penetrates through the crankshaft hole, one side, facing the box body, of the balance block is provided with a thrust surface around the main shaft, and one side, facing the balance block, of the box body is provided with a supporting surface around the crankshaft hole;

a first oil groove is concavely arranged on the supporting surface and communicated with the crankshaft hole; the main shaft is provided with a main oil way which is formed by an end face of one end, deviating from the eccentric shaft, of the main shaft, a second oil groove is concavely formed in the peripheral surface of the main shaft, the second oil groove is annularly formed along the circumferential direction of the main shaft, one side, close to the balance block, of the second oil groove is communicated to the thrust surface, and the second oil groove is further communicated with the main oil way.

In one embodiment, a side of the box body facing the balance weight is provided with a supporting boss surrounding the crankshaft hole, and the surface of the supporting boss is the supporting surface; the first oil groove penetrates through the inner circumferential surface and the outer circumferential surface of the support boss.

In one embodiment, the axial depth of the first oil groove is 0.1 mm-3 mm, and the axial depth of the first oil groove is smaller than the axial height of the support boss.

In one embodiment, the first oil groove extends in a radial direction of the crankshaft bore.

In one embodiment, the radial depth of the second oil groove is 0.1 mm-3 mm, and the radial depth of the second oil groove is uniform at all positions in the circumferential direction.

In one embodiment, the main oil path includes an oil chamber formed in the main shaft and opened from an end surface of the main shaft facing away from the eccentric shaft, a first oil hole opened from an outer surface of the main shaft and penetrating to the oil chamber, and a spiral oil groove formed in the outer surface of the main shaft, communicating with the first oil hole, and extending spirally toward the balance weight; one side of the second oil groove, which is far away from the balance block, is communicated with the spiral oil groove.

In one embodiment, a third oil groove is further concavely arranged on the outer peripheral surface of the main shaft, and the third oil groove is communicated between one side of the second oil groove, which is far away from the balance block, and the spiral oil groove; the third oil groove extends along the axial direction of the main shaft or obliquely extends relative to the axial direction of the main shaft.

In one embodiment, the axial width of the second oil groove is 0.5 mm-3 mm; and/or the axial height of the third oil groove is 0.5 mm-5 mm.

In one embodiment, the radial depth of the third oil groove is 0.1 mm-3 mm, and the radial depth of the third oil groove is uniform at all positions in the axial direction.

Another objective of the embodiments of the present application is to provide a compressor, which includes a motor and the pump body assembly as described in the embodiments above, the pump body assembly further includes a connecting rod, a piston, and a cylinder, and the connecting rod, the piston, and the cylinder are all disposed on a side of the box body away from the main shaft; the motor is connected with the main shaft, the eccentric shaft is connected with the connecting rod, and the piston is driven to move in the cylinder.

The beneficial effect of the pump body subassembly that this application embodiment provided and compressor lies in:

according to the pump body assembly provided by the embodiment of the application, the first oil channel communicated with the crankshaft hole of the crankcase is formed on the supporting surface of the crankcase, and the second oil groove communicated with the main oil channel and the thrust surface of the balance block is formed on the main shaft, so that when the thrust surface of the balance block is abutted to the supporting surface of the crankcase, the second oil groove can guide lubricating oil of the main oil channel to the first oil groove, the lubricating oil in the first oil groove can be further diffused between the thrust surface and the supporting surface and lubricate the thrust surface and the supporting surface, the friction power consumption of the main shaft relative to the rotation of the crankcase can be reduced, and the abrasion between the crankshaft and the crankcase can be improved; and, need not to set up parts such as backing sheet, ball bearing between thrust surface and the backing surface, can reduce the assembly degree of difficulty between bent axle and the crankcase, reduce the material cost of this pump body subassembly. The compressor with the pump body assembly has the advantages that the lubrication between the crankshaft and the crankcase is good, the friction power consumption is low, the abrasion degree of the crankshaft and the crankcase can be reduced, the assembly cost is low, and the material cost is low.

Drawings

In order to more clearly illustrate the technical solutions in the embodiments of the present application, the drawings needed to be used in the embodiments will be briefly described below, and it is obvious that the drawings in the following description are only some embodiments of the present application, and it is obvious for those skilled in the art to obtain other drawings without creative efforts.

FIG. 1 is a top view of a crankcase housing in a pump block assembly according to an embodiment of the present disclosure;

FIG. 2 is an enlarged view at A in FIG. 1;

FIG. 3 is a schematic cross-sectional view of a first oil sump in the housing of FIG. 1;

FIG. 4 is an elevation view of a crankshaft in a pump block assembly provided by an embodiment of the present application;

FIG. 5 is an enlarged view at B in FIG. 4;

FIG. 6 is a schematic cross-sectional view of a third oil sump in the crankshaft of FIG. 4;

FIG. 7 is a schematic diagram of a mating relationship between a crankshaft and a housing in a pump body assembly according to an embodiment of the present application.

The designations in the figures mean:

100-a pump body assembly;

1-crankshaft, 11-main shaft, 113-spiral oil groove, 114-second oil groove, 115-third oil groove, 116-second oil hole, 12-balance block, 121-thrust boss, 122-thrust surface and 13-eccentric shaft;

2-box, 21-crankshaft hole, 22-supporting boss, 23-supporting surface, 231-first oil groove.

Detailed Description

In order to make the objects, technical solutions and advantages of the present application more apparent, the present application is described in further detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the present application and are not intended to limit the present application.

It will be understood that when an element is referred to as being "secured to" or "disposed on" another element, it can be directly or indirectly secured to or disposed on the other element. When an element is referred to as being "connected to" another element, it can be directly or indirectly connected to the other element. The terms "upper", "lower", "left", "right", and the like, indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are only for convenience of description, but do not indicate or imply that the referred devices or elements must have a specific orientation, be constructed and operated in a specific orientation, and thus, should not be construed as limiting the patent. The terms "first", "second" and "first" are used merely for descriptive purposes and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features. The meaning of "plurality" is two or more unless specifically limited otherwise.

Referring to fig. 1, 4 and 7, a pump body assembly 100 for a compressor is provided according to an embodiment of the present disclosure. Specifically, the pump body assembly 100 includes a crankshaft 1 and a crankcase including a case 2 and cylinders (not shown), as shown in fig. 1 and 7, the case 2 being provided with crank holes 21 penetrating opposite sides thereof, the cylinders being provided on the case 2. As shown in fig. 4, the crankshaft 1 includes a main shaft 11, a balance weight 12 and an eccentric shaft 13 connected in sequence, the central axis of the eccentric shaft 13 is parallel to the central axis of the main shaft 11, but the central axis of the eccentric shaft 13 is located on one side of the central axis of the main shaft 11, the center of mass of the balance weight 12 is located on the other side of the central axis of the main shaft 11, and the balance weight 12 is used for balancing the rotation moment of the eccentric shaft 13 during the rotation of the eccentric shaft 13 with the main shaft 11. As shown in fig. 7, the main shaft 11 passes through the crank hole 21; as shown in fig. 4, 5 and 7, the side of the counterweight 12 facing the crankcase is provided with a thrust surface 122; as shown in fig. 2 and 7, a support surface 23 is provided on the side of the case 2 facing the counterweight 12. The thrust surface 122 abuts the support surface 23 after the main shaft 11 passes through the crank hole 21.

In this embodiment, as shown in fig. 2, the supporting surface 23 is concavely provided with a first oil groove 231, and the first oil groove 231 is communicated with the crankshaft hole 21; as shown in fig. 4 and 5, the main shaft 11 is provided with a main oil path and a second oil groove 114, the main oil path is opened from a side end surface of the main shaft 11 away from the eccentric shaft 13, extends inside the main shaft 11 until penetrating to the outer circumferential surface of the main shaft 11, the second oil groove 114 is concavely provided on the outer circumferential surface of the main shaft 11, and is annularly provided along the circumferential direction of the main shaft 11, and a side of the second oil groove 114 close to the balance weight 12 penetrates to a thrust surface 122 of the balance weight 12, in other words, the thrust surface 122 is connected in parallel with a side wall of the second oil groove 114, and a side of the second oil groove 114 away from the balance weight 12 is communicated with the main oil path.

In a specific application, the lubricating oil enters the main oil path from the end surface of the main shaft 11 on the side away from the eccentric shaft 13, flows out from the end of the main oil path (i.e., the opening formed on the outer circumferential surface of the main shaft 11), enters the second oil groove 114, and then reaches the inner edge of the thrust surface 122 of the counterweight 12; since the first oil groove 231 is recessed with respect to the support surface 23, the lubricating oil can be diffused radially outward and into the first oil groove 231; further, as the weight 12 rotates, the lubricating oil can be diffused between the thrust surface 122 and the support surface 23; the first oil groove 231 also has a certain oil storage function, and the lubricating oil stored therein can ensure that the lubrication between the thrust surface 122 and the support surface 23 is always maintained for a certain period of time.

According to the pump body assembly 100 provided by the embodiment of the application, the first oil groove 231 penetrating through the crankshaft hole 21 of the crankcase body 2 is formed on the supporting surface 23 of the crankcase body 2, and the second oil groove 114 penetrating through the main oil path and the thrust surface 122 of the balance block 12 is formed on the main shaft 11, so that when the thrust surface 122 of the balance block 12 is abutted to the supporting surface 23 of the crankcase body 2, the second oil groove 114 can guide the lubricating oil of the main oil path to the first oil groove 231, and the lubricating oil in the first oil groove 231 can further diffuse between the thrust surface 122 and the supporting surface 23 and lubricate between the thrust surface 122 and the supporting surface 23, so that the friction power consumption of the main shaft 11 rotating relative to the crankcase body 2 can be reduced, and the mutual abrasion between the crankshaft 1 and the crankcase body 2 can be improved; in addition, the thrust surface 122 and the support surface 23 do not need to be provided with a support sheet, a ball bearing and other parts, so that the assembly difficulty between the crankshaft 1 and the crankcase can be reduced, and the material cost of the pump body assembly 100 can be reduced.

When the pump assembly 100 is used in a compressor, the pump assembly is generally disposed such that the axial direction of the main shaft 11 is aligned with the vertical direction, and the main shaft 11, the balance weight 12, and the eccentric shaft 13 of the crankshaft 1 are sequentially connected from the bottom up, as shown in fig. 4. Thus, the thrust surface 122 of the weight 12 is the lower surface thereof, and the support surface 23 of the case 2 is the upper surface thereof. The pump body assembly 100 will be described in detail based on this orientation. It will be appreciated that the crankshaft 1 and crankcase may each have other orientations in the non-use condition, but without affecting the relative relationship between the different parts of the crankshaft 1 and crankcase. In addition, the following terms "axial direction", "radial direction" and "circumferential direction" are based on the main shaft 11, that is, "axial direction" refers to the axial direction of the main shaft 11 (including the direction coincident with or parallel to it), "radial direction" and "circumferential direction" are the same.

As shown in fig. 4 and 5, an annular thrust boss 121 is formed on a side of the counterweight 12 facing the spindle 11, and a lower surface of the thrust boss 121 is a thrust surface 122. Thus, the thrust surface 122 protrudes relative to other surface positions on the lower side of the balance block 12, so that only the thrust surface 122 abuts against the crankcase, and the other positions of the balance block 12 can be prevented from being worn, and the whole abrasion and structural influence on the balance block 12 can be avoided.

Referring to fig. 4, in one embodiment, the main oil passage includes an oil chamber (not shown) opened from an end surface (lower end) of the main shaft 11 facing away from the eccentric shaft 13 and extending upward inside the main shaft 11, a first oil hole (not shown) opened from an outer surface of the main shaft 11 and penetrating to the oil chamber, and a spiral oil groove 113 formed on the outer surface of the main shaft 11, communicating with the first oil hole, and extending spirally toward the balance weight 12. The side (lower side) of the second oil groove 114 facing away from the weight 12 communicates with the spiral oil groove 113.

Specifically, when the pump block assembly 100 is in operation, the lubricating oil enters the oil chamber from the opening of the lower end surface of the main shaft 11, flows upward under the action of centrifugal force and is thrown out of the first oil hole, further enters the helical oil groove 113, and continues to flow upward under the action of centrifugal force until entering the second oil groove 114. The lubricating oil entering the second oil groove 114 can be diffused outward along the thrust surface 122 during the rotation of the weight 12, and more importantly, the lubricating oil entering the second oil groove 114 can enter and be stored in the first oil groove 231; further, the lubricating oil in the first oil groove 231 lubricates the thrust surface 122 and the thrust surface 122 during the relative rotation of the counterweight 12 and the case 2.

Generally, the upper end of the spiral oil groove 113 has a large distance from the thrust surface 122 based on the manufacturing process of the spiral oil groove 113. In the embodiment, in order to reduce the axial width H1 of the second oil groove 114 and avoid the influence on the overall structural strength of the main shaft 11 due to the need of removing too much material from the main shaft 11 by providing the second oil groove 114, a third oil groove 115 is further concavely provided on the outer circumferential surface of the main shaft 11, as shown in fig. 5, the third oil groove 115 is communicated between the spiral oil groove 113 and the side of the second oil groove 114 away from the balance weight 12. That is, the spiral oil groove 113 may be located far from the thrust surface 122 to ensure the convenience of manufacturing, and the second oil groove 114 may have a smaller axial width H1 without adversely affecting the structural strength of the main shaft 11.

The axial width H1 of the second oil groove 114 may be 0.5mm to 3mm, optionally 1mm to 2mm, and specifically may be 1.2mm, 1.5mm, or the like. The specific value of the axial width H1 of the second oil groove 114 can be set according to the requirement in the specific product application, and is merely exemplary and not particularly limited.

The radial depth of the second oil groove 114 also determines its oil storage capacity and its influence on the strength of the main shaft 11. In an embodiment, the radial depth of the second oil groove 114 is 0.1mm to 3mm, optionally, the radial depth of the second oil groove 114 is 0.1mm to 1mm, specifically, 0.1mm, 0.2mm, 0.5mm, 0.8mm, and the like, and specific values may be selected as needed, which is not illustrated. By limiting the radial depth of the second oil groove 114, it is possible to ensure that the second oil groove 114 has a sufficient oil storage space, and the lubricating oil can smoothly enter the second oil groove 114 and smoothly move in the second oil groove 114, so as to ensure continuous and reliable lubrication between the supporting surface 23 and the thrust surface 122, and avoid the influence on the strength of the crankshaft 1 due to the excessive radial depth, thereby ensuring the structural reliability of the whole pump assembly 100.

Alternatively, the radial depth of the second oil groove 114 is uniform all over the circumferential direction, that is, the bottom wall of the second oil groove 114 is an arc-shaped surface which is coaxial with the main shaft 11. This is for the purpose of uniform oil storage around the circumference of the second oil groove 114 and easier manufacturing.

As shown in fig. 4 and 5, in one embodiment, the third oil groove 115 extends vertically in the axial direction of the main shaft 11. This is intended to minimize the axial length of the vertically extending third oil groove 115, enabling the lubricating oil to reach the second oil groove 114 via the shortest distance. And also facilitates the manufacturing of the third oil groove 115. Of course, in other alternative embodiments, it is also possible that the third oil groove 115 is provided to extend obliquely with respect to the axial direction of the main shaft 11, and the setting can be specifically set according to the structural requirement. Based on this, as shown in fig. 5, the axial height H2 of the third oil groove 115 can be determined according to the upper end position of the spiral oil groove 113 and the axial width H1 of the second oil groove 114, and for example, can be 0.5mm to 5mm, specifically, 1mm to 3mm, etc., and it is understood that this is only an example and is not particularly limited.

In one embodiment, the radial depth D3 of the third oil groove 115 also determines its oil storage capability and its effect on the strength of the spindle 11. In one embodiment, as shown in fig. 6, the radial depth D3 of the third oil groove 115 is 0.1mm to 3mm, and optionally, the radial depth D3 of the third oil groove 115 is 0.1mm to 1mm, specifically, 0.1mm, 0.2mm, 0.5mm, 0.8mm, and the like, and specific values may be selected as needed, and are not illustrated. By limiting the radial depth D3 of the third oil groove 115, it is possible to ensure that the third oil groove 115 has a sufficient oil storage space, and the lubricating oil can smoothly enter the third oil groove 115 and smoothly move in the third oil groove 115, so that the lubricating oil can be ensured to continuously and reliably flow to the second oil groove 114 through the third oil groove, and the strength of the crankshaft 1 can be prevented from being affected by the excessive radial depth, and the structural reliability of the pump assembly 100 as a whole can be ensured.

The cross-sectional shape of the third oil groove 115 may be a triangle with a wide outer part and a narrow inner part, or a trapezoid, an arc, etc. with a wide outer part and a narrow inner part, that is, the first oil groove 231 is in an outward-expanding opening shape; alternatively, the cross-sectional shape of the first oil groove 231 may be a rectangular shape or the like; still alternatively, as shown in fig. 6, the radial depth D3 of the first oil groove 231 is kept uniform throughout the axial direction, that is, the bottom wall of the third oil groove 115 is an arc-shaped surface which is coaxial with the main shaft 11, so that the oil storage is uniform throughout the third oil groove 115. In a particular product application, the cross-sectional shape of third oil groove 115 may be configured as desired, generally to facilitate manufacturing and to ensure smooth and uniform flow of the lubricating oil.

As shown in fig. 5 and 7, the crankshaft 1 is further provided with an auxiliary oil passage including a second oil hole 116 communicating with the oil spiral groove 113 and penetrating inward, a passage (not shown) extending upward from the inside of the main shaft 11 into the eccentric shaft 13, and a third oil hole (not shown) formed in the eccentric shaft 13 and penetrating through the eccentric shaft 13. Wherein the second oil hole 116 may be disposed at an upper end of the spiral oil groove 113 and communicate with the third oil groove 115. In this way, when the lubricating oil moves upward in the helical oil groove 113 and reaches the upper end of the helical oil groove 113, the lubricating oil is divided into two paths, one of which reaches the first oil groove 231 via the third oil groove 115 and the second oil groove 114 as described above, and the other of which enters the passage via the second oil hole 116 and is thrown off from the third oil hole, so as to lubricate the outer peripheral surface of the eccentric shaft 13.

Referring to fig. 1, 2 and 7, a support boss 22 surrounding the crank hole 21 is disposed on a side of the case 2 facing the counterweight 12, a surface of the support boss 22 is a support surface 23, in other words, the support surface 23 protrudes relative to other positions around the crank hole 21 on the case 2, and the counterweight 12 abuts against the boss and only abuts against the support surface 23 without being worn to other positions of the case 2.

As shown in fig. 2, in one embodiment, the first oil groove 231 extends along a radial direction of the crank hole 21, and the first oil groove 231 has a substantially straight bar shape. This is provided for the purpose of relatively easy manufacturing of the first oil groove 231. Of course, in other usable embodiments, the first oil groove 231 may extend along a straight line inclined with respect to the radial direction of the crankshaft hole 21, or may extend in a curved shape, such as an arc-shaped extension, a wave-shaped extension, or even extend around the crankshaft hole 21, which allows the first oil groove 231 to have a larger extension length and oil storage space, and thus, more lubricating oil can be stored. In practical product application, the extending shape of the first oil groove 231 is preferably set by comprehensively considering the processing and manufacturing difficulty and the oil storage space thereof, so as to ensure that the processing cost is not obviously increased and a good lubricating effect can be ensured.

The first oil groove 231 penetrates the inner circumferential surface of the support boss 22 and communicates with the crank hole 21. The first oil groove 231 may penetrate the outer circumferential surface of the support boss 22, which facilitates the machining and manufacturing of the first oil groove 231 and ensures the lubrication of the entire region of the support surface 23 with relative reliability. Of course, without being limited thereto, in other alternative embodiments, it is also possible that the first oil groove 231 does not penetrate to the outer circumferential surface of the support boss 22 according to specific needs.

In one embodiment, as shown in fig. 2, the first oil groove 231 extends in a radial direction of the crank hole 21 and penetrates to an outer surface of the support boss 22.

As shown in fig. 3, the axial depth D1 of the first oil groove 231 is 0.1mm to 3mm, and optionally, the axial depth D1 of the first oil groove 231 is 0.1mm to 1mm, specifically, 0.1mm, 0.2mm, 0.5mm, 0.8mm, and the like, and specific values may be selected as needed, which is not illustrated one by one. Through carrying out above-mentioned injecing to the axial depth D1 of first oil groove 231, can enough guarantee that first oil groove 231 has sufficient oil storage space, lubricating oil can get into first oil groove 231 smoothly and flow in first oil groove 231 to guarantee to last, reliably lubricate between holding surface 23 and the thrust surface 122, can avoid again because of the radial depth is too big influencing the intensity of support boss 22 and the intensity of box 2, guarantee the holistic structural reliability of crankcase.

Wherein, as shown in fig. 2, 3 and 7, the axial depth D1 of the first oil groove 231 is smaller than the axial height of the support boss 22. This is provided to ensure the structural strength of the support boss 22.

As shown in fig. 2 and 3, the cross-sectional shape of the first oil groove 231 may be a triangle with a wide outside and a narrow inside, or a trapezoid with a wide outside and a narrow inside, an arc, or the like, that is, the first oil groove 231 is in an outward-expanding opening shape; alternatively, the cross-sectional shape of the first oil groove 231 may be a rectangular shape, and the cross-sectional shape may be set according to the processing technology and the actual requirements, and is not particularly limited herein. The inner walls of the first oil grooves 231 are smoothly transited and connected (especially for the above-mentioned cross-sectional shapes except for the arc shape), and the connection between the first oil grooves 231 and the supporting surface 23 is smoothly transited and connected, so as to avoid the wear of the supporting boss 22 and the counterweight 12 caused by the defects of the residual material, the burr on the supporting surface 23, and the like.

It should be noted that the number of the first oil grooves 231 on the support surface 23 is not limited to one, and may be plural, and the extension shape, the axial depth D1, the cross-sectional shape, and the like of each first oil groove 231 may be independently set according to the foregoing embodiments, and the interval between the first oil grooves 231 is preferably set so as not to affect the strength of the part of the support boss 22 remaining therebetween.

In addition, the present embodiment also provides a compressor (not shown) including a motor and the pump body assembly 100 described in the above embodiments, and the crankcase further includes a connecting rod, a piston, and the like provided on the case 2. Wherein, the rotor of motor is connected with main shaft 11, and the motor drives main shaft 11 and rotates around its own central axis, and then, eccentric shaft 13 and balancing piece 12 also rotate around the central axis of main shaft 11 eccentrically correspondingly. The eccentric shaft 13 is further connected to a piston via a connecting rod (not shown), and the eccentric shaft 13 drives the piston to reciprocate in the cylinder via the connecting rod.

The compressor with the pump body assembly 100 has the advantages that the lubrication between the crankshaft 1 and the box body 2 of the crankcase is good, the friction power consumption is low, the abrasion degree of the crankshaft 1 and the crankcase can be reduced, the assembly cost is low, and the material cost is low.

The compressor is particularly a reciprocating compressor which can be applied to refrigeration equipment such as refrigerators, freezers and the like.

The above description is only exemplary of the present application and should not be taken as limiting the present application, as any modification, equivalent replacement, or improvement made within the spirit and principle of the present application should be included in the protection scope of the present application.

Claims (10)

1. A pump body assembly comprises a crankshaft and a crankcase, wherein the crankcase comprises a box body, a crankshaft hole is formed in the box body, the crankshaft comprises a main shaft, a balance block and an eccentric shaft which are sequentially connected, the main shaft penetrates through the crankshaft hole, a thrust surface is arranged on one side, facing the box body, of the balance block in a surrounding mode of the main shaft, and a supporting surface is arranged on one side, facing the balance block, of the box body in a surrounding mode of the crankshaft hole;

the crankshaft structure is characterized in that a first oil groove is concavely arranged on the supporting surface and communicated with the crankshaft hole; the main shaft is provided with a main oil way which is formed by an end face of one end, deviating from the eccentric shaft, of the main shaft, a second oil groove is concavely formed in the peripheral surface of the main shaft, the second oil groove is annularly formed along the circumferential direction of the main shaft, one side, close to the balance block, of the second oil groove is communicated to the thrust surface, and the second oil groove is further communicated with the main oil way.

2. The pump body assembly according to claim 1, wherein a side of the case body facing the weight is provided with a support boss surrounding the crank hole, a surface of the support boss being the support surface; the first oil groove penetrates through the inner circumferential surface and the outer circumferential surface of the support boss.

3. The pump body assembly according to claim 2, wherein the axial depth of the first oil groove is 0.1mm to 3mm, and the axial depth of the first oil groove is smaller than the axial height of the support boss.

4. The pump body assembly of claim 1, wherein the first oil groove extends radially of the crankshaft bore.

5. The pump body assembly according to claim 1, wherein the radial depth of the second oil groove is 0.1mm to 3mm, and the radial depth of the second oil groove is uniform all over the circumferential direction.

6. The pump block assembly according to any one of claims 1 to 5, wherein the main oil passage includes an oil chamber opened from an end surface of the main shaft that faces away from the eccentric shaft and formed inside the main shaft, a first oil hole opened from an outer surface of the main shaft and penetrating to the oil chamber, and a helical oil groove formed on the outer surface of the main shaft, communicating with the first oil hole, and extending helically toward the balance weight; one side of the second oil groove, which is far away from the balance block, is communicated with the spiral oil groove.

7. The pump body assembly according to claim 6, wherein a third oil groove is further recessed in the outer peripheral surface of the main shaft, and the third oil groove is communicated between the spiral oil groove and a side of the second oil groove facing away from the balance weight; the third oil groove extends along the axial direction of the main shaft or obliquely extends relative to the axial direction of the main shaft.

8. The pump body assembly according to claim 7, wherein the second oil groove has an axial width of 0.5mm to 3 mm; and/or the axial height of the third oil groove is 0.5 mm-5 mm.

9. The pump body assembly according to claim 7, wherein the third oil groove has a radial depth of 0.1mm to 3mm, and the radial depth of the third oil groove is uniform throughout the axial direction.

10. A compressor, comprising a motor and a pump body assembly according to any one of claims 1 to 9, the pump body assembly further comprising a connecting rod, a piston and a cylinder, the connecting rod, the piston and the cylinder being disposed on a side of the casing facing away from the main shaft; the motor is connected with the main shaft, the eccentric shaft is connected with the connecting rod, and the piston is driven to move in the cylinder.

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