A vehicle compressor and split type shaft sleeve thereof

Abstract

The application provides a scroll compressor for vehicles and a balance block structure thereof, and belongs to the technical field of scroll compressors for vehicles.The scroll compressor for vehicles comprises a shaft sleeve outer ring, an outer edge of the shaft sleeve outer ring is matched with a dynamic scroll needle bearing gap of the scroll compressor for vehicles, and the shaft sleeve outer ring comprises a first through hole which is axially through the shaft sleeve outer ring; a shaft sleeve inner ring is located in the first through hole, an outer edge of the shaft sleeve inner ring is matched with an inner edge of the shaft sleeve outer ring in a gap mode, the shaft sleeve inner ring comprises a second through hole which is axially through the shaft sleeve inner ring, and the shaft sleeve inner ring is sleeved with an eccentric crankshaft of the scroll compressor for vehicles through the second through hole.The application can prolong the service life of the shaft sleeve part and reduce the wear resistance requirement of the shaft sleeve body material.

Description

TECHNICAL FIELD

[0001] The present application relates to the field of compressors, in particular to a split type shaft sleeve of a vehicle compressor. BACKGROUND

[0002] Compared with deep groove ball bearings of the same volume, needle bearings, especially needle bearings without inner rings, have the characteristics of small volume and strong load capacity, and are widely used in compressor products. The application of needle bearings without inner rings helps to realize the small and light design of compressors. When using needle bearings without inner rings, a shaft sleeve is needed to play the role of the inner ring of the bearing. In order to ensure the service life of the shaft sleeve and the bearing, the material selection and design of the shaft sleeve are very important, and the shaft sleeve material should have very strong wear resistance. Usually, bearing steel or similar high-hardness high-quality steel materials are selected, and heat treatment or surface coating technology is used to improve wear resistance. In the cooperation of the shaft sleeve and the needle bearing without the inner ring, the load bearing part of the shaft sleeve is fixed, that is, it always bears at the same position, and long-term high-load operation can easily cause material fatigue spalling and lead to wear failure; the inner side of the shaft sleeve is irregular, and if the surface roughness level of the bearing outer ring is to be improved, the processing technology has high requirements.

[0003] Therefore, how to prolong the service life of the shaft sleeve part and reduce the wear resistance requirement of the shaft sleeve body material is a technical problem to be solved by those skilled in the art. SUMMARY

[0004] In order to overcome the defects of the prior art, the present application provides a vehicle compressor and a split type shaft sleeve thereof, so as to prolong the service life of the shaft sleeve part and reduce the wear resistance requirement of the shaft sleeve body material.

[0005] The present application provides a split type shaft sleeve applied to a vehicle compressor, comprising:

[0006] A shaft sleeve outer ring, an outer edge of the shaft sleeve outer ring is gap-fitted with a needle bearing of a moving scroll of the vehicle compressor, and the shaft sleeve outer ring comprises a first through hole axially penetrating the shaft sleeve outer ring;

[0007] A shaft sleeve inner ring, the shaft sleeve inner ring is located in the first through hole, an outer edge of the shaft sleeve inner ring is gap-fitted with an inner edge of the shaft sleeve outer ring, the shaft sleeve inner ring comprises a second through hole axially penetrating the shaft sleeve inner ring, and the shaft sleeve inner ring is sleeved with an eccentric crankshaft of the vehicle compressor through the second through hole.

[0008] In some embodiments of the present application, there is a friction force between the outer edge of the shaft sleeve inner ring and the inner edge of the shaft sleeve outer ring, and in response to a force applied to the inner edge of the shaft sleeve inner ring / a force applied to the outer edge of the shaft sleeve outer ring being greater than the friction force, the shaft sleeve inner ring and the shaft sleeve outer ring rotate relatively.

[0009] In some embodiments of the present application, a gap between the outer edge of the shaft sleeve outer ring and the rolling needle bearing of the orbiting scroll of the vehicle compressor is greater than or equal to 0 microns and less than or equal to 50 microns.

[0010] In some embodiments of the present application, a gap between the outer edge of the shaft sleeve inner ring and the inner edge of the shaft sleeve outer ring is greater than or equal to 0 microns and less than or equal to 50 microns.

[0011] In some embodiments of the present application, the shaft sleeve inner ring is integrated with the balance block of the orbiting scroll of the vehicle compressor.

[0012] In some embodiments of the present application, an end of the shaft sleeve outer ring, which faces away from the balance block of the orbiting scroll, includes a ring piece that extends from the inner edge of the shaft sleeve outer ring to the crankshaft.

[0013] According to yet another aspect of the present application, there is also provided a vehicle compressor, comprising:

[0014] a housing having a receiving space;

[0015] a compression mechanism located in the receiving space, the compression mechanism including a fixed scroll and an orbiting scroll;

[0016] an electric mechanism located in the receiving space, including a motor rotor and a motor stator, the electric mechanism driving the orbiting scroll to rotate relative to the fixed scroll to compress a refrigerant in the compression chamber;

[0017] an eccentric crankshaft coupled to the motor rotor of the electric mechanism and the orbiting scroll to transmit a rotational force of the motor rotor, respectively;

[0018] a split shaft sleeve as described above, the eccentric crankshaft being coupled to the orbiting scroll through the split shaft sleeve and the rolling needle bearing of the orbiting scroll.

[0019] In some embodiments of the present application, an end of the eccentric crankshaft, which is coupled to the orbiting scroll, includes an annular groove and a retainer ring located in the annular groove, the retainer ring protruding from the outer edge of the eccentric crankshaft in the radial direction of the eccentric crankshaft, and the height of the retainer ring protruding from the outer edge of the eccentric crankshaft in the radial direction of the eccentric crankshaft is less than the radial width of the outer edge of the shaft sleeve outer ring.

[0020] In some embodiments of the present application, there is also provided:

[0021] a gasket located between the split shaft sleeve and the retainer ring.

[0022] In some embodiments of the present application, the end of the outer ring of the split bearing away from the balance block of the orbiting scroll comprises a ring, which extends from the inner edge of the outer ring of the split bearing to the crankshaft, and the ring is located between the inner ring of the split bearing and the retainer.

[0023] Compared with the prior art, the present application has the following advantages:

[0024] The present application prolongs the service life of the split bearing by making the split bearing comprise an inner ring and an outer ring, so that the outer ring can alternately bear different parts, and reduces the wear resistance requirement of the material of the inner ring and the process difficulty of the inner ring, thereby reducing the material cost. BRIEF DESCRIPTION OF DRAWINGS

[0025] The above and other features and advantages of the present application will become more apparent by describing in detail example embodiments thereof with reference to the attached drawings in which:

[0026] Figure 1 A perspective view of a compressor according to an embodiment of the present application is shown.

[0027] Figure 2 A cross-sectional view of a compressor according to an embodiment of the present application is shown.

[0028] Figure 3 A cross-sectional view of a crankshaft, a split bearing, and a connection of a needle bearing according to an embodiment of the present application is shown.

[0029] Figure 4 A schematic view of a crankshaft, a split bearing, and a connection of a needle bearing according to an embodiment of the present application is shown.

[0030] Figure 5 A partial enlarged view of Figure 3 is shown.

[0031] Figure 6 A schematic view of a crankshaft, a split bearing, and a connection of a needle bearing according to another embodiment of the present application is shown.

[0032] Figure 7 A partial enlarged view of Figure 6 is shown. DETAILED DESCRIPTION

[0033] Example embodiments now will be described more fully hereinafter with reference to the accompanying drawings. Example embodiments, however, can be implemented in many different forms and should not be construed as limited to the embodiments set forth herein; rather, these embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the scope of the example embodiments to those skilled in the art. Like reference numerals refer to like elements throughout the several views.

[0034] To improve the defects of the prior art, the present application provides a vehicle compressor, preferably a scroll compressor for electric vehicles, but the compressor provided by the present application is not limited to electric vehicles. The compressor provided by the present application is of a horizontal structure, i.e. the shaft transmission mechanism and the scroll pump body axis are arranged horizontally.

[0035] Firstly, referring to Figures 1-2 , Figures 1-2 The compressor according to the embodiment of the present application is shown. Figure 1 The compressor according to the embodiment of the present application is shown. Figure 2 The compressor according to the embodiment of the present application is shown.

[0036] In the embodiment, the compressor comprises a housing 110, a compression mechanism, an electric mechanism, an eccentric crankshaft 7 and a balance block structure. The housing 110 has a containing space. The compression mechanism is located in the containing space, and the compression mechanism comprises a static scroll 130 and a dynamic scroll 140. The static scroll 130 is provided with first scroll teeth 131. The dynamic scroll 140 is provided with second scroll teeth 141, and one side of the dynamic scroll 140 provided with the second scroll teeth 141 is opposite to the first scroll teeth 131 of the static scroll 130. The first scroll teeth 131 of the static scroll 130 and the second scroll teeth 141 of the dynamic scroll 140 form a compression chamber. The side of the static scroll 130 away from the dynamic scroll 140 forms an exhaust chamber with the front housing 110. The side of the dynamic scroll 140 away from the static scroll 130 forms a low-pressure chamber with the rear housing (not shown in the figure). The electric mechanism is located in the containing space, and the electric mechanism comprises a motor rotor 5 and a motor stator 160. The electric mechanism drives the dynamic scroll 140 to rotate relative to the static scroll 130 to compress the refrigerant in the compression chamber. The eccentric crankshaft 7 is coupled to the motor rotor 5 of the electric mechanism and the dynamic scroll 140 to transmit the rotating force of the motor rotor 5. The eccentric crankshaft 7 is coupled to the dynamic scroll 140 through the split shaft sleeve and the dynamic scroll needle bearing.

[0037] Figure 3 The cross-sectional view of the connection of the crankshaft, the split shaft sleeve and the needle bearing according to the embodiment of the present application is shown. The split shaft sleeve comprises a shaft sleeve outer ring 11 and a shaft sleeve inner ring 12. The outer edge of the shaft sleeve outer ring 11 is in clearance fit with the dynamic scroll needle bearing 142 of the vehicle compressor. The shaft sleeve outer ring 11 comprises a first through hole axially penetrating the shaft sleeve outer ring 11. The shaft sleeve inner ring 12 is located in the first through hole, and the outer edge of the shaft sleeve inner ring 12 is in clearance fit with the inner edge of the shaft sleeve outer ring 11. The shaft sleeve inner ring 12 comprises a second through hole axially penetrating the shaft sleeve inner ring 12, and the shaft sleeve inner ring 12 sleeves the eccentric crankshaft 7 of the vehicle compressor through the second through hole.

[0038] Thus, the outer edge of the inner ring of the bushing and the inner edge of the outer ring of the bushing have a frictional force therebetween, and in response to a force applied to the inner edge of the inner ring of the bushing / force applied to the outer edge of the outer ring of the bushing being greater than the frictional force, the inner ring of the bushing and the outer ring of the bushing rotate relatively.

[0039] In a specific embodiment, when the compressor is running smoothly, the inner edge of the outer ring of the bushing 11 and the outer edge of the inner ring of the bearing 12 do not move relatively. When the compressor is used on a vehicle, it will be affected by external vibrations. Under the influence of the vibrations, the inner edge of the outer ring of the bushing 11 and the outer edge of the inner ring of the bearing 12 will move relatively, thereby enabling the outer ring of the bushing 11 to bear alternately at different positions, thereby prolonging the service life of the bushing part. When the bearing surface of the outer ring of the bushing 11 is worn for a long time, the frictional force of the bearing surface will increase. When the frictional force is greater than the frictional force between the inner edge of the outer ring of the bushing 11 and the inner ring of the bushing 12, the inner edge of the outer ring of the bushing 11 and the outer edge of the inner ring of the bearing 12 will move relatively, adjusting the position of the bearing surface of the outer ring of the bushing 11, thereby prolonging the service life of the bushing part. In addition, under the drive of the crankshaft eccentric pin 71 of the eccentric crankshaft 7, the inner ring of the bushing 12 is driven due to the frictional force between the inner ring of the bushing 12 and the outer ring of the bushing 11, thereby enabling the outer ring of the bushing 11 to be driven, so that the tangential frictional force between the outer ring of the bushing 11 and the needle bearing 142 enables the outer ring of the bushing 11 to form a sliding fit with respect to the needle bearing 142. In this way, the outer ring of the bushing 11 is no longer always bearing at the same position, and the rotating bushing can achieve alternate bearing at different positions, thereby prolonging the service life of the bushing part.

[0040] In some preferred embodiments, the gap between the outer edge of the outer ring of the bushing 11 and the needle bearing 142 of the moving vane plate of the vehicle compressor is greater than or equal to 0 microns and less than or equal to 50 microns. The gap between the outer edge of the inner ring of the bushing 12 and the inner edge of the outer ring of the bushing 11 is greater than or equal to 0 microns and less than or equal to 50 microns. Thus, the requirements of the gap fit are met.

[0041] Further, the inner ring of the bushing 12 can form an integrated balance block 144 with the balance block 143 of the moving vane plate of the vehicle compressor. Specifically, after the bushing is divided into two parts, the requirements for the bushing are reduced, and the integrated manufacturing of the bushing and the balance block can be achieved, thereby reducing the cost. In addition, after the bushing and the balance block are integrated, the centrifugal force acting on the moving disc assembly as a whole is reduced, and the stress condition of the vane plate profile under high speed can be improved.

[0042] Further, the end of the outer ring of the bushing 11 away from the balance block 143 of the moving vane plate includes a ring piece, which extends from the inner edge of the outer ring of the bushing 11 to the crankshaft 7. Thus, the axial positioning of the bushing can be achieved through the ring piece.

[0043] The following will be described in detail with reference to the accompanying drawings. Figure 4 and Figure 5, Figure 6 and Figure 7 to describe the limiting design provided by the present application.

[0044] Firstly, refer to Figure 4 and Figure 5 , Figure 4 Fig. 1 shows a schematic diagram of the connection of a crankshaft, a split bearing bush and a needle bearing according to an embodiment of the present application. Figure 5 Fig. 2 shows a partial enlarged view of Figure 4 .

[0045] In the present embodiment, the end 71 of the eccentric crankshaft 7 connecting the moving scroll 140 comprises a ring-shaped groove 14 and a retainer ring 13 located in the ring-shaped groove 14. The retainer ring 13 protrudes from the outer edge of the eccentric crankshaft 7 in the radial direction of the eccentric crankshaft 7, and the height of the protrusion of the retainer ring 13 from the outer edge of the eccentric crankshaft 7 in the radial direction of the eccentric crankshaft 7 is less than the radial width of the outer edge of the bearing bush outer ring 11. Thus, the axial limiting of the bearing bush can be achieved by the cooperation of the retainer ring 13 and the ring-shaped groove 14. Further, the retainer ring 13 and the bearing bush outer ring 11 are in clearance fit.

[0046] In the present embodiment, one end of the bearing bush outer ring 11 opposite to the moving scroll balance block 143 comprises a ring-shaped piece extending from the inner edge of the bearing bush outer ring 11 to the crankshaft, and the ring-shaped piece is located between the bearing bush inner ring 12 and the retainer ring 13. Thus, the cross section of the bearing bush outer ring 11 is L-shaped, so that the axial limiting of the bearing bush can be achieved by the cooperation of the retainer ring 13 and the ring-shaped piece of the bearing bush outer ring 11.

[0047] Next, refer to Figure 6 and Figure 7 , Figure 6 Fig. 4 shows a schematic diagram of the connection of a crankshaft, a split bearing bush and a needle bearing according to another embodiment of the present application. Figure 7 Fig. 5 shows a partial enlarged view of Figure 6 .

[0048] In the present embodiment, the end 71 of the eccentric crankshaft 7 connecting the moving scroll 140 comprises a ring-shaped groove 14 and a retainer ring 13 located in the ring-shaped groove 14. The retainer ring 13 protrudes from the outer edge of the eccentric crankshaft 7 in the radial direction of the eccentric crankshaft 7, and the height of the protrusion of the retainer ring 13 from the outer edge of the eccentric crankshaft 7 in the radial direction of the eccentric crankshaft 7 is less than the radial width of the bearing bush inner ring 12. Thus, the axial limiting of the bearing bush can be achieved by the cooperation of the retainer ring 13 and the ring-shaped groove 14.

[0049] In the present embodiment, the gasket 15 is arranged between the split bearing bush and the retainer ring 13, so that the axial limiting of the bearing bush can be achieved by the cooperation of the retainer ring 13 and the gasket 15.

[0050] Further, in the present embodiment, the blocking ring 13 is in a clearance fit with the gasket 15, the gasket 15 and the outer sleeve 11.

[0051] The above merely illustrates the implementation manners of the present application, and the present application is not limited thereto, and each embodiment can be implemented alone or in combination.

[0052] Compared with the prior art, the present application has the following advantages:

[0053] The present application prolongs the working life of the sleeve part by making the split sleeve include the inner sleeve and the outer sleeve, so that the outer sleeve can realize the alternate bearing of different parts; at the same time, the wear resistance requirement of the material of the inner sleeve and the process difficulty of the inner sleeve are reduced, and the material cost is reduced.

[0054] The exemplary embodiments of the present application are specifically shown and described above. It should be understood that the present application is not limited to the disclosed embodiments, but rather the present application is intended to cover various modifications and equivalent arrangements included within the scope of the appended claims.

Claims

1. A split type shaft bushing applied to a vehicle compressor, characterized by, include: a shaft sleeve outer ring, wherein the outer edge of the shaft sleeve outer ring is clearance-matched with the movable scroll needle roller bearing of the vehicle compressor, and the shaft sleeve outer ring includes a first through hole axially extending through the shaft sleeve outer ring; The inner ring of the sleeve is located in the first through hole, and the outer edge of the inner ring of the sleeve is clearance-matched with the inner edge of the outer ring of the sleeve. The inner ring of the sleeve includes a second through hole axially extending through the inner ring of the sleeve. The inner ring of the sleeve is sleeved with the eccentric crankshaft of the vehicle compressor through the second through hole. The gap between the outer edge of the inner ring of the sleeve and the inner edge of the outer ring of the sleeve is greater than or equal to 0 microns and less than or equal to 50 microns. The gap between the outer edge of the outer ring of the sleeve and the movable scroll needle roller bearing of the vehicle compressor is greater than or equal to 0 microns and less than or equal to 50 microns.

2. The split bushing of claim 1, wherein, There is friction between the outer edge of the inner ring of the sleeve and the inner edge of the outer ring of the sleeve. In response to the force applied to the inner edge of the inner ring of the sleeve / the force applied to the outer edge of the outer ring of the sleeve being greater than the friction, the inner ring of the sleeve and the outer ring of the sleeve rotate relatively.

3. The split bushing of claim 1, wherein, The shaft sleeve inner ring and the movable scroll balance block of the vehicle compressor form an integrated balance block.

4. The split bushing of claim 1, wherein, One end of the shaft sleeve outer ring facing away from the movable scroll balance block comprises an annular piece, and the annular piece extends from the inner edge of the shaft sleeve outer ring toward the crankshaft.

5. A vehicle compressor characterized by comprising: include: A housing having a receiving space; A compression mechanism is located in the accommodating space, and the compression mechanism includes a fixed scroll and a movable scroll; an electric mechanism, located in the accommodating space, comprising a motor rotor and a motor stator, wherein the electric mechanism drives the movable scroll to rotate relative to the fixed scroll to compress the refrigerant in the compression chamber; an eccentric crankshaft, respectively connected to the motor rotor of the electric mechanism and the movable scroll to transmit the rotational force of the motor rotor; According to the split sleeve according to any one of claims 1 to 4, the eccentric crankshaft is connected to the movable scroll through the split sleeve and the movable scroll needle roller bearing.

6. The compressor for an automobile as set forth in claim 5, wherein The end of the eccentric crankshaft connected to the movable scroll includes an annular groove and a retaining ring located in the annular groove, the retaining ring protrudes from the outer edge of the eccentric crankshaft in the radial direction of the eccentric crankshaft, and the height of the retaining ring protruding from the outer edge of the eccentric crankshaft in the radial direction of the eccentric crankshaft is less than the radial width of the outer edge of the outer ring of the sleeve.

7. The compressor for an automobile as set forth in claim 6, wherein Also includes: A washer is located between the split shaft sleeve and the retaining ring.

8. The compressor for an automobile as set forth in claim 6, wherein One end of the shaft sleeve outer ring facing away from the movable scroll balance block includes an annular plate, which extends from the inner edge of the shaft sleeve outer ring toward the crankshaft and is located between the shaft sleeve inner ring and the retaining ring.

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