Scroll compressor

Abstract

The present invention discloses a scroll compressor, comprising: a movable scroll component (20), wherein the movable scroll component (20) has an end plate (22); and a thrust plate (80), wherein the thrust plate (80) is configured to axially support the movable scroll component (20), wherein the end plate (22) has a first thrust surface (21) that contacts with and slides relative to the thrust plate (80), and the thrust plate (80) has a second thrust surface (81) for contacting and supporting the first thrust surface (21), and an annular groove (23) is formed on the radially inner side adjacent to the first thrust surface (21), and the outer diameter R of the annular groove (23) is 1 / 4 of the first thrust surface (21). a Satisfy the following parameter relationship: R b ‑R or <R a <R b +R or , where R b is the inner diameter of the thrust plate (80), R or The radius of gyration of the movable scroll component (20) relative to the thrust plate (80) is defined as the radius of gyration of the movable scroll component (20) relative to the thrust plate (80). The scroll compressor can reduce damage to the thrust surface of the thrust plate.

Description

Technical Field

[0001] The present invention relates to a thrust plate for a scroll compressor and a scroll compressor including the thrust plate. Background Art

[0002] In a scroll compressor, compression of a fluid is achieved by relative movement between a moving scroll member and a stationary scroll member. In order to provide axial support for the moving scroll member, a thrust plate is provided on one side of an end plate of the moving scroll member. The thrust plate is fixed to the scroll compressor housing. When the scroll compressor operates, the moving scroll member moves relative to the thrust plate. Sufficient lubrication is required between the contact surface (thrust surface) of the end plate of the moving scroll member and the thrust plate to reduce the friction and wear therebetween. At present, most of the lubrication structures adopted between the end plate of the moving scroll member and the thrust surface of the thrust plate have defects such as complex structures, insufficient lubrication, or severe wear of the thrust surface.

[0003] Therefore, there is a need in the art for an oil circuit arrangement or design for a scroll compressor that can supply lubricant more efficiently and does not damage the thrust surface. Summary of the Invention

[0004] One or several embodiments of the present invention provide a scroll compressor that can supply lubricant to a thrust surface more efficiently and does not damage the thrust surface.

[0005] One or several embodiments of the present invention provide a scroll compressor, including: a moving scroll member having an end plate; and a thrust plate configured to axially support the moving scroll member, wherein the end plate has a first thrust surface that contacts and slides relative to the thrust plate, the thrust plate has a second thrust surface for contacting and supporting the first thrust surface, an annular groove is formed radially inside adjacent to the first thrust surface, and an outer diameter R of the annular groove a satisfies the following parameter relationship: R b -R or <R a <R b +R or , where R b is the inner diameter of the second thrust surface of the thrust plate, and R or is the radius of gyration of the moving scroll member relative to the translational rotation of the thrust plate. This parameter setting can achieve: in a region where the contact stress between the moving scroll member and the thrust plate is small or there is no contact stress, the annular groove contacts the radial inner side of the thrust surface of the thrust plate, and the lubricant in the annular groove is brought to the thrust surface of the thrust plate as the moving scroll member makes translational rotation. In addition, since the annular oil groove is in a region with small stress, defects such as burrs on the edges of the annular groove can be reduced from damaging the thrust surface of the thrust plate.

[0006] Furthermore, the outer diameter R of the annular groove a satisfies the following parameter relationship: R a = R b - 0.5R or . Under this parameter condition, the best balance can be achieved between the supply of lubricant from the annular groove to the thrust surface of the thrust plate and the reduction of damage to the thrust surface of the thrust plate caused by defects such as burrs on the edge of the annular groove.

[0007] Furthermore, the cross-sectional shape of the annular groove is V-shaped or U-shaped.

[0008] Furthermore, the annular grooves are a plurality of concentrically arranged annular grooves.

[0009] Furthermore, a plurality of radial channels for fluidly connecting the plurality of annular grooves are provided at intervals in the circumferential direction on the annular groove. The radial channels facilitate the flow of lubricant in the plurality of annular grooves and further guide the lubricant to the thrust surface of the moving scroll member.

[0010] Furthermore, the plurality of radial channels are arranged at equal intervals in the circumferential direction.

[0011] Furthermore, the plurality of annular grooves are arranged at equal intervals in the radial direction.

[0012] Furthermore, a hub portion is provided on the radial inner side of the first thrust surface of the moving scroll member, and the plurality of radial channels extend in the radially inward direction to the junction of the hub portion and the first thrust surface, so as to facilitate guiding the lubricant conveyed along the outer side of the hub portion into the annular groove.

[0013] Furthermore, it further includes a bearing sleeve for supporting the thrust plate, and the thrust plate is fixed to the bearing sleeve or formed as an integral part with the bearing sleeve.

[0014] Furthermore, the radial inner side of the thrust plate adjacent to the second thrust surface has a rounded corner. BRIEF DESCRIPTION OF THE DRAWINGS

[0015] Through the following description with reference to the drawings, the features and advantages of one or several embodiments of the present invention will become more easily understood, wherein:

[0016] Figure 1 is a cross-sectional view of a scroll compressor according to the first embodiment of the present invention;

[0017] Figure 2 is an enlarged view near the moving scroll member of the scroll compressor according to the first embodiment of the present invention;

[0018] Figure 3AIs a perspective view of a moving scroll member according to a first embodiment of the present invention, Figure 3B is a cross-sectional view of a moving scroll member according to a first embodiment of the present invention; Figure 3C Is Figure 3B An enlarged cross-sectional view of the annular groove portion in; Figure 3D Is Figure 3B An enlarged cross-sectional view of a modification of the annular groove in.

[0019] Figure 4 Is a relationship view of the mutual movement of the thrust plate and the moving scroll member according to the first embodiment of the present invention.

[0020] Figure 5A Is a perspective view of an example of the thrust plate; Figure 5B Is a perspective view of another example of the thrust plate.

[0021] Figure 6A Is a perspective view of a moving scroll member according to a second embodiment of the present invention, Figure 6B is a cross-sectional view of a moving scroll member according to a second embodiment of the present invention;

[0022] Figure 7 Is a cross-sectional view of a scroll compressor according to the first embodiment of the present invention;

[0023] Figure 8 Is an enlarged view near the moving scroll member of the scroll compressor according to the first embodiment of the present invention. Detailed Embodiments

[0024] The following descriptions of various embodiments of the present invention are merely exemplary and in no way limit the present invention or its application or use. The same reference numerals are used in the respective drawings to denote the same components, and thus the construction of the same components will not be described repeatedly.

[0025] Now reference will be made to Figure 1 Describe the basic construction and operating principle of a scroll compressor according to a first embodiment of the present invention. The scroll compressor 10 includes a generally cylindrical housing 12. An intake joint (not shown) is provided on the housing 12 for sucking in low-pressure gaseous refrigerant. One end of the housing 12 is fixedly connected to an end cap 14, and the other end is fixedly connected to a bottom cover. The end cap 14 is equipped with a discharge joint for discharging the compressed refrigerant. A partition 16 extending transversely with respect to the housing 12 is further provided between the housing 12 and the end cap 14, thereby dividing the internal space of the compressor into a high-pressure side and a low-pressure side. The space between the end cap 14 and the partition 16 constitutes the high-pressure side space, and the space between the partition 16, the housing 12 and the bottom cover constitutes the low-pressure side space.

[0026] The housing 12 contains a moving scroll member 20 and a stationary scroll member 30 that serve as a compression mechanism, as well as a motor 40 and a drive shaft 50 that serve as a drive mechanism. The compression mechanism can be driven by the drive mechanism and is supported by a bearing housing 70. The bearing housing 70 can be fixed to the housing 12 in any desired manner, such as by riveting at multiple points.

[0027] The moving scroll member 20 includes a moving scroll end plate 22, on one surface of which a spiral blade 24 is provided, and on the other surface a cylindrical hub portion 26 is provided. The stationary scroll member 30 includes a stationary scroll end plate 32 and a spiral blade 34. The spiral blade 24 of the moving scroll member 20 and the spiral blade 34 of the stationary scroll member 30 engage with each other, and when the moving scroll member 20 and the stationary scroll member 30 move relative to each other, a fluid chamber with a gradually decreasing volume from the outside to the center is formed therebetween, thereby compressing the refrigerant in the fluid chamber.

[0028] The motor 40 includes a stator 42 and a rotor 44. The stator 42 is fixedly connected to the housing 12. The rotor 44 is fixedly connected to the drive shaft 50 and rotates within the stator 42. One end of the drive shaft 50 is provided with an eccentric crank pin 52 and a counterweight 60. The counterweight 60 is fixedly provided on the drive shaft 50, so that it can rotate integrally with the drive shaft 50 when the drive shaft 50 rotates. The upper side portion of the drive shaft 50 is supported rotatably by a bearing in the bearing housing 70. The counterweight 60 is located within the bearing housing 70.

[0029] One end of the drive shaft 50 has an eccentric crank pin 52. The eccentric crank pin 52 of the drive shaft 50 is inserted into the hub portion 26 of the moving scroll member 20 via a bushing 58 to rotationally drive the moving scroll member 20. When the moving scroll member 20 moves relative to the stationary scroll member 30, the fluid chamber between the moving scroll member 20 and the stationary scroll member 30 moves from a radially outer position to the central position of the moving scroll member 20 and the stationary scroll member 30 and is compressed. The compressed fluid is discharged via an exhaust port 36 provided at the center of the stationary scroll end plate 32 of the stationary scroll member 30. The other end of the drive shaft 50 may include a concentric hole 54. The concentric hole 54 leads to the eccentric crank pin 52 via an eccentric hole 56, so as to supply lubricant in the bottom oil sump of the compressor to the movable components of the compressor for lubrication.

[0030] A thrust plate 80 is provided between the moving scroll member 20 and the bearing sleeve 70, and the thrust plate 80 can be fixed to the bearing sleeve 70 or integrally formed with the bearing sleeve 70. The thrust plate 80 is used to axially support the moving scroll member 20. The end plate 22 of the moving scroll member 20 has a thrust surface 21 that contacts and slides relative to the thrust plate 80, and the thrust plate 80 also has a thrust surface 81 that is used to contact and support the thrust surface 21 of the moving scroll member 20. As the drive shaft 50 rotates, relative movement and contact stress will occur between the thrust surface 21 of the moving scroll member 20 and the thrust surface 81 of the thrust plate 80. Therefore, sufficient lubrication is required between these two thrust surfaces to reduce the friction force therebetween and prevent the two from jamming or excessive wear.

[0031] The following will refer to Figure 1 and Figure 2 to describe the lubrication process between the thrust surface 21 of the moving scroll member 20 and the thrust surface 81 of the thrust plate 80. In the example of the scroll compressor shown in Figure 1 , lubricant is stored at the bottom of the housing 12. The end of the concentric hole 54 is immersed in the lubricant at the bottom of the housing 12 or otherwise supplied with lubricant. In one example, a lubricant supply device, such as an oil pump or an oil fork, can be provided in or near the concentric hole 54. During the operation of the compressor, one end of the concentric hole 54 is supplied with lubricant by the lubricant supply device, and the lubricant entering the concentric hole 54 is pumped or thrown into the eccentric hole 56 by the centrifugal force during the rotation of the drive shaft 50 and flows upward along the eccentric hole 56 until it reaches the end face of the eccentric crank pin 52. The lubricant discharged from the end face of the eccentric crank pin 52 enters the space 90 between the bearing sleeve 70 and the thrust plate 80 along the gaps between the eccentric crank pin 52 and the bushing 58 and between the bushing 58 and the hub 26 and accumulates in the space 90. A counterweight 60 is fixedly provided at one end of the drive shaft 50 and is located between the thrust plate 80 and the bearing sleeve 70, that is, in the space 90. As the drive shaft 50 rotates, the counterweight 60 fixedly provided at one end of the drive shaft also rotates. As shown by the arrow in Figure 2 , a part of the lubricant accumulated in the space 90 is agitated by the counterweight 60 and moves upward along the outside of the hub 26 to reach the annular groove 23 on the lower side of the moving scroll end plate 22 of the moving scroll member 20, and spreads over the thrust surface between the thrust surface 21 of the moving scroll member 20 and the thrust surface 81 of the thrust plate 80 as the moving scroll member 20 makes translational rotation. Optionally, no counterweight 60 needs to be provided in the scroll compressor, and a part of the lubricant accumulated in the space 90 is agitated by the hub 26 and moves upward to reach the annular groove 23 on the lower side of the moving scroll end plate 22 of the moving scroll member 20, and then lubricates the thrust surfaces between the moving scroll member 20 and the thrust plate 80.

[0032] The following will refer to Figures 3A - 3D the structure of the orbiting scroll member 20 according to the first embodiment of the present invention in detail. The orbiting scroll member 20 includes an orbiting scroll end plate 22, a hub portion 26 formed on one side of the orbiting scroll end plate 22, and a spiral blade 24 formed on the other side of the orbiting scroll end plate 22. A thrust surface 21 that contacts a thrust plate (not shown) and slides relative to the thrust plate is formed on the surface of the orbiting scroll end plate 22 on the side of the hub portion 26. An annular groove 23 is formed radially inward adjacent to the thrust surface 21. As Figure 3C shown, the cross-sectional shape of the annular groove 23 is U-shaped. Alternatively, as Figure 3D shown, the cross-sectional shape of the annular groove 23 is V-shaped. Alternatively, the cross-sectional shape of the annular groove 23 can be any shape that facilitates storing lubricant and guiding lubricant.

[0033] Figure 4 is a relationship view of the mutual movement of the thrust plate and the orbiting scroll member according to the first embodiment of the present invention. In Figure 4 , it is assumed that the inner diameter of the thrust surface 81 of the thrust plate 80 is R b (FIGS. 5A and 5B respectively show the inner diameter R of the thrust surface 81 of the thrust plate 80 with and without a rounded corner at the radially inner side b ), it is assumed that the radius of gyration of the orbiting scroll member 20 rotating translationally relative to the thrust plate 80 (or a stationary scroll member, not shown) is R or (see Figure 4 the circle formed by the dashed line in a ), and it is assumed that the outer diameter of the annular groove 23 is R a . Then when R b < R or , the annular groove 23 cannot contact the thrust surface 81 of the thrust plate 80 due to its too small outer diameter, making it difficult to bring the lubricant in the annular groove 23 to the thrust surface 81 of the thrust plate 80. Additionally, when R a > R b + R or , the annular groove 23 contacts the entire edge of the outer diameter of the annular groove 23 with the thrust surface 81 of the thrust plate 80 during the translational rotation of the orbiting scroll member 20 relative to the thrust plate 80, resulting in damage to the thrust surface 81 of the thrust plate 80 by defects such as burrs on the edge of the annular groove 23 under the action of the contact stress between the orbiting scroll member 20 and the thrust plate 80. Therefore, in order to balance the supply of lubricant from the annular groove 23 to the thrust surface 81 of the thrust plate 80 and reduce the damage to the thrust surface 81 of the thrust plate 80 by defects such as burrs on the edge of the annular groove 23, the outer diameter of the annular groove 23 is R a can be designed such that the above parameters satisfy the formula: R b-R or <R a <R b +R or In this case, the annular groove 23 partially extends into the thrust surface 81 of the thrust plate 80 in areas where contact stress between the orbiting scroll 20 and the thrust plate 80 is low or absent, allowing lubricant in the annular groove 23 to be carried to the thrust surface 81 of the thrust plate 80 as the orbiting scroll 20 translates. Specifically, the translational rotation of the orbiting scroll 20 generates contact stress between the orbiting scroll 20 and the thrust plate 80. This contact stress distribution has the following characteristics: contact stress between the thrust plate 80 and the orbiting scroll 20 is minimal or absent in the areas of the thrust plate 80 closest to the hub and furthest from the hub 62. Contact stress between the thrust plate 80 and the orbiting scroll 20 is maximum in areas perpendicular to the line connecting the areas of the thrust plate 80 closest to the hub and furthest from the hub 62, and gradually decreases along the circumferential direction toward the areas closest to the hub 62 and furthest from the hub 62. Therefore, because the annular groove 23 is concentrically disposed with the hub 62, in the area of the thrust plate 80 closest to the hub 62 (i.e., the area where the contact stress between the thrust plate 80 and the orbiting scroll 20 is minimal or absent), the annular groove 23 partially extends into the thrust surface 81 of the thrust plate 80, thereby carrying lubricant in the annular groove 23 to the thrust surface 81 of the thrust plate 80. Furthermore, because the contact stress between the thrust plate 80 and the orbiting scroll 20 is minimal or absent in this area, damage to the thrust surface 81 of the thrust plate 80 by the portion of the edge of the annular groove 23 that enters the thrust plate 80 is reduced. The remaining portion of the edge of the annular groove 23 does not contact the thrust surface 81 of the thrust plate 80 and, therefore, does not damage the thrust surface 81 of the thrust plate 80.

[0034] In R b -R or <R a <R b +R or Within the parameter range, the outer diameter R of the annular groove 23 a The smaller the R is, the less the portion of the annular groove 23 extends into the thrust plate 80, the less lubricant is taken out of the annular groove 23, and the less damage is caused to the thrust surface 81 of the thrust plate 80; and a The larger the annular groove 23 is, the more the portion of the annular groove 23 extends into the thrust plate 80, the more lubricant is carried out of the annular groove 23, and the greater the damage to the thrust surface 81 of the thrust plate 80. Therefore, the oil supply condition can be determined according to the operating environment of the compressor, and the inner diameter of the annular groove 23 can be set accordingly.

[0035] In an example Ra Satisfies the formula: R a = R b - 0.5R or . Under this parameter condition, an optimal balance can be achieved between the supply of lubricant from the annular groove 23 to the thrust surface 81 of the thrust plate 80 and the reduction of damage to the thrust surface 81 of the thrust plate 80 caused by defects such as burrs on the edge of the annular groove 23. This is particularly applicable to variable-frequency compressors or compressors with non-constant operating conditions.

[0036] Figure 7 Shows a first comparative example with respect to an embodiment of the present invention. Figure 7 The first comparative example shown discloses a moving scroll member 20' for a scroll compressor. The moving scroll member 20' includes a moving scroll end plate 22', a spiral blade 24' extending on one side of the end plate 22', and a hub portion 26' extending on the other side of the end plate 22'. The end plate 22' is supported by a thrust plate (not shown). As the moving scroll member 20' makes a translational rotation, relative motion and contact stress will occur between the moving scroll member 20' and the thrust plate, thereby causing a certain amount of wear between the moving scroll member 20' and the thrust plate. To solve the wear problem, an oil inlet hole 27', a transverse hole 28', an oil outlet hole 29' are provided on the moving scroll end plate 22', and an annular oil groove 23' is provided on the thrust surface 21' of the moving scroll member 20'. When the compressor operates, the lubricant enters through the oil inlet hole 27', flows along the transverse hole 28', and then flows from the oil outlet hole 29' into the annular oil groove 23'. Finally, as the moving scroll member 20' moves relative to the thrust plate, the lubricant enters between the moving scroll member 20' and the thrust plate from the annular oil groove 23' to reduce the wear between the moving scroll member 20' and the thrust plate.

[0037] In the first comparative example, since the annular oil groove is provided at the middle position of the thrust surface 21' of the moving scroll member 20', defects such as burrs on the two edges of the annular oil groove 23' will damage the thrust surface of the thrust plate when the moving scroll member 20 and the thrust surface move relative to each other. In addition, the oil supply path in this oil circuit layout is relatively long, resulting in a small oil supply volume, and the thrust surface cannot be fully lubricated, resulting in serious wear.

[0038] Figure 8 Shows a second comparative example that is an improvement based on the first comparative example. In the second comparative example, compared with the first comparative example, a second oil supply channel identical to the first comparative example is symmetrically added to supply double the amount of lubricant into the annular oil groove 23'. Although the second comparative example increases the oil supply volume of the lubricant compared with the first comparative example, the second comparative example still has the defect that defects such as burrs on the edge of the annular oil groove 23' are likely to damage the thrust surface of the thrust plate.

[0039] AndFigure 7 , Figure 8 Compared with the comparative example shown in Figure 8 , in the scroll compressor according to the first embodiment of the present invention, an annular groove 23 is provided radially inside the thrust surface 21 of the orbiting scroll member 20 (i.e., in the region where the contact stress with the thrust surface 81 of the thrust plate 80 is small or there is no contact stress), so as to effectively reduce the damage to the thrust surface 81 of the thrust plate 80 caused by defects such as burrs on the edge of the annular groove 23.

[0040] Next, reference will be made to Figure 6A and Figure 6B to describe in detail the structure of the orbiting scroll member 20 according to the second embodiment of the present invention. The orbiting scroll member 20 includes an orbiting scroll end plate 22, a hub portion 26 formed on one side of the orbiting scroll end plate 22, and a spiral blade 24 formed on the other side of the orbiting scroll end plate 22. A thrust surface 21 that contacts and slides relative to a thrust plate (not shown) is formed on the surface of the hub portion 26 of the orbiting scroll end plate 22. An annular groove 23 is formed radially inside the vicinity of the thrust surface 21. The annular groove 23 is two concentrically arranged annular grooves, and a plurality of radial channels 25 for fluidly connecting the two annular grooves 23 are provided at intervals in the circumferential direction on the annular groove 23. The radial channels 25 extend in the radially inward direction to the junction of the hub portion 26 and the thrust surface 21 of the orbiting scroll member 20, so as to facilitate guiding the lubricant conveyed outside the hub portion 26 into the annular groove 23 and further guiding it onto the thrust surface 21 of the orbiting scroll member 20. Optionally, the radial channels 25 can be one or more, and the radial channels 25 can be arranged at equal intervals or unequal intervals in the circumferential direction of the annular groove 23. Optionally, the annular groove 23 can be three or more. In the case where there are multiple annular grooves 23, the outer diameter of the annular groove 23 is the outer diameter of the outermost annular groove. Optionally, the multiple annular grooves 23 are arranged at equal intervals in the radial direction.

[0041] Although various embodiments of the present invention have been described in detail herein, it should be understood that the present invention is not limited to the specific embodiments described and shown here, and other variations and modifications can be implemented by those skilled in the art without departing from the essence and scope of the present invention. All such variations and modifications fall within the scope of the present invention. Moreover, all the components described herein can be replaced by other technically equivalent components.

Claims

1. A scroll compressor comprising: A movable scroll component (20), wherein the movable scroll component (20) has an end plate (22); as well as a thrust plate (80), the thrust plate (80) being configured to axially support the movable scroll component (20), The end plate (22) has a first thrust surface (21) that contacts the thrust plate (80) and slides relative to the thrust plate (80), and the thrust plate (80) has a second thrust surface (81) for contacting and supporting the first thrust surface (21). It is characterized in that an annular groove (23) is formed on the radial inner side adjacent to the first thrust surface (21), and the outer diameter R of the annular groove (23) is a Satisfy the following parameter relationship: R b -R or <R a <R b +R or , where R b is the inner diameter of the second thrust surface (81) of the thrust plate (80), R or It is the radius of gyration of the movable scroll component (20) in translational rotation relative to the thrust plate (80).

2. The scroll compressor according to claim 1, wherein: The outer diameter R of the annular groove (23) a Satisfy the following parameter relationship: R a =R b -0.5R or .

3. The scroll compressor according to claim 1 or 2, characterized in that: The cross-sectional shape of the annular groove (23) is V-shaped or U-shaped.

4. The scroll compressor according to claim 1 or 2, characterized in that: The annular groove (23) is a plurality of concentrically arranged annular grooves (23).

5. The scroll compressor according to claim 4, wherein: The plurality of annular grooves (23) are arranged at equal intervals in the radial direction.

6. The scroll compressor according to claim 4, characterized in that A plurality of radial channels (25) are arranged in the plurality of annular grooves (23) at intervals along the circumferential direction, so as to enable the plurality of annular grooves (23) to communicate with each other through fluid.

7. The scroll compressor according to claim 6, characterized in that The plurality of radial channels (25) are arranged at equal intervals along the circumferential direction.

8. The scroll compressor according to claim 6 or 7, characterized in that: A hub portion (26) is provided radially inside the first thrust surface (21) of the movable scroll component (20), and a plurality of radial channels (25) extend radially inward to a junction between the hub portion (26) and the first thrust surface (21).

9. The scroll compressor according to claim 1, wherein: The invention also includes a bearing sleeve (70) for supporting the thrust plate (80), wherein the thrust plate (80) is fixed to the bearing sleeve (70) or formed as an integral piece with the bearing sleeve (70).

10. The scroll compressor according to claim 1, wherein The thrust plate (80) has a rounded corner at a radially inner side adjacent to the second thrust surface (81).

Images