CN212155162U

CN212155162U - Scroll compressor having a plurality of scroll members

Info

Publication number: CN212155162U
Application number: CN202020598750.4U
Authority: CN
Inventors: 徐榜; 张跃
Original assignee: Emerson Climate Technologies Suzhou Co Ltd
Current assignee: Gulun Environmental Technology Suzhou Co ltd
Priority date: 2020-04-20
Filing date: 2020-04-20
Publication date: 2020-12-15
Anticipated expiration: 2030-04-20

Abstract

The utility model discloses a scroll compressor, include: an orbiting scroll member (20), the orbiting scroll member (20) having an end plate (22); and a thrust plate (80), the thrust plate (80) being configured for axial support of the orbiting scroll member (20), wherein the end plate (22) has a first thrust surface (21) contacting the thrust plate (80) and sliding relative to the thrust plate (80), the thrust plate (80) has a second thrust surface (81) for contacting and supporting the first thrust surface (21), an annular groove (23) is formed adjacent to a radially inner side of the first thrust surface (21), and the annular groove (23) is formed adjacent to a radially inner side of the first thrust surface (21)(23) Outer diameter R of_aThe following parameter relationships are satisfied: r_b‑R_or<R_a<R_b+R_orWherein R is_bIs the inner diameter, R, of the thrust plate (80)_orThe radius of gyration is the translational rotation of the orbiting scroll member (20) relative to the thrust plate (80). The scroll compressor can reduce damage to the thrust surface of the thrust plate.

Description

Scroll compressor having a plurality of scroll members

Technical Field

The utility model relates to a scroll compressor that is used for scroll compressor's thrust plate and includes this thrust plate.

Background

In a scroll compressor, compression of a fluid is achieved by relative movement between orbiting and non-orbiting scroll members. To provide axial support to the orbiting scroll member, a thrust plate is provided on the end plate side of the orbiting scroll member. The thrust plate is fixed to the scroll compressor housing. When the scroll compressor is operating, the orbiting scroll member moves relative to the thrust plate. Sufficient lubrication is required between the contact surfaces (thrust surfaces) of the end plate and the thrust plate of the orbiting scroll member to reduce friction and wear therebetween. At present, most of lubricating structures adopted between end plates of movable scroll parts and thrust surfaces of thrust plates have the defects of complex structure, insufficient lubrication or serious abrasion of the thrust surfaces.

Accordingly, there is a need in the art for an oil circuit arrangement or design for a scroll compressor that provides more efficient oil supply without damaging the thrust surfaces.

SUMMERY OF THE UTILITY MODEL

One or more embodiments of the present invention provide a scroll compressor capable of more efficiently supplying a lubricant to a thrust surface without damaging the thrust surface.

One or more embodiments of the present invention provide a scroll compressor, including: an orbiting scroll member having an end plate; and a thrust plate configured to axially support the orbiting scroll member, wherein the end plate has a first thrust surface contacting and sliding with respect to the thrust plate, the thrust plate has a second thrust surface contacting and supporting the first thrust surface, an annular groove is formed at a radially inner side adjacent to the first thrust surface, and an outer diameter R of the annular groove_aThe following parameter relationships are satisfied: r_b-R_or<R_a<R_b+R_orWherein R is_bIs the inner diameter, R, of the second thrust surface of the thrust plate_orThe radius of gyration is the translational rotation of the movable vortex component relative to the thrust plate. The parameter setting can be realized as follows: in areas of lesser or no contact stress between the orbiting scroll member and the thrust plate, the annular groove is in contact with the radially inner side of the thrust surface of the thrust plate so that lubricant in the annular groove is carried onto the thrust surface of the thrust plate as the orbiting scroll member translates. In addition, because the annular oil groove is in a lower stress area, the damage of the defects of the edge of the annular groove, such as burrs and the like, to the thrust surface of the thrust plate can be reduced.

Further, the outer diameter R of the annular groove_aThe following parameter relationships are satisfied: r_a＝R_b-0.5R_or. Under this parameter condition, an optimum balance of supply of the lubricant from the annular groove to the thrust surface of the thrust plate and reduction of damage to the thrust surface of the thrust plate by defects of the edge of the annular groove such as burrs and the like can be achieved.

Further, the cross-sectional shape of the annular groove is V-shaped or U-shaped.

Further, the annular groove is a plurality of annular grooves which are concentrically arranged.

Further, a plurality of radial passages that fluidly communicate the plurality of annular grooves are provided at intervals in a circumferential direction on the annular grooves. The radial passages facilitate the flow of lubricant in the plurality of annular grooves and further direct lubricant onto the thrust surfaces of the orbiting scroll member.

Further, the plurality of radial passages are arranged at equal intervals in the circumferential direction.

Further, the plurality of annular grooves are provided at equal intervals in the radial direction.

Further, a hub is disposed radially inward of the first thrust surface of the orbiting scroll member, and a plurality of radial passages extend radially inward to an interface of the hub and the first thrust surface to facilitate channeling lubricant delivered along an outside of the hub into the annular groove.

Further, a bearing sleeve for supporting the thrust plate is included, the thrust plate being fixed to or formed as one piece with the bearing sleeve.

Further, the thrust plate has a radius at a radially inner side adjacent the second thrust surface.

Drawings

The features and advantages of one or more embodiments of the present invention will become more readily understood from the following description with reference to the accompanying drawings, in which:

FIG. 1 is a cross-sectional view of a scroll compressor according to a first embodiment of the present invention;

FIG. 2 is an enlarged view of the vicinity of the orbiting scroll member of the scroll compressor according to the first embodiment of the present invention;

FIG. 3A is a perspective view and FIG. 3B is a cross-sectional view of an orbiting scroll member according to a first embodiment of the present invention; FIG. 3C is an enlarged sectional view of the annular recessed portion of FIG. 3B; fig. 3D is an enlarged sectional view of a modification of the annular groove in fig. 3B.

Fig. 4 is a view of the relationship of the mutual movement of the thrust plate and the orbiting scroll member according to the first embodiment of the present invention.

FIG. 5A is a perspective view of one example of a thrust plate; fig. 5B is a perspective view of another example of a thrust plate.

FIG. 6A is a perspective view and FIG. 6B is a cross-sectional view of an orbiting scroll member in accordance with a second embodiment of the present invention;

FIG. 7 is a cross-sectional view of a scroll compressor according to a first embodiment of the present invention;

fig. 8 is an enlarged view of the vicinity of the orbiting scroll part of the scroll compressor according to the first embodiment of the present invention.

Detailed Description

The following description of the various embodiments of the present invention is merely exemplary in nature and is in no way intended to limit the invention, its application, or uses. The same reference numerals are used to designate the same components in the respective drawings, and thus the configurations of the same components will not be described repeatedly.

The basic configuration and operation principle of a scroll compressor according to a first embodiment of the present invention will now be described with reference to fig. 1. The scroll compressor 10 includes a generally cylindrical housing 12. An intake joint (not shown) is provided on the housing 12 for sucking a low-pressure gaseous refrigerant. An end cover 14 is fixedly connected to one end of the housing 12, and a bottom cover is fixedly connected to the other end. The end cap 14 is fitted with a discharge fitting for discharging compressed refrigerant. A partition 16 extending transversely with respect to the shell 12 is also provided between the shell 12 and the end cover 14, thereby dividing the interior space of the compressor into a high pressure side and a low pressure side. The space between the end cap 14 and the diaphragm 16 constitutes a high pressure side space, and the space between the diaphragm 16, the casing 12 and the bottom cap constitutes a low pressure side space.

The housing 12 accommodates therein an orbiting scroll member 20 and a non-orbiting scroll member 30 as compression mechanisms, and a motor 40 and a drive shaft 50 as drive mechanisms. The compression mechanism may be driven by a drive mechanism and supported by a bearing housing 70. The bearing sleeve 70 may be secured to the housing 12 at any desired manner, such as riveting at a plurality of points.

The orbiting scroll member 20 includes an orbiting scroll end plate 22 having a spiral vane 24 provided on one surface of the orbiting scroll end plate 22 and a cylindrical hub 26 provided on the other surface thereof. Non-orbiting scroll member 30 includes a non-orbiting scroll end plate 32 and a spiral vane 34. The spiral blades 24 of the orbiting scroll member 20 and the spiral blades 34 of the non-orbiting scroll member 30 are engaged and form fluid pockets therebetween, which are gradually reduced in volume from the outside toward the central body, when the orbiting scroll member 20 and the non-orbiting scroll member 30 are relatively moved, thereby compressing refrigerant in the fluid pockets.

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 driving shaft 50 is provided with an eccentric crank pin 52 and a weight 60. The balance weight 60 is fixedly provided on the drive shaft 50, and thus can be rotated integrally with the drive shaft 50 when the drive shaft 50 rotates. The upper portion of the drive shaft 50 is rotatably supported by bearings in the bearing housing 70. The counterweight 60 is located in the bearing housing 70.

One end of the drive shaft 50 has an eccentric crank pin 52. Eccentric crank pin 52 of drive shaft 50 is inserted into hub 26 of orbiting scroll member 20 via bushing 58 to rotatably drive orbiting scroll member 20. As the orbiting scroll member 20 moves relative to the non-orbiting scroll member 30, the fluid pockets between the orbiting scroll member 20 and the non-orbiting scroll member 30 move from a radially outer position to a central position of the orbiting scroll member 20 and the non-orbiting scroll member 30 and are compressed. The compressed fluid is discharged through an exhaust port 36 provided in the center of the non-orbiting scroll end plate 32 of the non-orbiting scroll member 30. The other end of the drive shaft 50 may include a concentric bore 54. The concentric bore 54 opens to the eccentric crank pin 52 via the eccentric bore 56 to supply lubricant in the compressor bottom sump to the movable components of the compressor for lubrication.

Thrust plate 80 is disposed between orbiting scroll member 20 and bearing housing 70, and thrust plate 80 may be fixed to bearing housing 70 or formed as a unitary piece with bearing housing 70. Thrust plate 80 serves to axially support orbiting scroll member 20. End plate 22 of orbiting scroll member 20 has a thrust surface 21 in contact with thrust plate 80 and sliding relative to thrust plate 80, thrust plate 80 also having a thrust surface 81, thrust surface 81 for contacting and supporting thrust surface 21 of orbiting scroll member 20. As drive shaft 50 rotates, relative movement and contact stresses may develop between thrust surface 21 of orbiting scroll member 20 and thrust surface 81 of thrust plate 80. Sufficient lubrication is required between the two thrust surfaces to reduce the friction therebetween to prevent seizure or excessive wear of the two.

The lubrication process between thrust surface 21 of orbiting scroll member 20 and thrust surface 81 of thrust plate 80 will be described with reference to fig. 1 and 2. In the example of the scroll compressor shown in FIG. 1, lubricant is stored in the bottom of the shell 12. The ends of the concentric bores 54 are immersed in lubricant in the bottom of the housing 12 or otherwise supplied with lubricant. In one example, a lubricant supply, such as an oil pump or oil fork, may be provided in or near the concentric bore 54. During operation of the compressor, one end of the concentric bore 54 is supplied with lubricant by the lubricant supply, and lubricant entering the concentric bore 54 is pumped or thrown into the eccentric bore 56 by centrifugal force during rotation of the drive shaft 50 and flows up the eccentric bore 56 to 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 gap between the eccentric crank pin 52 and the bush 58 and the gap between the bush 58 and the hub 26 and collects in the space 90. The weight 60 is fixedly disposed at one end of the drive shaft 50 and is located between the thrust plate 80 and the bearing housing 70, i.e., in the space 90. As the driving shaft 50 rotates, the weight 60 fixedly provided at one end of the driving shaft also rotates. As indicated by the arrows in fig. 2, a portion of the lubricant collected in space 90 is agitated by counterweight 60 and moves up the outside of hub 26 into annular recess 23 on the underside of orbiting scroll end plate 22 of orbiting scroll member 20 and spreads between thrust surface 21 of orbiting scroll member 20 and thrust surface 81 of thrust plate 80 as orbiting scroll member 20 rotates in translation. Alternatively, without the provision of counterweight 60 in the scroll compressor, a portion of the lubricant collected in space 90 is agitated by hub 26 and moves upwardly into annular recess 23 on the underside of orbiting scroll end plate 22 of orbiting scroll member 20, thereby lubricating the thrust surface between orbiting scroll member 20 and thrust plate 80.

The structure of the orbiting scroll part 20 according to the first embodiment of the present invention will be described in detail with reference to fig. 3A to 3D. The orbiting scroll part 20 includes an orbiting scroll end plate 22, a hub 26 formed at one side of the orbiting scroll end plate 22, and a spiral vane 24 formed at 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 on the boss 26 side of orbiting scroll end plate 22. An annular groove 23 is formed adjacent the radially inner side of the thrust surface 21. As shown in fig. 3C, the sectional shape of the annular groove 23 is U-shaped. Alternatively, as shown in fig. 3D, the sectional shape of the annular groove 23 is V-shaped. Alternatively, the cross-sectional shape of the annular groove 23 may be any shape that facilitates storing and guiding lubricant.

Fig. 4 is a view of the relationship of the mutual movement of the thrust plate and the orbiting scroll member according to the first embodiment of the present invention. In the context of figure 4 of the drawings,suppose the thrust surface 81 of the thrust plate 80 has an inner diameter R_b(FIGS. 5A, 5B show the inner diameter R of the thrust surface 81 of the thrust plate 80 with and without rounding at the radially inner side, respectively_b) Given a radius of gyration, R, of orbiting scroll member 20 for translational rotation relative to thrust plate 80 (or non-orbiting scroll member, not shown)_or(see the circle formed by the dotted line in FIG. 4), assuming that the outer diameter of the annular groove 23 is R_a. When R is_a<R_b-R_orAt this time, the annular groove 23 cannot come into contact with the thrust surface 81 of the thrust plate 80 because its outer diameter is too small, so that it is difficult to bring the lubricant in the annular groove 23 onto the thrust surface 81 of the thrust plate 80. In addition, when R is_a>R_b+R_orAt this time, because of the excessive outer diameter of annular groove 23, the entire edge at which the outer diameter of annular groove 23 is located is in contact with thrust surface 81 of thrust plate 80 during translational rotation of orbiting scroll member 20 relative to thrust plate 80, resulting in defects such as burrs or the like at the edge of annular groove 23 tending to damage thrust surface 81 of thrust plate 80 under the effect of contact stress between orbiting scroll member 20 and thrust plate 80. Therefore, in order to balance the supply of the lubricant from the annular groove 23 to the thrust surface 81 of the thrust plate 80 and the reduction of the damage of the edge of the annular groove 23 such as the burr or the like to the thrust surface 81 of the thrust plate 80, the outer diameter of the annular groove 23 is R_aIt may be designed such that the above parameters satisfy the formula: r_b-R_or<R_a<R_b+R_or. In this case, it is possible to realize: in areas of lesser or no contact stress between orbiting scroll member 20 and thrust plate 80, annular groove 23 extends partially into thrust surface 81 of thrust plate 80 such that lubricant in annular groove 23 is carried to thrust surface 81 of thrust plate 80 as orbiting scroll member 20 translates. Specifically, due to the translational rotation of orbiting scroll member 2O, contact stress may be generated between orbiting scroll member 20 and thrust plate 80. The distribution of the contact stress has the following characteristics: in the region of thrust plate 80 closest to and farthest from hub 62, there is minimal or no contact stress between thrust plate 80 and orbiting scroll member 20, and in the region of thrust plate 80 closest to hub 62In the region where the line between the region closest to hub 62 is perpendicular, the contact stress between thrust plate 80 and orbiting scroll member 20 is greatest and gradually decreases in the circumferential direction toward the region closest to hub 62 and the region farthest from hub 62. Thus, because annular groove 23 is disposed concentrically with hub 62, in the region of thrust plate 80 closest to hub 62 (i.e., the region where there is minimal or no contact stress between thrust plate 80 and orbiting scroll member 20), annular groove 23 extends partially into thrust surface 81 of thrust plate 80, carrying lubricant in annular groove 23 to thrust surface 81 of thrust plate 80. And since there is minimal or no contact stress between thrust plate 80 and orbiting scroll member 20 in this region, damage to thrust surface 81 of thrust plate 80 by the portion of the edge of annular groove 23 entering thrust plate 80 may be reduced. And the other part of the edge of the annular groove 23 does not contact the thrust surface 81 of the thrust plate 80, so that the thrust surface 81 of the thrust plate 80 is not damaged.

At R_b-R_or<R_a<R_b+R_orWithin the range of the parameters of (1), the outer diameter R of the annular groove 23_aThe smaller the portion of the annular groove 23 that extends into the thrust plate 80, the less lubricant is carried out of the annular groove 23 and less damage is done to the thrust surface 81 of the thrust plate 80; and R is_aThe larger the portion of the annular groove 23 that 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, it is possible to determine the oil supply condition according to the compressor operation environment, thereby setting the inner diameter size of the annular groove 23 according to the oil supply condition.

In one example R_aSatisfies the formula: r_a＝R_b-0.5R_or. Under this parameter condition, an optimum balance of supply of the lubricant from the annular groove 23 to the thrust surface 81 of the thrust plate 80 and reduction of damage to the thrust surface 81 of the thrust plate 80 by defects of the edge of the annular groove 23 such as burrs and the like can be achieved. This applies in particular to variable-frequency compressors or compressors whose operating conditions are not constant.

Fig. 7 shows a first comparative example with respect to an embodiment of the present invention. A first comparative example shown in fig. 7 discloses an orbiting scroll member 20 ' for a scroll compressor, the orbiting scroll member 20 ' including an orbiting scroll end plate 22 ', a spiral vane 24 ' extending on one side of the end plate 22 ', and a hub 26 ' extending on the other side of the end plate 22 '. The end plate 22' is supported by a thrust plate (not shown). As orbiting scroll member 20 ' translates, relative movement and contact stresses between orbiting scroll member 20 ' and the thrust plate occur, thereby causing some wear between orbiting scroll member 20 ' and the thrust plate. To solve the wear problem, an oil inlet hole 27 ', a cross hole 28 ', an oil outlet hole 29 ' are provided on the orbiting scroll end plate 22 ', and an annular oil groove 23 ' is provided on the thrust surface 21 ' of the orbiting scroll part 20 '. When the compressor is operated, the lubricant enters from the oil inlet hole 27 'and flows along the cross hole 28' and then flows from the oil outlet hole 29 'into the annular oil groove 23'. Eventually, as orbiting scroll member 20 'moves relative to the thrust plate, lubricant enters between orbiting scroll member 20' and the thrust plate from annular oil groove 23 'to reduce wear between orbiting scroll member 20' and the thrust plate.

In the first comparative example, since the annular oil groove is provided at the intermediate position of the thrust surface 21 ' of the orbiting scroll member 20 ', defects such as burrs or the like at both edges of the annular oil groove 23 ' may damage the thrust surface of the thrust plate when the orbiting scroll member 20 and the thrust surface move relatively. In addition, the oil way is arranged on a longer oil supply road, so that the oil supply amount is small, the thrust surface cannot be sufficiently lubricated, and the abrasion is serious.

Fig. 8 shows a second comparative example which is improved on the basis of the first comparative example. In the second comparative example, compared to the first comparative example, one oil supply passage identical to that of the first comparative example is symmetrically added to supply double the lubricant into the annular oil groove 23'. Although the second comparative example improves the amount of lubricant supplied as compared with the first comparative example, the second comparative example still has a defect in which the edge of the annular oil groove 23' such as a burr or the like easily damages the thrust surface of the thrust plate.

In the scroll compressor according to the first embodiment of the present invention, as compared with the comparative example shown in fig. 7 and 8, the annular groove 23 is provided at the radially inner side adjacent to the thrust surface 21 of the orbiting scroll member 20 (i.e., the region where the contact stress with the thrust surface 81 of the thrust plate 80 is small or no), so that damage to the thrust surface 81 of the thrust plate 80 due to defects of the edge of the annular groove 23 such as burrs or the like can be effectively reduced.

The structure of the orbiting scroll part 20 according to the second embodiment of the present invention will be described in detail with reference to fig. 6A and 6B. The orbiting scroll part 20 includes an orbiting scroll end plate 22, a hub 26 formed at one side of the orbiting scroll end plate 22, and a spiral vane 24 formed at 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 on the boss 26 side of orbiting scroll end plate 22. An annular groove 23 is formed adjacent the radially inner side of the thrust surface 21. The annular groove 23 is two annular grooves arranged concentrically, and a plurality of radial passages 25 that fluidly communicate the two annular grooves 23 are provided at intervals in the circumferential direction on the annular groove 23. The radial passages 25 extend in a radially inward direction to the intersection of the hub 26 of the orbiting scroll member 20 and the thrust surface 21 to facilitate channeling lubricant carried along the outside of the hub 26 into the annular groove 23 and further onto the thrust surface 21 of the orbiting scroll member 20. Alternatively, the radial passages 25 may be one or more, and the radial passages 25 may be arranged at equal intervals or at unequal intervals in the circumferential direction of the annular groove 23. Alternatively, the annular grooves 23 may be three or more. In the case where the annular groove 23 is plural, the outer diameter of the annular groove 23 is the outer diameter of the outermost annular groove. Alternatively, the plurality of annular grooves 23 are provided at equal intervals in the radial direction.

Although various embodiments of the present invention have been described in detail herein, it is to be understood that the invention is not limited to the precise embodiments described and illustrated herein, and that other modifications and variations may be effected by one skilled in the art without departing from the spirit and scope of the invention. All such variations and modifications are intended to fall within the scope of the present invention. Moreover, all the components described herein may be replaced by other technically equivalent components.

Claims

1. A scroll compressor, comprising:

an orbiting scroll member having an end plate; and

a thrust plate configured for axial support of the orbiting scroll member,

wherein the end plate has a first thrust surface in contact with and sliding relative to the thrust plate, the thrust plate has a second thrust surface for contacting and supporting the first thrust surface,

characterised in that an annular groove is formed adjacent the radially inner side of the first thrust surface, the annular groove having an outer diameter R_aThe following parameter relationships are satisfied: r_b-R_or<R_a<R_b+R_orWherein R is_bIs the inner diameter, R, of the second thrust surface of the thrust plate_orThe radius of gyration is the translational rotation of the movable vortex component relative to the thrust plate.

2. The scroll compressor of claim 1, wherein an outer diameter R of the annular groove_aThe following parameter relationships are satisfied: r_a＝R_b-0.5R_or。

3. The scroll compressor of claim 1 or 2, wherein the annular groove is V-shaped or U-shaped in cross-section.

4. The scroll compressor of claim 1 or 2, wherein the annular groove is a plurality of annular grooves arranged concentrically.

5. The scroll compressor of claim 4, wherein the plurality of annular grooves are equally spaced radially.

6. The scroll compressor of claim 4, wherein a plurality of radial passages fluidly communicating the plurality of annular grooves are provided at intervals in a circumferential direction in the plurality of annular grooves.

7. The scroll compressor of claim 6, wherein a plurality of the radial passages are equally spaced in a circumferential direction.

8. The scroll compressor of claim 6 or 7, wherein a hub is disposed radially inward of the first thrust surface of the orbiting scroll member, and the plurality of radial passages extend in a radially inward direction to an intersection of the hub and the first thrust surface.

9. The scroll compressor of claim 1, further comprising a bearing housing for supporting the thrust plate, the thrust plate being fixed to or formed as one piece with the bearing housing.

10. The scroll compressor of claim 1, wherein the thrust plate has a rounded corner at a radially inner side adjacent the second thrust surface.