WO2021013103A1

WO2021013103A1 - Balance block for scroll compressor and scroll compressor

Info

Publication number: WO2021013103A1
Application number: PCT/CN2020/102820
Authority: WO
Inventors: 邹宏伟; 刘轩; 严宏
Original assignee: 艾默生环境优化技术(苏州)有限公司
Priority date: 2019-07-19
Filing date: 2020-07-17
Publication date: 2021-01-28

Abstract

A balance block (150, 250, 350, 450, 550) for a scroll compressor (100). The scroll compressor (100) comprises a movable scroll component (1) having a movable scroll end plate, a main bearing seat (8) having a thrust plate (4), and a driving shaft (3) for driving the movable scroll component (1), wherein the thrust plate (4) is provided with a thrust surface (41) which is used for supporting and is in contact with an end plate of the movable scroll plate (11); at least one part of the balance block (150, 250, 350, 450, 550) is provided in a concave cavity between the movable scroll component (1) and the main bearing seat (8); the balance block (150, 250, 350, 450, 550) can rotate along with the rotation of the driving shaft (3); the balance block (150, 250, 350, 450, 550) comprises an upper surface facing the movable scroll end plate (11), wherein a guide surface structure (170, 270, 370, 470, 570) is provided on the upper surface, and the guide surface structure (170, 270, 370, 470, 570) is provided with a guide surface (171, 271, 371, 471, 571) for guiding a lubricant in the concave cavity to move towards the thrust surface (41) in a rotating process of the balance block (150, 250, 350, 450, 550). Further provided is the scroll compressor (100) comprising the balance block (150, 250, 350, 450, 550). The balance block structure can effectively improve the lubrication situation of the thrust surface, and can greatly reduce the abrasion risk of the thrust surface.

Description

Balance weight for scroll compressor and scroll compressor

This application claims the priority of the following Chinese patent applications: the application number submitted to the Chinese Patent Office on July 19, 2019 is 201910656199.6, and the invention is named "balance weight and scroll compressor for scroll compressors" in China Patent application; a Chinese patent application filed with the Chinese Patent Office on July 19, 2019, with the application number 201921148485.3 and the invention titled "balance weight and scroll compressor for scroll compressors". The entire contents of these patent applications are incorporated into this application by reference.

Technical field

The present disclosure relates to the field of compressors, and more specifically, to a balance weight for scroll compressors.

Background technique

This section provides background information related to the present disclosure, which does not necessarily constitute prior art.

A scroll compressor usually includes a compression mechanism composed of a fixed scroll component and a movable scroll component. The movable scroll component is supported by the main bearing seat/thrust plate to provide axial restraint, and is driven by the eccentric component to perform translational rotation relative to the fixed scroll component. Since the movable scroll component moves relative to the thrust plate, it is necessary to provide sufficient lubrication to the thrust surface between the thrust plate and the movable scroll component. In addition, during the operation of the scroll compressor, the centrifugal force or torque generated by the rotation of the eccentric component may cause the compressor to vibrate. Usually, balance weights are provided on the rotating parts, such as the upper end of the drive shaft, to provide reverse centrifugal force or centrifugal torque to balance the unbalance generated by the eccentric part.

In existing scroll compressors, taking a vertical scroll compressor as an example, lubricant is stored at the bottom of the compressor housing. Part of the lubricant flows through the lubricant channel inside the drive shaft, the eccentric hole on the end face of the eccentric crank pin, the gap between the orbiting scroll hub and the eccentric crank pin under the action of centrifugal force or the oil pump, and then flows to the recess of the main bearing seat. The lubricating oil collected in the recess and on the balance weight splashes to the lower surface of the orbiting scroll end plate due to the high-speed rotation of the balance weight, and spreads over the main bearing housing and the orbiting scroll component along with the translational rotation of the orbiting scroll component Between the thrust surface. Therefore, the upper surface of the balance weight, the lower surface of the movable scroll end plate, the outer surface of the movable scroll hub, and the inner surface of the main bearing seat/thrust plate collectively surround an area for lubricant splash.

Due to the large space in this area, the amount of lubricant that can splash into the thrust surface for effective lubrication is often unstable, especially when the compressor rotates at a low speed, the rotation speed of the balance weight is low, which cannot provide sufficient splash power for the lubricant , Resulting in insufficient lubrication of the thrust surface between the movable scroll component and the main bearing seat, and the thrust surface is seriously worn.

Therefore, there is a need to provide an improved scroll compressor, which can increase the amount of lubricant entering the thrust surface between the movable scroll component and the thrust plate without affecting the existing structure of the compressor, and ensure that the compressor is Under all working conditions, sufficient lubrication of the thrust surface can be realized, and the wear probability of the thrust surface can be reduced.

Summary of the invention

The general summary of the present disclosure is provided in this section, rather than a comprehensive disclosure of the full scope of the present disclosure or all the features of the present disclosure.

The purpose of the present disclosure is to provide a counterweight that facilitates the entry of lubricant into the thrust surface and a scroll compressor equipped with the counterweight.

According to an aspect of the present disclosure, there is provided a balance weight for a scroll compressor, wherein the scroll compressor includes a movable scroll member having a movable scroll end plate, a main bearing seat with a thrust plate, and The drive shaft of the movable scroll component is driven, the thrust plate has a thrust surface for supporting and contacting the end plate of the movable scroll, and at least a part of the balance weight is provided in the recess between the movable scroll component and the main bearing housing. In the cavity, the balance weight can rotate with the rotation of the drive shaft. The balance weight includes an upper surface facing the end plate of the movable scroll, wherein a guide surface structure is provided on the upper surface, and the guide surface structure has a rotating process in the balance weight The guide surface for the lubricant in the middle guide cavity to move toward the thrust surface.

Optionally, the guide surface structure is a slope member protruding with respect to the upper surface of the balance weight.

Optionally, the ramp member is integrally or separately provided at the upper surface of the balance weight.

Optionally, the balance weight includes a mounting portion and a weight portion, the weight portion extends beyond the mounting portion in the axial direction, and the guide surface structure is a protrusion extending substantially radially inward from the weight portion.

Optionally, the balance weight is provided with a groove recessed from the upper surface, the guide surface structure is defined by the groove, the groove has a bottom surface, and at least a part of the bottom surface of the bottom surface extends from the bottom of the groove to the surface of the balance weight , Thereby forming a guide surface, that is, the guide surface is the bottom surface of the groove extending from the bottom of the groove to the upper surface of the balance weight.

Optionally, the groove depth of the groove gradually decreases, and the bottom surface gradually extends from the bottom of the groove to the upper surface of the balance weight, that is, the bottom surface gradually rises to extend to the upper surface of the balance weight, and the entire bottom surface forms a guide surface .

Optionally, at the end where the guide surface of the groove meets the upper surface, the width of the groove gradually decreases.

Optionally, the balance weight is further provided with a drainage groove with a concave upper surface. The drainage groove is used to introduce the lubricant into the groove. The groove depth of the drainage groove is smaller than the groove at the end of the groove where the drainage groove communicates with the groove. deep.

Optionally, the first included angle formed between the guide surface and the upper surface of the balance weight is less than or equal to 90°.

Optionally, the guiding surface is a flat surface, a circular arc surface, a parabolic surface, or a spherical surface.

Optionally, the second included angle formed between the guide surface and the radial direction of the balance weight is greater than or equal to 0°.

According to another aspect of the present disclosure, there is also provided a scroll compressor, wherein the scroll compressor includes the balance weight as described above.

Optionally, the guide surface structure is arranged in an area surrounded by the upper surface of the balance weight, the outer surface of the hub of the movable scroll component, the lower surface of the movable scroll end plate, and the inner surface of the thrust plate.

Optionally, the scroll compressor further includes an unloading bushing, and the balance weight is installed on the drive shaft, or the balance weight is installed on the unloading bushing or is integrated with the unloading bushing.

In general, the guide surface structure provided on the balance weight according to the present disclosure helps the lubricant in the cavity formed between the main bearing seat and the movable scroll end plate to be thrown or splashed toward the movable scroll component, so that more The lubricant enters the thrust surface between the movable scroll component and the main bearing seat or thrust plate, which can provide sufficient lubrication on the thrust surface under various working conditions, greatly reducing the wear probability of the thrust surface .

Description of the drawings

The aforementioned and additional features and characteristics of the present disclosure will become clearer from the following detailed description with reference to the accompanying drawings, which are merely examples and are not necessarily drawn to scale. In the drawings, the same reference signs are used to indicate the same parts. In the drawings:

Figure 1 shows a partial longitudinal sectional view of a conventional turbo compressor;

Figure 2 shows a top view of the turbo compressor in Figure 1;

Figure 3 shows a perspective view of a balance weight in a conventional turbo compressor;

4 shows a partial longitudinal sectional view of the turbo compressor according to the first embodiment of the present disclosure;

Fig. 5a shows a perspective view of a balance weight in a turbo compressor according to the first embodiment of the present disclosure, wherein the balance weight includes a flat slope guide surface structure;

Figure 5b shows a perspective view of the balance weight in Figure 5a when the guide surface structure is not installed;

6a, 6b, 6c, 6d, 7 and 8 respectively show perspective views of modified examples of the balance weight in the turbo compressor according to the first embodiment of the present disclosure;

9a and 9b show a side view of a balance weight in a turbo compressor according to the first embodiment of the present disclosure, wherein the guide surface structure of the balance weight has different heights;

Fig. 10a shows a perspective view of a counterweight in a turbo compressor according to a second embodiment of the present disclosure, wherein the counterweight includes a curved guide surface structure;

Fig. 10b shows a schematic diagram with different curved surfaces of the guide surface structure of the counterweight in the turbo compressor according to the second embodiment of the present disclosure;

Fig. 11 shows a perspective view of a balance weight in a turbo compressor according to a third embodiment of the present disclosure, wherein the balance weight includes a spherical slope guide surface structure;

12 shows a perspective view of a balance weight in a turbo compressor according to a fourth embodiment of the present disclosure, wherein the balance weight includes a groove-type guide surface structure;

FIG. 13 shows a perspective view of a modified example of the balance weight in the turbo compressor according to the fourth embodiment of the present disclosure.

Detailed ways

The preferred embodiments of the present disclosure will now be described in detail with reference to FIGS. 1 to 13. The following description is merely exemplary in nature and is not intended to limit the present disclosure and its applications or uses. In each view, the corresponding components or parts use the same reference signs.

Figures 1 and 2 show a partial structure of a conventional turbo compressor. Here, a scroll compressor is taken as an example for description, but it should be understood that the present disclosure is not limited to scroll compressors. As shown in Figures 1 and 2, the conventional turbo compressor 10 includes a compression mechanism composed of a fixed scroll member 2 and a movable scroll member 1, a drive shaft 3 for driving the compression mechanism, and a motor (not shown in the figure). Out) etc. The orbiting scroll component 1 includes an end plate 11, a hub 12 formed on one side of the end plate 11, and a spiral blade 13 formed on the other side of the end plate 11. One side of the movable scroll member 1 is supported by the thrust plate 4 of the upper part of the main bearing housing 8 so that a thrust surface 41 is formed between the end plate 11 and the thrust plate 4. It should be noted that the thrust plate 4 can be mounted on the main bearing housing 8 or can be integrated with the main bearing housing 8. One end of the drive shaft 3 is supported by a main bearing provided in the main bearing housing 8. An eccentric crank pin 31 is provided at one end of the drive shaft 3, and an unloading bush 14 is provided between the eccentric crank pin 31 and the hub 12 of the movable scroll component 1. The drive shaft 3 is driven by the motor, and the movable scroll component 1 will rotate in translation relative to the fixed scroll component 2 (that is, the central axis of the movable scroll component 1 rotates around the central axis of the fixed scroll component 2, but the movable scroll The rotating member 1 itself does not rotate around its own central axis) to achieve fluid compression.

During the operation of the scroll compressor 10, the centrifugal force or the centrifugal torque generated by the rotation of the eccentric component may cause the vibration of the compressor. Generally, a balance weight is provided on the rotating part to provide reverse centrifugal force or centrifugal torque to balance the unbalance produced by the eccentric part. The shape and structure of the balance weight can be changed according to specific application requirements. FIG. 3 shows a perspective view of the balance weight in FIG. 1 and FIG. 2. The balance weight 5 includes a substantially circular arc-shaped weight portion 51 and a substantially annular mounting portion 52 for mounting the balance weight 5 to the drive shaft 3. The weight portion 51 extends beyond the mounting portion 52 in the axial direction. . The balance weight 5 is arranged in the cavity between the main bearing housing 8 and the movable scroll component 1. As shown in FIG. 1, the balance weight 5 is mounted on the drive shaft 3, but those skilled in the art will know that the balance weight 5 can also be mounted on the unloading bush 14 or be integrated with the unloading bush 14. In this article, there is a certain gap between the upper surface of the balance weight 5 and the end plate 11 of the movable scroll component 1, and the portion of the upper surface of the balance weight 5 directly facing the end plate 11 of the movable scroll component 1 is defined as the balance There is no obstruction between the top surface of the block 5 and the top surface of the balance weight 5 and the lower surface of the end plate 11.

The lubrication process of the thrust surface 41 will be described below with reference to FIG. 1. In the example of the vertical scroll compressor shown in FIG. 1, lubricant is stored at the bottom of the compressor housing. Correspondingly, a channel extending substantially along its axial direction is formed in the drive shaft 3, that is, a central hole (not shown in the figure) formed at the lower end of the drive shaft 3 and a channel extending upward from the central hole to the end face of the eccentric crank pin 31 Eccentric hole 32. The end of the center hole is immersed in the lubricant at the bottom of the compressor housing or is otherwise supplied with lubricant. During the operation of the compressor, one end of the center hole is supplied with lubricant by the lubricant supply device. The lubricant that enters the center hole is pumped or thrown into the eccentric hole 32 by the centrifugal force during the rotation of the drive shaft 3 And it flows upward along the eccentric hole 32 until it reaches the end surface of the eccentric crank pin 31. The lubricant discharged from the end surface of the eccentric crank pin 31 flows downward along the gap between the unloading bush 14 and the eccentric crank pin 31 and the gap between the unloading bush 14 and the hub 12 to reach the recess of the main bearing housing. Part of the lubricant collected in the recess and on the balance weight flows through the main bearing housing 8 and flows downward, and part of the lubricant is thrown out and splashed as the balance weight 5 rotates. Since there is a gap between the top surface of the balance weight 5 and the end plate 11 of the movable scroll component 1, and there is a gap between the hub 12 and the main bearing housing 8 or the thrust plate 4, the upper surface of the balance weight 5 especially refers to the balance The top surface of the block 5, the outer surface of the hub 12, the lower surface of the end plate 11 and the inner surface of the main bearing housing 8 or the thrust plate 4 collectively surround the area 6. In this area 6, the lubricant is thrown upwards to the lower surface of the end plate 11 of the movable scroll member 1 and spreads between the movable scroll member 1 and the thrust plate 4 along with the translational rotation of the movable scroll member 1. The thrust surface 41 is thereby lubricated.

Since the area 6 is relatively large, the amount of oil that can pass through the area 6 into the thrust surface 41 for effective lubrication is extremely unstable. Especially when the compressor is running at a low speed, the rotation speed of the balance weight 5 is reduced, so that the power of the lubricant throwing and splashing is reduced, and a sufficient amount of lubricant reaching the thrust surface 41 cannot be provided.

This paper proposes a structure for improving the splashing of lubricant in the area 6, as shown in FIGS. 4 to 5b according to the balance weight 150 according to the first embodiment of the present disclosure and the scroll equipped with the balance weight 150 Compressor 100.

In the first embodiment of the present disclosure, the balance weight 150 has the same main structure as the existing balance weight 5, that is, it includes a substantially circular arc-shaped weight portion 151 and a substantially annular mounting portion 152. It extends beyond the mounting portion 152 in the axial direction, thereby forming a recess on the mounting portion 152 relative to the weight portion 151. At the recess, a part of the upper surface of the balance weight 150 constitutes a top surface directly facing the end plate 11 of the movable scroll member 1 without being blocked. On the basis of ensuring the unbalanced amount of the balance weight 150, the top surface of the balance weight 150 is also provided with a flat slope member 170 for guiding the lubricant to be thrown upward or splash. As shown in FIG. 5a and FIG. 5b, the planar slope member 170 is configured to include a base and a protrusion with a triangular cross-section provided on the base. The protrusion has a guide surface 171 for guiding the lubricant to fling or splash upward. Mounting holes are also provided on the base, and the flat slope member 170 can be mounted on the top surface of the balance weight 150 by screws or bolts. The flat slope member 170 may also be welded or riveted to the balance weight 150. Specifically, the planar ramp member 170 is arranged along the substantially radial direction of the mounting portion 152, that is, the intersection of the guide surface 171 on the protrusion of the planar ramp member 170 and the upper surface of the mounting portion 152 is along the substantially radial direction of the mounting portion 152. The direction extends such that the guide surface 171 thereof faces the lubricant converging in the recess of the balance weight 150.

FIG. 4 shows a partial structure of the scroll compressor 100 equipped with the balance weight 150 as described above. Similar to the existing scroll compressor 10, the scroll compressor 100 also includes a fixed scroll component 120, a movable scroll component 110, a drive shaft 130, a main bearing seat 180, a thrust plate 140 and a counterweight 150. The connection structure and working principle of the components of the scroll compressor 100 are similar to those of the existing scroll compressor 10, and will not be repeated here. When the balance weight 150 is fixed on the drive shaft 130, the flat slope member 170 provided on the balance weight 150 is formed on the upper surface of the balance weight 150, especially the top surface, the outer surface of the hub 120, the lower surface of the end plate 110 and The main bearing seat 180 or the inner side surface of the thrust plate 140 is in an area 160 that is jointly surrounded. The lubricant collected in the recess of the balance weight 150 is thrown out as the balance weight 150 rotates, and moves upward by means of the guide surface 171 of the planar ramp member 170, thereby making it easier for the lubricant to splash to the end of the movable scroll component 110 Plate and enter the thrust surface 141. Compared with the "open" area 6 in the existing scroll compressor 10 without any structure that assists the upward movement of the lubricant, the provision of the flat slope member 170 in the area 160 can increase the boost for the upward movement of the lubricant, so that More lubricant enters the thrust surface.

In addition, since the flat slope member according to the first embodiment of the present disclosure can be fixed on the balance weight by screws or bolts, the installation operation is simple and can be directly applied to mass production balance weights, which is convenient for production and assembly. The balance weight with a flat slope member is suitable for a variety of compressors and is an effective universal measure to reduce the wear of the thrust surface in the compressor.

Although the first embodiment shown in FIGS. 4 to 5b includes the flat slope member 170 having a convex block with a triangular cross section, the flat slope member may actually be configured as a convex block having various shapes. In addition, the flat slope member can not only be installed on the balance weight in a separate manner, but also can be integrally formed on the balance weight.

FIG. 6a shows an example in which a flat slope member 170 having a convex block with a rectangular cross section is installed on the balance weight 150 in a split manner. As shown in FIG. 6a, the guide surface 171 of the convex block of the planar slope member 170 is perpendicular to the upper surface of the mounting portion 151 of the balance weight 150, so that the lubricant in the concave portion of the balance weight 150 moves upward to the convex by means of the guide surface 171 On the top surface of the block, since the gap between the top surface of the protrusion and the end plate of the movable scroll component 110 is small, the lubricant can be more easily thrown out to the end plate of the movable scroll component 110; or the balance block 150 When being thrown out, the lubricant in the concave portion hits the guide surface 171 of the protrusion, so as to more easily splash to the end plate of the movable scroll component 110.

6b to 6d respectively show an example in which a flat slope member 270 having a convex block with a trapezoidal, wedge-shaped, or rectangular cross-section is integrally formed on the balance weight 250. In an example in which the flat slope member and the balance weight are integrally formed, the flat slope member 270 omits the base and is directly formed as a bump. Wherein, the planar slope member 270 in FIG. 6b has a top surface and a guide surface 271, and the acute angle between the guide surface 271 and the upper surface of the mounting portion of the balance weight 250 is the first included angle α; the planar slope member in FIG. 6c 270 has a top surface and a segmented guide surface 271. The segmented guide surface 271 is composed of an inclined portion having a first included angle α and a vertical portion perpendicular to the upper surface of the mounting portion of the balance weight 250; Figure 6d The flat slope member 270 in the middle is similar to FIG. 6a, except that it is integrally formed on the balance weight 250. The flat slope member 270 has a guide surface 271 perpendicular to the upper surface of the mounting portion of the balance weight 250, that is, the first clamp The angle α is 90°. Those skilled in the art will understand that the first included angle α between the guide surface of the flat slope member and the upper surface of the installation portion of the smooth block can be appropriately selected within the range of 90° or less as required.

In the above example, since the flat slope member is formed as a part of the balance weight, the BOM structure is simplified, and the additional processing and installation time when producing the balance weight is reduced.

Although in the first embodiment shown in FIGS. 4 to 5b, the planar ramp member 170 is arranged along the substantially radial direction of the mounting portion 152, the planar ramp member may actually be aligned with the radial direction of the mounting portion 152. The direction of the angle is arranged.

As shown in FIG. 7, the plane slope member 270 has a top surface and a guide surface 271, and an acute angle formed between the line of intersection between the guide surface 271 and the upper surface of the mounting portion of the balance weight 250 and the radial direction of the mounting portion Is the second angle β. Since the lubricant in the recess of the counterweight 250 is subjected to centrifugal force as the counterweight 250 rotates, the trajectory of the lubricant in the recess can be a curve that gradually moves away from the center of the installation part of the counterweight 250, and the flat slope member runs along with the installation part. The arrangement in which the radial direction of 152 forms a certain included angle, that is, the intersection line of the guide surface 271 of the planar ramp member and the upper surface of the mounting portion of the balance weight 250 forms a second included angle β with the radial direction of the mounting portion 152, Make the line of intersection between the guide surface 271 and the upper surface of the mounting portion of the balance weight 250 intersect or even be perpendicular to the trajectory of the lubricant in the recess as much as possible, thereby making more lubricant more fully rely on the flat slope The member 270 moves upward. Those skilled in the art will understand that the second included angle β between the intersection of the guide surface 271 of the planar ramp member and the upper surface of the mounting portion of the balance weight 250 and the radial direction of the mounting portion 152 may be greater than Appropriate selection is made within the range equal to 0°.

The dimensions of the plane slope member will be further explained below. In this article, the size of the projection of the plane ramp member 170 or the plane ramp member 270 in the circumferential direction of the mounting portion of the balance weight is defined as the length of the plane ramp member, and the size along the radial direction of the mounting portion of the balance weight The size is defined as the width of the flat slope member, and its dimension in the direction perpendicular to the upper surface of the mounting part of the balance weight is positioned to the height of the flat slope member. Figures 8 to 9b show examples of flat ramp members with different widths and heights.

Although in the first embodiment shown in FIGS. 4 to 5b, the width of the planar ramp member 170 is smaller than the radial width of the mounting portion 151 of the balance weight 150, those skilled in the art will understand that the planar ramp member 170 The width can also be equal to the radial width of the mounting portion 151 of the balance weight 150, or even greater than the radial width of the mounting portion 151 of the balance weight 150 without affecting the assembly of the balance weight 150 and the drive shaft 130, as shown in Figure 8. Shown. Those skilled in the art will also understand that the height of the planar ramp member 270 may not exceed the top surface of the counterweight portion of the balance weight 250 as shown in FIG. 9a, that is, the planar ramp member 270 is completely accommodated in the recess of the balance weight 250 Inside, it can also exceed the top surface of the counterweight portion of the balance weight 250 as shown in Figure 9b, that is, the flat slope member 270 extends beyond the recess of the balance weight 250 and extends upward in the area 160, as long as it does not interfere with other components. can. In addition, although not particularly shown in the figure, the length of the flat slope member 170 can also be selected within an appropriate range as required, as long as it does not interfere with other components.

Fig. 10a shows a balance weight 350 according to the second embodiment of the present disclosure. The main structure and working principle of the balance weight 350 and the compressor equipped with the balance weight 350 are the same as those of the first embodiment of the present disclosure, and will not be repeated here.

As shown in FIG. 10a, the balance weight 350 has a substantially circular arc-shaped counterweight portion 351 and a substantially annular mounting portion 352. The weight portion 351 extends beyond the mounting portion 352 in the axial direction, so that a concave portion relative to the weight portion 351 is formed on the mounting portion 352. At the recess, a part of the upper surface of the balance weight 350 constitutes a top surface that directly faces the end plate of the movable scroll without being blocked. A curved slope member 370 is integrally formed at the top surface of the balance weight 350. The curved slope member 370 has a guide surface 371 extending from the upper surface of the mounting part 352 to the weight part 351. As shown in FIG. 10b, the guiding surface 371 may be configured as a concave or convex paraboloid, arc surface, or the like. The guide surface 371 of the curved slope member is more conducive to the upward movement of the lubricant, so that more lubricant enters the thrust surface.

Those skilled in the art will understand that the curved slope member 370 having a curved surface (guide surface) 371 according to the second embodiment of the present disclosure is different from the one having flat surfaces (guide surface) 171, 271 according to the first embodiment of the present disclosure. Similar to the

flat slope members

170 and 270, the curved slope member 370 may not only be integrally formed on the balance weight, but also be installed on the balance weight in a separate manner. In addition, the curved slope member 370 can also have various shapes (only the plane is replaced by a curved surface), size, and different first and second included angles such as the

flat slope members

170 and 270, which will not be repeated here. .

FIG. 11 shows a balance weight 450 according to the third embodiment of the present disclosure. The main structure and working principle of the balance weight 450 and the compressor equipped with the balance weight 450 are the same as those of the first embodiment of the present disclosure, and will not be repeated here.

As shown in FIG. 11, the balance weight 450 has a substantially circular arc-shaped counterweight portion 451 and a substantially annular mounting portion 452. The weight portion 451 extends beyond the mounting portion 452 in the axial direction, so that a concave portion relative to the weight portion 451 is formed on the mounting portion 452. At the recess, a part of the upper surface of the balance weight 450 constitutes a top surface directly facing the end plate of the movable scroll without being blocked. A portion of the weight portion 451 protrudes inward along the upper surface of the mounting portion 452 substantially in the radial direction or at a certain angle to the radial direction to form a bump, and a spherical guide surface is processed on the bump 471, thereby forming a spherical slope member 470. In this way, the method of forming the spherical slope member 470 is simpler, and the production process is more time- and cost-effective.

Those skilled in the art will understand that the spherical slope member 470 having a spherical surface (guide surface) 471 according to the third embodiment of the present disclosure is different from the curved surface slope member having a curved surface (guide surface) 371 according to the second embodiment of the present disclosure. The member 370 is similar to the

planar ramp members

170, 270 having planes (guide surfaces) 171, 271 according to the first embodiment of the present disclosure. The spherical ramp member 470 may not only be integrally formed on the balance weight, but also be divided The way is installed on the balance weight. In addition, the spherical slope member 370 may also include various shapes such as the planar slope members 170 and 270 (only the flat surface is replaced by a spherical surface), size, and different first included angle α and second included angle β, which will not be repeated here. . In addition, the method of forming the spherical slope member 470 according to the third embodiment of the present disclosure may also be used for the formation of the

flat slope members

170 and 270 and the curved slope member 370.

In order to guide the lubricant in the concave portion of the balance weight to be thrown and splashed toward the movable scroll component, in addition to forming a slope member protrudingly on the upper surface of the mounting portion of the balance weight, it may also be formed on the upper surface of the mounting portion of the balance weight Form grooves.

FIG. 12 shows a balance weight 550 according to the fourth embodiment of the present disclosure. The main structure and working principle of the balance weight 450 and the compressor equipped with the balance weight 550 are the same as the first embodiment of the present disclosure, and will not be repeated here.

As shown in FIG. 12, the balance weight 550 has a substantially circular arc-shaped weight portion 551 and a substantially annular mounting portion 552. The weight portion 551 extends beyond the mounting portion 552 in the axial direction, so that a concave portion relative to the weight portion 551 is formed on the mounting portion 552. At the recess, a part of the upper surface of the balance weight 550 constitutes a top surface directly facing the end plate of the movable scroll component without being blocked. A groove 570 is provided on the upper surface (at the top surface) of the mounting portion 552, and the groove 570 extends substantially along the circumferential direction of the mounting portion 552, and may also extend in a direction at a certain angle to the circumferential direction of the mounting portion 552. The groove 570 has a bottom surface. The bottom surface consists of a first portion 572 that is substantially parallel to the upper surface of the mounting portion 552 and extends from the bottom of the groove 570 (the lowest part of the groove 570 in FIG. 12, that is, the flat portion 572). The second part 571 of the upper surface of the mounting part 552 is composed, and the second part 571 is formed as a guide surface. When the compressor installed with the balance weight 550 is running, more lubricant is collected in the groove 570 and moves upward along the guide surface of the groove 570 to be thrown out to the end plate of the movable scroll, thereby resisting the thrust The surface is lubricated.

FIG. 13 shows an example of further optimization of the groove 570 of the balance weight 550 in FIG. 12. As shown in FIG. 13, the groove 570 may be formed in a form in which the groove depth gradually becomes shallower from one end to the other end thereof, that is, the bottom surface of the groove 570 starts from the bottom of the groove 570 (the groove 570 in FIG. The lowest part of the groove 570 gradually rises to extend to the upper surface of the mounting part 552, so that the guide surface is formed by the entire bottom surface of the groove 570. Preferably, at the end of the groove 570 where the groove depth is relatively shallow, that is, at the end where the guide surface of the groove 570 meets the upper surface of the mounting portion, the radial width of the groove 570 is gradually reduced, thereby enabling During the rotation of the counterweight, the speed of the lubricant in the groove 570 is further increased, which is more helpful for the lubrication to be thrown out or splashed to the end plate of the movable scroll. Preferably, a drainage groove 573 communicating with the groove 570 is further provided at the deeper end of the groove 570. The drainage groove 573 guides more lubricant into the groove 570 so that more lubricant can be thrown out or splashed to the orbiting scroll end plate by virtue of the guiding surface of the groove 570. Preferably, the groove depth of the drainage groove 573 is smaller than the groove depth of the groove 570 at the end where the drainage groove 573 communicates with the groove 570. Preferably, the radial width of the drainage groove 573 is greater than the radial width of the groove 570, thereby As a result, more lubricating oil is collected into the groove 570 via the drainage groove 573, and is guided to the thrust surface via the guide surface of the groove 570.

Those skilled in the art will understand that the guiding surface of the groove 570 may also be configured as a flat surface, a circular arc surface, a parabolic surface, or a spherical surface as described in the first to third embodiments. In addition, similarly, the acute angle between the guide surface of the groove 570 and the upper surface of the mounting portion 552 is the first included angle α, and the first included angle α is less than or equal to 90°. Since the groove 570 can be arranged along a direction at a certain angle to the circumferential direction of the mounting portion 552, the acute angle between the groove 570 and the radial direction of the mounting portion 552 is the second included angle β, and the second included angle β is greater than or equal to 0°.

The following Table 1 lists the pump oil test results of the compressors according to the first and fourth embodiments of the present disclosure and existing compressors. The compressor is a scroll compressor model ZW520HSP, wherein, in the compressor in the first embodiment, the first angle α between the guide surface of the ramp member of the balance weight and the upper surface of the installation portion of the balance weight Is 30°, and the second included angle β between the intersection of the guide surface of the ramp member and the upper surface of the mounting portion of the balance weight and the radial direction of the mounting portion is 90°.

Table 1

It can be seen from Table 1 that setting a guide surface structure on the balance weight to guide the throwing and splashing of lubricant can effectively improve the lubrication condition of the thrust surface, regardless of whether the guide surface structure is a slope member or a groove. Especially when the guide surface structure is configured as a ramp member, the amount of lubricant that can enter the thrust surface is greatly increased, which greatly reduces the risk of wear on the thrust surface.

The balance weight for the scroll compressor and the scroll compressor according to the preferred embodiment of the present disclosure are described above in conjunction with the specific embodiments. It can be understood that the above description is only exemplary rather than restrictive, and those skilled in the art can conceive of various variations and modifications with reference to the above description without departing from the scope of the present disclosure. These variations and modifications are also included in the protection scope of the present disclosure.

Claims

A balance weight (150, 250, 350, 450, 550) for a scroll compressor (100). The scroll compressor (100) includes a movable scroll component with a movable scroll end plate, The main bearing seat of the thrust plate and the drive shaft that drives the movable scroll member, the thrust plate has a thrust surface for supporting and contacting the end plate of the movable scroll, and the balance weight At least a part is provided in a cavity between the movable scroll component and the main bearing housing, the balance weight can rotate with the rotation of the drive shaft, and the balance weight includes The upper surface of the end plate,

It is characterized in that a guide surface structure (170, 270, 370, 470, 570) is provided on the upper surface, and the guide surface structure has the function of guiding the lubrication in the cavity during the rotation of the balance weight. The guide surface (171, 271, 371, 471, 571) of the agent moving toward the thrust surface.
The balance weight (150, 250, 350, 450, 550) according to claim 1, wherein the guide surface structure is a slope member (170, 270, 370, 470) protruding with respect to the upper surface.
The balance weight (150, 250, 350, 450, 550) according to claim 2, wherein the slope member is integrally or separately provided at the upper surface.
The balance weight (150, 250, 350, 450, 550) according to claim 1, wherein the balance weight includes a mounting portion (152, 252, 352, 452, 552) and a weight portion (151, 251, 351, 451, 551), the weight portion extends beyond the mounting portion in the axial direction, and the guide surface structure is a protrusion extending radially inward from the weight portion.
The balance weight (150, 250, 350, 450, 550) according to claim 1, wherein the balance weight is provided with a groove (570) recessed from the upper surface, and the guide surface structure is formed by The groove (570) defines that the guide surface is a bottom surface of the groove extending from the bottom of the groove to the upper surface.
The balance weight (150, 250, 350, 450, 550) according to claim 5, wherein the groove depth of the groove gradually decreases, and the bottom surface gradually extends from the bottom of the groove to the Upper surface.
The balance weight (150, 250, 350, 450, 550) according to claim 5, wherein, at the end where the guide surface of the groove (570) meets the upper surface, the The width of the groove gradually decreases.
The balance weight (150, 250, 350, 450, 550) according to claim 5, wherein the balance weight is further provided with a drainage groove (573) with a concave upper surface, the drainage groove (573) Used to introduce lubricant into the groove (570), the groove depth of the drainage groove (573) is smaller than that of the groove (571), and the drainage groove (573) is in communication with the groove (571) The depth of the groove at the end.
The balance weight (150, 250, 350, 450, 550) according to any one of claims 1-8, wherein the first included angle formed between the guide surface and the upper surface is less than or equal to 90 °.
The balance weight (150, 250, 350, 450, 550) according to any one of claims 1-8, wherein the guiding surface is a flat surface, a circular arc surface, a parabolic surface or a spherical surface.
The balance weight (150, 250, 350, 450, 550) according to any one of claims 1-8, wherein the second included angle formed between the guide surface and the radial direction of the balance weight Greater than or equal to 0°.
A scroll compressor (100), characterized in that, the scroll compressor further comprises the balance weight according to any one of claims 1-11.
The scroll compressor (100) according to claim 12, wherein the guide surface structure is provided on the upper surface of the balance weight, the outer surface of the hub of the movable scroll component, and the movable scroll end The lower surface of the plate and the inner side surface of the thrust plate jointly surround the area.
The scroll compressor (100) according to claim 12, the scroll compressor further comprising an unloading bushing, the balance weight is installed on the drive shaft, or the balance weight is installed on the unloading liner It is sleeved on or formed integrally with the unloading bushing.