WO2020083312A1

WO2020083312A1 - Counterweight, counterweight assembly and scroll compressor

Info

Publication number: WO2020083312A1
Application number: PCT/CN2019/112759
Authority: WO
Inventors: 沙海天; 纪高锋; 朱伟
Original assignee: 艾默生环境优化技术(苏州)有限公司
Priority date: 2018-10-23
Filing date: 2019-10-23
Publication date: 2020-04-30

Abstract

A counterweight assembly for a scroll compressor and the scroll compressor (10). The counterweight assembly comprises a bushing (200) and counterweights (100, 400) mounted on the bushing. A driving shaft (30) of the scroll compressor (10) drives a moving scroll (160) of the scroll compressor (10) by means of the bushing (200). The counterweights (100, 400) comprise counterweight portions (300, 500), and the counterweight portions (300, 500) comprise front end portions (310, 510) and tail end portions (320, 520) relative to the rotation direction of the counterweight assembly. The counterweight portions (300, 500) are configured so that the radial distances from outer peripheral edges of the counterweight portions (300, 500) to the center of the counterweight assembly are variable from the front end portions (310, 510) to the tail end portions (320, 520). The present structure may flexibly change the shape of the counterweight and the location of the center of mass so as to reduce gas power consumption and improve oil circulation.

Description

Counterweight, counterweight assembly and scroll compressor

This application requires the priority of the Chinese patent application submitted to the State Intellectual Property Office of China on October 23, 2018, with the application number 201821719127.9 and the name "weight assembly and scroll compressor for scroll compressors", and This application requires the priority of the Chinese patent application submitted to the State Intellectual Property Office of China on October 23, 2018 with the application number 201821719563.6 and the name "counterweight, counterweight assembly and scroll compressor", the entire content of which is cited Incorporated in this application.

Technical field

The present disclosure relates to a counterweight, a counterweight assembly including the counterweight, and a scroll compressor including the counterweight assembly.

Background technique

The content of this section only provides background information related to the present disclosure, which may not constitute prior art.

In rotating machinery (e.g. compressors, especially scroll compressors) that include moving parts (e.g. compression mechanisms, motors, rotating shafts, etc.), the movement of the moving parts (e.g. rotation) will increase during mechanical operation due to unbalance Large vibration, noise, etc. In some cases, the unbalanced movement of the moving part is caused by an unbalanced center of mass due to machining errors of the moving part itself and / or components mounted thereon. In other cases, the unbalanced movement of the moving parts is caused by the eccentric structure specifically provided in the moving parts themselves and / or the components mounted thereon to achieve special functions (for example, in scroll compressors, An eccentric pin is provided at the drive shaft to use the principle of eccentricity to make the movable scroll perform circumferential translation with respect to the fixed scroll).

In response to such motion imbalance, a counterweight capable of providing reverse centrifugal force is usually provided on the moving part to balance the generated motion imbalance to reduce vibration and noise.

However, the design of prior art counterweights has poor adaptability to rotating members of different construction types (especially for special counterweights such as counterweights mounted to bushings). Therefore, there is a need for the flexible design of the counterweight itself in order to achieve flexible adjustment of the weight of the counterweight and the center of mass of the counterweight and thus the flexible adjustment of the centrifugal force of the counterweight. In addition, if the counterweight has insufficient strength due to its shape or the like, the counterweight in high-speed movement will easily break (eg, fatigue fracture). In addition, the counterweight of the prior art has limitations on the application of materials, inconvenient processing and high cost.

In addition, the counterweight moves with the movement of the moving parts. In applications such as high-speed rotation of moving parts, gas flow in the environment where the counterweight is located, and / or liquid flow (such as oil flow) in the environment where the counterweight is located, the presence of the counterweight can cause the motion resistance of the moving part The increase results in an increase in system power consumption. In addition, if the counterweight has insufficient strength due to its shape or the like, the counterweight in high-speed movement will easily break (eg, fatigue fracture).

In the counterweight for compressors disclosed in the prior art (WO2017199435A1), the radius, center position and height of the respective arc outer peripheral surfaces of the various parts of the counterweight are designed to increase the height of the corresponding counterweight part for adjustment The height of the center of mass of the counterweight, thereby reducing the bending torque of the counterweight. However, the counterweight performs an eccentric rotary motion around the center of rotation. In particular, there is radial flexibility compensation in the case where an unloading bush is used, so that the motion performed is not a rotational movement about the counterweight and the center of rotation of the bush. Since the prior art restricts the outer peripheral surface of the counterweight to a circular arc surface of equal radius, the motion trajectory of the circular arc is a non-circular trajectory with respect to the center of rotation, so a large gas power consumption is generated. Moreover, in the prior art, the weight portion is limited to a circular arc surface, so that the weight design is single and the function is single. In addition, this prior art lacks the design to promote oil circulation.

Summary of the invention

In a general aspect, an object of one or more embodiments of the present disclosure is to provide a counterweight with adjustable adaptability, sufficient strength, and / or ease of processing to overcome or alleviate at least one of the above-mentioned deficiencies .

In order to achieve the above object, according to an aspect of the present disclosure, there is provided a counterweight for a scroll compressor, the counterweight includes an installation portion and an eccentric weighting portion, the installation portion includes a main body portion and from the main body The eccentric weighted portion is fixedly fitted to the weighted portion.

Preferably, the body portion has a complete or partial ring shape, and the weight portion extends axially relative to the body portion, or radially extends relative to the body portion, or relative to the body The portion extends axially and radially.

Preferably, the body portion has a completely circular ring shape, and the weight portion is a substantially arc-shaped weight portion extending axially and radially from a portion of the circumferential periphery of the body portion.

Preferably, the eccentric weighted portion includes an axial weighted portion and / or a radial weighted portion, the axial weighted portion is axially fixedly fitted to the weighted portion, and the radial weighted portion is radially fixedly fitted To the weight section.

Preferably, the eccentric weighting part is a part made of a first material, and the weight part is a part made of a second material different from the first material.

Preferably, the eccentric weighting part is a part made of powder metallurgy, copper, zinc alloy or carbon steel, and the weight part is a part made of powder metallurgy or carbon steel.

Preferably, the eccentric weighted portion and the weighted portion are fixedly fitted by riveting, inlaying, interference fitting or screws.

According to another aspect of the present disclosure, there is provided a counterweight assembly for a scroll compressor, the counterweight assembly including a bush and the aforementioned counterweight.

Preferably, the drive shaft of the scroll compressor drives the movable scroll of the scroll compressor via the bush, the body portion includes a circular through hole, and the bush includes a The cylindrical part where the hole fits.

Preferably, the weight is mounted to the bush in such a manner that the inner peripheral surface of the circular through hole and the outer peripheral surface of the cylindrical portion are interference fitted.

Preferably, at least one first threaded hole is provided on the outer peripheral surface in the circumferential direction, and at least one second threaded hole corresponding to the at least one first threaded hole is provided on the inner peripheral surface, the The counterweight is also connected to the bush by threading the screw through the first threaded hole and the second threaded hole.

Preferably, a plurality of splines are provided along one circumferential direction on one of the outer peripheral surface of the cylindrical portion and the inner peripheral surface of the circular through hole, and the outer peripheral surface of the cylindrical portion and the circular shape A plurality of spline grooves corresponding to the plurality of splines are provided on the other one of the inner circumferential surfaces of the through holes, and the weight is installed to the bushing in such a manner that the splines and the spline grooves cooperate set.

Preferably, an interference fit is also implemented between the spline and the spline groove and / or a fixing device is also used at the axial ends of the spline and the spline groove to limit the counterweight Axial relative movement with the bushing.

Preferably, the spline is an involute spline or a rectangular spline.

Preferably, the weight is mounted to the bushing by welding.

Preferably, surface-to-surface welding is performed between the outer peripheral surface of the cylindrical portion and the inner peripheral surface of the circular through hole, and / or between the outer peripheral surface of the cylindrical portion and the circular through hole Seam welding is performed at the axial edges between the inner peripheral surfaces.

Preferably, the mounting portion is a component made of powder metallurgy, copper, zinc alloy or carbon steel, and the bushing is a component made of powder metallurgy.

Preferably, the bushing is an unloading bushing that allows the movable scroll of the scroll compressor to have radial flexibility.

According to yet another aspect of the present disclosure, a scroll compressor is provided, the scroll compressor including the weight assembly described above.

In the above scroll compressor: the orbiting scroll of the scroll compressor includes a hub, and the drive shaft of the scroll compressor includes an eccentric crank pin, which is fitted on the shaft via the bush In the hub to drive the movable scroll; or, the movable scroll of the scroll compressor includes a shank, and the drive shaft of the scroll compressor includes an eccentric recess, the shank passes through the lining The sleeve fits in the recess so that the movable scroll is driven by the drive shaft.

The advantage of the scroll compressor according to one or several embodiments of the present disclosure is, for example, that the structure of the fixed fit of the counterweight portion of the mounting portion through the eccentric weighting portion makes it possible to only adjust the weight without affecting the installation of the counterweight The shape and / or mass of the eccentric weighting part can be adjusted, so that the mass and / or geometric center of mass of the entire counterweight (weight assembly) can be flexibly adjusted to achieve different types of rotating members that are well suited to the compressor For example, the weight design of compression mechanism, motor, rotating shaft, bushing). In particular, for the counterweight mounted to the bushing, by flexibly splicing the counterweight functioning portion of the counterweight, for example, it is possible to conveniently change the counterweight mass and / or the radius of gyration, etc., so as to meet different compressor operations. Conditions, mechanical requirements, balance requirements and structural requirements under different materials, etc.

In another general aspect, an object of one or more embodiments of the present disclosure is to provide a weight assembly that is improved in terms of power consumption, etc., to overcome or alleviate at least one of the above-mentioned deficiencies.

In order to achieve the above object, according to one aspect of the present disclosure, there is provided a counterweight assembly for a scroll compressor, the counterweight assembly includes a bushing and a counterweight mounted on the bushing, the scroll The drive shaft of the rotary compressor drives the movable scroll of the scroll compressor via the bush, the counterweight includes a counterweight portion, and the counterweight portion includes a front end portion with respect to a rotation direction of the counterweight assembly And the tail end portion, the weight portion is configured such that the radial distance from the outer peripheral edge of the weight portion to the center of the weight assembly varies from the front end portion to the tail end portion.

Preferably, the outer peripheral edge of the weight portion is substantially arc-shaped.

Preferably, the radius of curvature of the outer peripheral edge changes from small to large from the front end to the tail end.

Preferably, the radius of curvature of the outer peripheral edge changes from small to large and then small from the front end to the tail end.

Preferably, the turning point of the change of the radius of curvature is located at a middle position of the outer periphery.

Preferably, the outer peripheral edge of the weight portion has a polygonal shape.

Preferably, the outer periphery has an equilateral polygonal shape.

Preferably, the outer periphery has an unequal polygonal shape.

Preferably, the outer angle of the equilateral polygon of the outer peripheral edge changes from small to large from the front end to the tail end.

Preferably, the front end portion includes a front axial end surface and a front circumferential end, and the front axial end surface is axially and circumferentially inclined toward the front circumferential end.

Preferably, when viewed in the radial direction, the angle of the front end formed by the front end is 25 degrees to 60 degrees.

Preferably, the tail end portion includes a tail axial end surface and a tail circumferential end, and the tail axial end surface is axially and circumferentially inclined toward the tail circumferential end.

Preferably, the front end portion is streamlined.

Preferably, the bushing is an unloading bushing that allows the movable scroll to have radial flexibility.

According to another aspect of the present disclosure, there is provided a scroll compressor including the weight assembly as described above.

Preferably, the movable scroll includes a hub, and the drive shaft of the scroll compressor includes an eccentric crank pin that is fitted in the hub via the bush to drive the movable scroll Or the movable scroll includes a handle, and the drive shaft includes an eccentric recess, the handle is fitted in the eccentric recess via the bushing so that the movable scroll is driven by the drive shaft.

The advantages of the counterweight assembly and the scroll compressor according to one or several embodiments of the present disclosure are, for example, a counterweight portion (circular arc) with the counterweight (disk) in which the outer peripheral edge The radial distance to the center, that is, the rotation center, is equal to the radius, so that the position of the center of mass of the counterweight and the radius of gyration are relatively fixed and lack of change, so it is difficult to adapt to the non-circular motion trajectory caused by eccentric rotation and lead to an increase in gas power consumption In contrast, by changing the radial distance (radius) of the counterweight and (unloading) bushing center of coordination (i.e., the center of rotation) to the periphery (outer periphery) of the counterweight portion, it is possible to flexibly change the counterweight Shape and center of mass position to adapt to gas force distribution and reduce gas power consumption. Also, the outer peripheral shape configuration of the weight assembly according to the present disclosure facilitates oil stirring, thereby improving oil circulation, and can facilitate the installation and positioning of the weight and (unloading) the bushing, for example, in the case of adopting a polygonal outer periphery.

BRIEF DESCRIPTION

The features and advantages of one or several embodiments of the present disclosure will become easier to understand through the following description with reference to the drawings, in which:

1A and 1B are perspective views showing counterweights according to the related art;

2 is a longitudinal sectional view showing a scroll compressor to which a counterweight according to the present disclosure is applied;

3 is a partially enlarged longitudinal sectional view showing the weight assembly of FIG. 2;

4 and 5 are a cross-sectional view and a perspective view respectively showing a counterweight according to an embodiment of the present disclosure;

6 and 7 are a cross-sectional view and a perspective view showing a modified example of the weight according to an embodiment of the present disclosure;

8 is a perspective view showing a counterweight assembly according to the present disclosure, in which the counterweight and the bush are connected with an interference fit;

9 and 10 are a cross-sectional view and a perspective view respectively showing a modified example of the weight assembly according to the present disclosure, in which the weight and the bush are connected by screws;

FIG. 11 is a perspective view showing a modified example of the weight assembly according to the present disclosure, in which the weight and the bush are splinedly connected;

12 and 13 are a cross-sectional view and a perspective view respectively showing a modified example of the weight assembly according to the present disclosure, in which the weight and the bushing interference are connected by welding;

14 is a partial cross-sectional view showing a modification of the scroll compressor according to the present disclosure;

15 is a longitudinal sectional view showing a scroll compressor to which a weight assembly according to the present disclosure is applied;

16 is an enlarged longitudinal sectional view showing the weight assembly of FIG. 15;

17 is a perspective view showing the weight assembly of FIG. 15;

18 is a top view showing a weight assembly according to an aspect of another embodiment of the present disclosure;

FIG. 19 is a top view showing a weight assembly according to another aspect of another embodiment of the present disclosure;

FIG. 20 is a perspective view showing the weight of the weight assembly according to the present disclosure;

21 is a plan view showing the counterweight of FIG. 20;

22 is a side view showing the weight of FIG. 20;

23 is a side view showing the weight of the weight assembly according to another aspect of the present disclosure;

24 is a plan view showing a counterweight according to an aspect of still another embodiment of the present disclosure;

25 is a plan view showing a counterweight according to another aspect of yet another embodiment of the present disclosure; and

FIG. 26 is a partial longitudinal sectional view showing another scroll compressor to which the weight assembly according to the present disclosure is applied.

detailed description

The following description of the preferred embodiments is merely exemplary, and in no way limits the disclosure and its application or usage.

The same reference numerals are used in the various drawings to denote the same components, so the configuration of the same components will not be repeated.

1A and 1B are perspective views showing weights according to the related art. In the weight 170 ′ for attaching to the rotor according to the related art shown in FIG. 1A, the weight portion 174 ′ is provided at the attachment portion along a part of the circumference of the attachment portion 172 ′ having a circular ring shape 172 'on the axial surface. In the counterweight 170 "for attaching to the drive shaft according to the related art shown in FIG. 1B, the counterweight 174" is provided at the attachment portion 172 along the sector-shaped edge of the attachment portion 172 "that is substantially fan-shaped "Radially outward.

The basic configuration and principle of the counterweight, the counterweight assembly, and the scroll compressor according to the embodiments of the present disclosure will be described below with reference to FIGS. 2 to 7.

As shown in FIG. 2, the scroll compressor 10 according to an embodiment of the present disclosure generally includes a housing 110, a top cover 112 provided at one end of the housing 110, a bottom cover 114 provided at the other end of the housing 110, and a top Between the cover 112 and the housing 110 to divide the internal space of the compressor into a partition 116 on the high-pressure side and the low-pressure side. The partition 116 and the top cover 112 form a high-pressure side, and the partition 116, the housing 110 and the bottom cover 114 form a low-pressure side. An intake joint 118 for sucking fluid is provided on the low-pressure side, and an exhaust joint 119 for discharging compressed fluid is provided on the high-pressure side. A motor 120 composed of a stator 122 and a rotor 124 is provided in the housing 110. The rotor 124 is provided with a drive shaft 30 to drive a compression mechanism composed of a fixed scroll 150 and a movable scroll 160. The movable scroll 160 includes an end plate 164, a hub portion 162 formed on one side of the end plate, and a spiral blade 166 formed on the other side of the end plate. The fixed scroll 150 includes an end plate 154, a spiral blade 156 formed on one side of the end plate, and an exhaust port 152 formed at a substantially central position of the end plate. Between the spiral blade 156 of the fixed scroll 150 and the spiral blade 166 of the movable scroll 160 are formed a series of compression chambers whose volume gradually decreases from the radially outer side to the radially inner side.

A part of the drive shaft 30 is supported by the main bearing 144 provided in the main bearing housing 20. An eccentric crank pin 32 is formed at one end of the drive shaft 30. The eccentric crank pin 32 is fitted in the hub 162 of the movable scroll 160 via a bush (unloading bush) 200 to drive the movable scroll 160.

The main bearing housing 20 is provided with a main bearing cover plate 50 as a thrust plate. The main bearing cover 50 may be fixed to the main bearing housing 20 by a fixing device. A space is formed between the main bearing housing 20 and the main bearing cover 50. One side of the movable scroll 160 is supported by the main bearing cover 50. Driven by the motor 120, the movable scroll 160 will rotate in translation relative to the fixed scroll 150 (ie, the central axis of the movable scroll 160 rotates around the central axis of the fixed scroll 150, but the movable scroll 160 itself does not revolve around itself The central axis of the rotation) to achieve fluid compression. The above translational rotation is achieved by the cross slip ring 190 provided between the fixed scroll 150 and the movable scroll 160. The fluid compressed by the fixed scroll 150 and the movable scroll 160 is discharged to the high-pressure side through the exhaust port 152. In order to prevent the fluid on the high-pressure side from flowing back to the low-pressure side through the exhaust port 152 under certain circumstances, a check valve or an exhaust valve 170 is provided at the exhaust port 152.

In order to reduce the contact force between the side surface of the spiral blade 156 of the fixed scroll 150 and the side surface of the spiral blade 166 of the movable scroll 160, a counterweight 300 according to an embodiment of the present disclosure is further provided. The counterweight 300 is configured to be able to rotate with the drive shaft 30 and the centrifugal force due to the rotation of the counterweight 300 acts on the hub 162 of the movable scroll 160.

Referring to FIGS. 4 to 5, the counterweight 300 of the present disclosure includes a mounting portion 310a and an axial eccentric weighting portion 310b (here, it should be noted that the eccentric weighting portion 310b may be set as a single or multiple according to circumstances), the mounting portion 310a It includes a body portion 310a1 and a weight portion 310a2 extending axially from the body portion 310a1 (here, it should be noted that the body portion and the weight portion may be formed integrally or separately), the weight portion 310a2 includes a substantially flat axial direction The outer surface 3101, the axial eccentric weighted portion 310b includes a corresponding substantially flat axial surface 3102, and the axial surface 3102 of the axial eccentric weighted portion 310b is fixedly fitted to the axial surface 3101 of the weight portion 310a2. 6 and 7, the counterweight 300 includes a mounting portion 320a and a radial eccentric weighted portion 320b, the radial eccentric weighted portion 320b includes a radial inner surface 3202, the mounting portion 320a includes a main body portion 320a1 and a radial direction from the main body portion 320a1 The extended weight portion 320a2 includes a radially outer surface 3201, and a radially inner surface 3202 of the radial eccentric weight portion 320b is fixedly fitted to the radially outer surface 3201 of the weight portion 320a2. Compared with the counterweight of the related art, the counterweight of the present disclosure adopts a split structure, in particular, a structure in which the eccentric weighting portion and the counterweight portion of the mounting portion are fixedly fitted so that the installation of the counterweight is not affected Only the shape and / or mass of the eccentric weighting part is adjusted, so that the mass and / or geometric center of mass of the entire counterweight (counterweight assembly) can be flexibly adjusted to achieve a good configuration for different types of compressors Counterweight design of rotating members (eg, compression mechanism, motor, rotating shaft, bushing). In particular, for the counterweight mounted to the bushing, by flexibly splicing the counterweight functioning portion of the counterweight, for example, it is possible to conveniently change the counterweight mass and / or the radius of gyration, etc., so as to meet different compressor operations. Conditions, mechanical requirements, balance requirements and structural requirements under different materials, etc.

In FIGS. 5 and 7, the main body portions 310a1 and 320a1 have a circular ring shape, and the weight portions 310a2 and 320a2 are substantially axially and radially extending from a part of the circumferential periphery (outer periphery) of the main body portions 310a1 and 320a1 Curved counterweight. This configuration facilitates a fixed fit with the eccentric weight without affecting installation and allows more flexible adjustment of the position of the center of mass (for example, the position of the center of mass can be displaced radially and / or axially). Of course, the main body parts 310a1 and 320a1 may also be partially circular.

In particular, in order to facilitate the adjustment of the mass and / or the position of the center of mass of the counterweight, it may be considered to flexibly select the material of the eccentric weight and the material of the weight, especially the material of the eccentric weight so that the material of the eccentric weight and the weight The material of the heavy part has a certain difference in density and so on. For example, the eccentric weighting part may be a part made of powder metallurgy, copper, zinc alloy or carbon steel, and the weight part may be a part made of powder metallurgy or carbon steel.

In addition, the eccentric weighted portion and the weighted portion are fixedly fitted by riveting, inlaying (see FIG. 6), interference fit, or screws.

According to another aspect of the present disclosure, with reference to FIGS. 3 and 8, the weight assembly according to the present disclosure is further described. The cylindrical portion 201 through which the through hole 301 fits. The counterweight 300 may be attached to the bush 200 in such a manner that the inner peripheral surface of the circular through hole 301 and the outer peripheral surface of the cylindrical portion 201 are interference fitted. The round-to-round interference fit of the counterweight and the bushing can simplify the assembly process and greatly reduce the processing cost.

Preferably, the bushing 200 may be an unloading bushing capable of radial translation relative to the drive shaft 30. Specifically, a substantially flat driving surface may be provided on the outer surface of the eccentric crank pin 32 of the drive shaft 30, and a substantially flat sliding surface may be provided on the inner surface of the unloading bush that slidingly fits with the driving surface of the eccentric crank pin 32 Driven surface. This radial sliding fit of the driven surface of the eccentric crank pin with the driven surface of the unloading bushing provides radial flexibility for the movable scroll of the compressor, thereby preventing substances such as foreign particles or liquid working fluid When entering the compression mechanism, the movable scroll is allowed to be temporarily displaced radially relative to the fixed scroll to prevent the scroll blades from being damaged due to excessive force.

In order to ensure a reliable and fixed fit and connection between the counterweight (specifically, the main body of the mounting portion of the counterweight) and the bushing, two linear expansion coefficients or Young's modulus can be considered for the mounting portion and the bushing The same or different materials are similar, which is more conducive to the guarantee of tightening force and the guarantee of normal working strength. Preferably, the mounting portion is a component made of powder metallurgy, copper, zinc alloy or carbon steel, and the bushing is a component made of powder metallurgy.

Referring to FIGS. 9 and 10, further, on the outer circumferential surface of the cylindrical portion 201 of the bush 200, four first threaded holes 202 are uniformly provided in the circumferential direction with respect to the central axis O of the circular through hole 301 in the inner circumferential surface Four second threaded holes 302 corresponding to the four first threaded holes 202 are provided thereon, and the counterweight 300 is also connected to the bush 200 by passing screws through the first threaded holes 202 and the second threaded holes 302. The connection strength when the counterweight and the bush are connected by means of screw thread is more reliable, and the reliability of the counterweight assembly and thus the compressor is higher. Although four screw holes are shown in the drawings, other numbers of screw holes may be provided as needed.

Referring to FIG. 11, further, a plurality of splines are provided on the outer circumferential surface of the cylindrical portion 201 of the bush 200 in the circumferential direction, and a plurality of splines are provided on the inner circumferential surface of the round through hole 301 of the weight Corresponding to the multiple spline grooves, the counterweight 300 is mounted to the bushing 200 in a manner that the splines and the spline grooves cooperate. Of course, it is also possible to provide splines on the inner peripheral surface of the round through-hole of the weight, and corresponding spline grooves on the outer peripheral surface of the cylindrical portion of the bush. In addition, an interference fit may be implemented between the spline and the spline groove and / or a fixing device may be used at the axial end of the spline and the spline groove to limit the axial direction between the counterweight 300 and the bush 200 Relative movement. Although the spline shown in the figure is an involute spline, the type of spline is not limited to this, for example, the spline may also be a rectangular spline.

Referring to FIG. 12, surface-to-surface welding is performed between the outer circumferential surface of the cylindrical portion 201 and the inner circumferential surface of the circular through hole 301. Referring to FIG. 13, a seam welding is performed at the axial edge between the outer circumferential surface of the cylindrical portion 201 and the inner circumferential surface of the circular through hole 301. To meet the requirements of welding, preferably, the mounting part is a component made of powder metallurgy or carbon steel, and the unloading bush is a component made of powder metallurgy.

In addition to the scroll compressor 10 according to the present disclosure as shown in FIG. 2, referring to FIG. 14, the counterweight according to the present disclosure is also applicable to another scroll compressor as shown in FIG. 14. The difference from the scroll compressor shown in FIG. 2 is that, in the scroll compressor shown in FIG. 14, the movable scroll 160 includes a handle 163 and the drive shaft 30 of the scroll compressor includes an eccentric recess 132, the handle 163 is fitted in the recess via the bush 200 so that the movable scroll 160 is driven by the drive shaft 30.

Preferably, in the scroll compressor of this embodiment, the bushing 200 may also be an unloading bushing that can be translated radially with respect to the drive shaft 30. Specifically, a substantially flat driving surface may be provided on the side surface of the eccentric recess 132, and a substantially flat driven surface slidingly fitted with the driving surface may be provided on the outer surface of the unloading bush. This radial sliding fit of the drive surface of the eccentric recess and the driven surface of the unloading bush provides radial flexibility for the movable scroll of the compressor.

The basic configuration and principle of the scroll compressor 10C to which the weight assembly according to another embodiment of the present disclosure is applied will be described below with reference to FIGS. 15 to 23.

As shown in FIG. 15, a scroll compressor 10C according to an embodiment of the present disclosure generally includes a housing 110C, a top cover 112C provided at one end of the housing 110C, a bottom cover 114C provided at the other end of the housing 110C, and a top cover A partition 116C that divides the internal space of the compressor into a high-pressure side and a low-pressure side between 112C and the casing 110C. A high-pressure side is formed between the partition 116C and the top cover 112C, and a low-pressure side is formed between the partition 116C, the housing 110C, and the bottom cover 114C. An intake joint 118C for sucking fluid is provided on the low-pressure side, and an exhaust joint 119C for discharging compressed fluid is provided on the high-pressure side. A motor 120C composed of a stator 122C and a rotor 124C is provided in the housing 110C. The rotor 124C is provided with a drive shaft 30C to drive a compression mechanism composed of a fixed scroll 150C and a movable scroll 160C. The movable scroll 160C includes an end plate 164C, a hub portion 162C formed on one side of the end plate, and a spiral blade 166C formed on the other side of the end plate. The fixed scroll 150C includes an end plate 154C, a spiral blade 156C formed on one side of the end plate, and an exhaust port 152C formed at a substantially central position of the end plate. Between the spiral blade 156C of the fixed scroll 150C and the spiral blade 166C of the movable scroll 160C are formed a series of compression chambers whose volume gradually decreases from the radially outer side to the radially inner side.

A part of the drive shaft 30C is supported by the main bearing 144C provided in the main bearing housing 20C. An eccentric crank pin 32C is formed at one end of the drive shaft 30C.

The main bearing housing 20C is provided with a main bearing cover 50C as a thrust plate. The main bearing cover 50C may be fixed to the main bearing housing 20C by a fixing device. A space is formed between the main bearing housing 20C and the main bearing cover 50C. One side of the movable scroll 160C is supported by the main bearing cover 50C. Driven by the motor 120C, the movable scroll 160C will rotate in translation relative to the fixed scroll 150C (ie, the central axis of the movable scroll 160C rotates around the central axis of the fixed scroll 150C, but the movable scroll 160C itself will not revolve around itself The central axis of the rotation) to achieve fluid compression. The above-mentioned translational rotation is achieved by the cross slip ring 190C provided between the fixed scroll 150C and the movable scroll 160C. The fluid compressed by the fixed scroll 150C and the movable scroll 160C is discharged to the high-pressure side through the exhaust port 152C. In order to prevent the fluid on the high-pressure side from flowing back to the low-pressure side through the exhaust port 152C under certain circumstances, a check valve or an exhaust valve 170C is provided at the exhaust port 152C.

In order to reduce the contact force between the side surface of the spiral blade 156C of the fixed scroll 150C and the side surface of the spiral blade 166C of the movable scroll 160C, referring to FIGS. 16 to 17, the scroll compressor 10C is further provided with The counterweight assembly includes a bush 200C and a counterweight 100C mounted on the bush 200C, and the drive shaft 30C of the scroll compressor drives the movable scroll 160C of the scroll compressor via the bush 200C. 18 to 19, the weight 100C includes a weight portion 300C, the weight portion 300C includes a front end portion 310C and a tail end portion 320C with respect to the rotation direction RD of the weight assembly, wherein the outer periphery of the weight portion 300C is substantially Arc shape, and the weight portion 300C is configured such that the radius of curvature ρ of the outer peripheral edge of the weight portion 300C changes from small to large from the front end portion 310C to the trailing end portion 320C (as shown in FIG. 18, the outer peripheral edge is shown with respect to the dotted line Arc change) to adapt to the gas force distribution when the weight assembly rotates in the direction of rotation RD, thereby reducing gas power consumption, especially in the environment where the weight is located, there is a moving fluid flow and / or the weight is attached The moving parts such as the bushing need to perform high-speed movement, such as 3600 rpm or more compressors, such as high-speed moving variable-speed compressors, due to the weight and therefore the weight of the attached moving parts, that is, the movement resistance of the entire rotating structure ( Fluid resistance) is reduced, so the power consumption of the rotating structure and thus the compressor is reduced. At the same time, this configuration makes the distance between the center of mass M of the counterweight and the center of rotation O2 of the counterweight assembly (ie, radius of gyration r) adjustable, that is, the radius of gyration r is determined by the shape design of the counterweight , The position of the center of mass M can be adjusted by changing the radius of curvature of the counterweight (in particular, the outer periphery of the counterweight), thereby reducing the impact of different compressor designs on assembly and production, and can also meet the different working conditions of the compressor, Mechanical requirements, balance requirements and structural requirements under different materials, etc.

Advantageously, as shown in FIG. 19, the radius of curvature ρ of the outer peripheral edge of the weight portion can also be changed from small to large and then smaller from the front end to the tail end, not only at the front end (windward surface) of the weight The pressure decreases and the drag caused by the wake (turbulence) at the tail end of the counterweight is reduced, that is, the pressure difference resistance encountered by the counterweight in motion and the head-on resistance (due to the presence of fluid And cause) to reduce, further reducing gas power consumption. Further, the turning point of the change of the radius of curvature ρ of the outer peripheral edge of the weight portion may be located at a middle position of the outer peripheral edge to further improve the reduction of resistance.

According to an aspect of this embodiment, referring to FIGS. 20 to 22, the front end portion 310C of the weight portion includes a front axial end surface 311C and a front circumferential end 312C that faces the front circumferential end 312C axis Tilt to the ground and circumferentially. With the inclined configuration of the front axial end surface, the gas resistance can be reduced to reduce the increase in gas power consumption, and the effect of pumping oil upward in the axial direction when the weight assembly rotates is provided, thereby improving oil circulation.

Further, referring to FIG. 22, when viewed in the radial direction, the angle γ of the front end formed by the front end may be greater than 0 degrees and less than 90 degrees, in particular, the angle γ of the front end is 25 degrees to 60 degrees, more particularly The angle γ of the tip portion is 25 degrees to 40 degrees.

In addition, the tail end portion 320C of the weight portion may also include a tail axial end surface 321C and a tail circumferential end 322C, the tail axial end surface 321C is axially and circumferentially inclined toward the tail circumferential end 322C, thereby reducing The drag caused by the wake at the tail end of the counterweight.

Advantageously, referring to FIG. 23, the front end portion 310C of the weight portion is streamlined to further reduce the resistance of the fluid at the front end portion (windward surface), wherein the front axial end surface 311C of the front end portion 310C is a streamlined curved surface.

In addition, the aforementioned bushing may be an unloading bushing that allows the movable scroll to have radial flexibility.

24 and 25 are top views showing a weight assembly according to another embodiment of the present disclosure, wherein, referring to FIG. 24, the outer periphery of the weight portion 500C of the weight 400C of the weight assembly may have an equilateral polygonal shape . In particular, referring to FIG. 25, the outer periphery of the weight portion 500C may also have an unequal polygon shape, and the outer corners A1, A2, and A3 of the unequal polygon of the outer periphery (only three are shown schematically in the figure) The outer corners, the number of outer corners are determined according to the unequal polygon of the outer peripheral edge of the weight portion) from the front end portion 510C to the tail end portion 520C from small to large. That is, with the above configuration, similar to the foregoing embodiment, the radial distance (radius) from the outer peripheral edge of the weight portion to the center O1 of the weight assembly (corresponding to the rotation center of the weight) from the front end From the end to the end, so that the distance between the center of mass of the counterweight and the center of rotation of the counterweight assembly changes accordingly to adapt to the gas force distribution when the counterweight assembly rotates in the direction of rotation RD, thereby reducing Gas power consumption. In particular, since the counterweight portion of the counterweight is polygonal, it is convenient to stir oil to improve oil circulation, and compared with the curved outer periphery of the counterweight, an accurate installation angle of the counterweight relative to the bush can be achieved, in particular, In the case where an unloading bush is used, the precise mounting angle of the counterweight with respect to the bush is achieved at an angle between the corresponding side of the polygon and the driving surface of the unloading bush.

It should be noted that in another embodiment, the features such as the inclined structure of the front axial end surface of the front end portion of the weight portion, the angle of the front end portion, the streamlined front end structure, and the unloading bush are all applicable to the disclosure Another embodiment.

In addition to the scroll compressor 10C according to the present disclosure as shown in FIG. 15, referring to FIG. 26, the weight assembly according to the present disclosure is also applicable to another scroll compressor as shown in FIG. 26. The difference from the scroll compressor shown in FIG. 15 is that, in the scroll compressor shown in FIG. 26, the movable scroll 160C includes a shank 163C, and the drive shaft 30C of the scroll compressor includes an eccentric recess At 132C, the shank 163C is fitted in the recess via the bush 200C so that the movable scroll 160C is driven by the drive shaft 30C.

Although various embodiments of the present disclosure have been described in detail herein, it should be understood that the present disclosure is not limited to the specific embodiments described and shown in detail herein, and that it can be used in the field without departing from the spirit and scope of the present disclosure. The technician implements other variants and variants. All these variations and variants fall within the scope of the present disclosure. Moreover, all components described herein may be replaced by other technically equivalent components.

Claims

A counterweight assembly for a scroll compressor, characterized in that the counterweight assembly includes a bush and a counterweight mounted on the bush, and the drive shaft of the scroll compressor passes through the bush The movable scroll of the scroll compressor is driven by a sleeve, the counterweight includes a counterweight portion, the counterweight portion includes a front end portion and a rear end portion with respect to a rotation direction of the counterweight assembly, the counterweight portion It is configured such that the radial distance from the outer peripheral edge of the weight portion to the center of the weight assembly varies from the front end portion to the tail end portion.
The weight assembly of claim 1, wherein the outer peripheral edge of the weight portion is substantially arc-shaped.
The weight assembly according to claim 2, wherein the radius of curvature of the outer peripheral edge changes from small to large from the front end to the tail end.
The weight assembly according to claim 2, wherein the radius of curvature of the outer periphery changes from small to large and then small from the front end to the rear end.
The weight assembly according to claim 4, wherein the turning point of the change of the radius of curvature is located at a middle position of the outer periphery.
The weight assembly according to claim 1, wherein the outer peripheral edge of the weight portion has a polygonal shape.
The weight assembly according to claim 6, wherein the outer periphery has an equilateral polygonal shape.
The counterweight assembly of claim 6, wherein the outer peripheral edge has an unequal polygonal shape.
The weight assembly according to claim 8, wherein the outer angle of the equilateral polygon of the outer peripheral edge changes from small to large from the front end to the tail end.
The weight assembly according to any one of claims 1 to 9, wherein the front end portion includes a front axial end surface and a front circumferential end, the front axial end surface facing the front circumferential end axis Tilt to the ground and circumferentially.
The weight assembly according to claim 10, wherein the front end portion formed by the front end portion has an angle of 25 degrees to 60 degrees when viewed in the radial direction.
The weight assembly of claim 10, wherein the tail end portion includes a tail axial end surface and a tail circumferential end, the tail axial end surface is axially and circumferentially toward the tail circumferential end Tilted.
The weight assembly according to any one of claims 1 to 9, wherein the front end portion is streamlined.
The weight assembly according to any one of claims 1 to 9, wherein the bushing is an unloading bushing that allows the movable scroll to have radial flexibility.
A scroll compressor, characterized in that the scroll compressor includes the weight assembly according to any one of claims 1 to 14.
The scroll compressor of claim 15, wherein:

The movable scroll includes a hub, and the drive shaft of the scroll compressor includes an eccentric crank pin that is fitted in the hub via the bush to drive the movable scroll; or

The movable scroll includes a handle, and the drive shaft includes an eccentric recess, and the handle is fitted in the eccentric recess via the bushing so that the movable scroll is driven by the drive shaft.
A counterweight for a scroll compressor, characterized in that the counterweight includes a mounting portion and an eccentric weighting portion, the mounting portion includes a main body portion and a counterweight portion extending from the main body portion, the eccentric The weighted portion is fixedly fitted to the weighted portion.
The counterweight according to claim 17, wherein:

The body portion is completely or partially circular, and

The weight portion extends axially relative to the main body portion, or radially extends relative to the main body portion, or extends axially and radially relative to the main body portion.
The counterweight according to claim 18, wherein the body portion has a completely circular ring shape, and the weight portion is a substantially arc extending axially and radially from a portion of the circumferential periphery of the body portion Shaped counterweight.
The weight according to claim 18, wherein the eccentric weighted portion includes an axial weighted portion and / or a radial weighted portion, the axial weighted portion is axially fixedly fitted to the weighted portion, the The radial weighted portion is radially fixedly fitted to the weighted portion.
The counterweight according to any one of claims 17 to 20, wherein the eccentric weighted portion is a member made of a first material, and the weighted portion is made of a material different from the first material. Two parts made of materials.
The counterweight according to any one of claims 17 to 20, wherein the eccentric weighted portion is a member made of powder metallurgy, copper, zinc alloy, or carbon steel, and the weighted portion is made of powder metallurgy Or parts made of carbon steel.
The weight according to any one of claims 17 to 20, wherein the eccentric weighted portion and the weighted portion are fixedly fitted by riveting, inlaying, interference fitting, or screws.
A weight assembly for a scroll compressor, characterized in that the weight assembly includes a bush and the weight according to any one of claims 17 to 23.
The counterweight assembly of claim 24, wherein the drive shaft of the scroll compressor drives the movable scroll of the scroll compressor via the bushing, and the body portion includes a circular through hole, so The bushing includes a cylindrical portion that cooperates with the circular through hole.
The weight assembly according to claim 25, wherein the weight is attached to the bush in such a manner that the inner peripheral surface of the circular through hole and the outer peripheral surface of the cylindrical portion are interference fitted.
The counterweight assembly according to claim 26, wherein at least one first threaded hole is provided on the outer peripheral surface in the circumferential direction, and a corresponding to the at least one first threaded hole is provided on the inner peripheral surface At least one second threaded hole, the counterweight is also connected to the bush by passing a screw through the first threaded hole and the second threaded hole.
The weight assembly according to claim 25, wherein a plurality of splines are circumferentially provided on one of the outer circumferential surface of the cylindrical portion and the inner circumferential surface of the circular through-hole, in the A plurality of spline grooves corresponding to the plurality of splines are provided on the other of the outer circumferential surface of the cylindrical portion and the inner circumferential surface of the circular through hole, and the counterweight is formed by the spline and the The spline groove is fitted to the bushing in a cooperating manner.
The weight assembly according to claim 28, wherein an interference fit is also implemented between the spline and the spline groove and / or at the axial ends of the spline and the spline groove A fixing device is used to limit the axial relative movement between the weight and the bush.
The weight assembly of claim 28, wherein the spline is an involute spline or a rectangular spline.
The weight assembly of claim 25, wherein the weight is mounted to the bushing by welding.
The weight assembly according to claim 31, wherein surface-to-surface welding is performed between the outer circumferential surface of the cylindrical portion and the inner circumferential surface of the circular through hole, and / or Seam welding is performed at the axial edge between the outer peripheral surface and the inner peripheral surface of the circular through hole.
The weight assembly according to any one of claims 24 to 32, wherein the mounting portion is a member made of powder metallurgy, copper, zinc alloy, or carbon steel, and the bushing is made of powder metallurgy Into parts.
The counterweight assembly according to any one of claims 24 to 32, wherein the bushing is an unloading bushing that allows the movable scroll of the scroll compressor to be provided with radial flexibility.
A scroll compressor, characterized in that the scroll compressor includes the weight assembly according to any one of claims 24 to 34.
The scroll compressor of claim 35, wherein:

The movable scroll of the scroll compressor includes a hub, and the drive shaft of the scroll compressor includes an eccentric crank pin that is fitted in the hub via the bush to drive the Moving vortex; or

The movable scroll of the scroll compressor includes a handle, and the drive shaft of the scroll compressor includes an eccentric recess, and the handle is fitted in the eccentric recess via the bush so that the movable scroll Driven by the drive shaft.