CN220869651U - Scroll compressor having a rotor with a rotor shaft having a rotor shaft with a - Google Patents

Abstract

The present utility model provides a scroll compressor, comprising: a fixed scroll; a centrifugal motion assembly including an orbiting scroll including a hub portion and a center of mass adjustment member including a hub portion and a driving shaft including an eccentric crank pin fitted in the hub portion to drive the orbiting scroll to orbit relative to the fixed scroll to generate a centrifugal force, wherein the center of mass adjustment member is configured to rotate with the driving shaft, the centrifugal force generated by its rotation always acts on the hub portion of the orbiting scroll and is directed substantially opposite to the direction of the centrifugal force generated by the orbiting scroll, the center of mass adjustment member including a main body portion and an adjustment portion movable in a radial direction of the scroll compressor relative to the main body portion as a rotational speed of the driving shaft varies, such that a center of mass of the centrifugal motion assembly varies as the rotational speed of the driving shaft varies. According to the scroll compressor disclosed by the utility model, the contact force between the scrolls can be kept in a reasonable interval under different rotating speeds, so that the friction between the scrolls is reduced, the noise is reduced and the energy efficiency is improved.

Description

Scroll compressor having a rotor with a rotor shaft having a rotor shaft with a

Technical Field

The present utility model relates to the field of compressors, and in particular to a centrifugal motion assembly for a scroll compressor, and more particularly to a centrifugal motion assembly for a variable frequency scroll compressor.

Background

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

Scroll compressors typically include a compression mechanism consisting of a non-orbiting scroll and an orbiting scroll that engage one another to form a series of chambers therebetween for compressing a working fluid. The movable vortex moves in translation relative to the fixed vortex under the drive of the eccentric component, so that the fluid in the cavity is compressed. In order to achieve compression of the fluid, an effective radial seal must be formed between the non-orbiting and orbiting scrolls, i.e., a certain radial contact force needs to be maintained between the non-orbiting and orbiting scrolls. On the other hand, the orbiting scroll will generate centrifugal force during the orbiting process relative to the non-orbiting scroll, which will have a direct effect on the radial contact force between the scrolls.

When a scroll compressor, particularly a variable frequency scroll compressor, runs at a high speed, centrifugal force generated by an movable scroll is increased sharply, so that radial contact force between the movable scroll and a fixed scroll is increased sharply, at the moment, the damage risk of the scroll is high, and meanwhile, noise of the running of the compressor is increased; when the scroll compressor runs at a low speed, the centrifugal force generated by the movable scroll is reduced, but a certain contact force is needed between the movable scroll and the fixed scroll to realize radial sealing between the movable scroll and the fixed scroll.

In addition, during the operation of the scroll compressor, centrifugal force or centrifugal moment generated by the rotation of the eccentric member may cause vibration of the compressor. A counterweight is typically provided on a rotating member, such as the upper end of a drive shaft, to provide a counter centrifugal force or centrifugal torque to balance the amount of unbalance created by the eccentric member. Obviously, the centrifugal force provided by the balance weight and the centrifugal force generated by the movable vortex form a reverse moment, so that radial contact force between the movable vortex and the fixed vortex is influenced to a certain extent. Therefore, for variable frequency compressors, it is often difficult to select a balance weight of suitable mass, and the balance weight cannot effectively adjust the radial contact force between the orbiting scroll and the non-orbiting scroll.

Therefore, there is a need to provide an improved centroid adjuster and a scroll compressor including the centroid adjuster, so as to balance radial contact forces between an orbiting scroll and a non-orbiting scroll of the scroll compressor in a high rotational speed state and a low rotational speed state, ensure that the scroll compressor has good radial seal in each rotational speed state, reduce friction loss between the orbiting scroll and the non-orbiting scroll, reduce compressor operation noise, and have lower design strength requirements on the scrolls.

Disclosure of utility model

The accompanying drawings are included to provide a general overview of the utility model and are not intended to provide a complete disclosure of the full scope of the utility model or all-character thereof.

It is an object of the present utility model to provide a scroll compressor equipped with a centrifugal motion assembly having its center of mass adjusted with the rotational speed of the scroll compressor, the centrifugal motion assembly including a center of mass adjuster to ensure that the contact force between the scrolls of the compressor at different rotational speeds is maintained within a reasonable interval.

It is another object of the present utility model to provide a scroll compressor equipped with a centrifugal motion assembly having a center of mass adjusted with the rotational speed of the scroll compressor, the centrifugal motion assembly including a center of mass adjuster to achieve stepless adjustment of the contact force between the scrolls of the compressor.

According to one aspect of the present utility model, there is provided a scroll compressor comprising: the fixed vortex comprises a fixed vortex end plate and a fixed vortex blade formed on one side of the fixed vortex end plate; the centrifugal motion assembly comprises an movable vortex and a mass center adjusting piece, wherein the movable vortex comprises an movable vortex end plate, movable vortex blades formed on one side of the movable vortex end plate and a hub part formed on the other side of the movable vortex end plate; and a driving shaft including an eccentric crank pin fitted in the hub portion to drive the orbiting scroll to orbit with respect to the fixed scroll to generate a centrifugal force, wherein the centroid adjusting member is configured to rotate with the driving shaft, the centrifugal force generated by the rotation of the centroid adjusting member always acts on the hub portion of the orbiting scroll, the direction of the centrifugal force generated by the centroid adjusting member is substantially opposite to the direction of the centrifugal force generated by the orbiting scroll, and wherein the centroid adjusting member includes a main body portion and an adjusting portion movable in a radial direction of the scroll compressor with respect to the main body portion as a rotational speed of the driving shaft varies, such that a centroid of the centrifugal movement assembly varies in the radial direction of the scroll compressor as the rotational speed of the driving shaft varies.

Optionally, the main body portion and the adjusting portion are connected to each other by an elastic member, and the mass and the position of the adjusting portion and the pretightening force of the elastic member are set to: in the case where the rotation speed is less than or equal to the preset rotation speed, the adjusting portion is maintained at the initial position.

Optionally, the mass and position of the adjustment portion and the pretension of the elastic member are set to: when the rotational speed increases beyond the preset rotational speed, the adjustment portion moves from the initial position in a direction away from the main body portion until reaching an equilibrium position where the centrifugal force generated by the adjustment portion is equal to the elastic force of the elastic member.

Optionally, the mass and position of the adjustment portion and the pretension of the elastic member are set to: the adjusting portion moves toward the initial position until the initial position under the condition that the rotational speed gradually decreases to or below the preset rotational speed.

Optionally, a limiting member is provided on the main body portion and/or the adjustment portion to prevent the adjustment portion from being completely separated from the main body portion.

Optionally, the main body portion includes a recess opening outwardly in the radial direction, the adjustment portion being fully accommodated in the recess in the initial position.

Optionally, the adjustment portion comprises a channel extending in a radial direction, the resilient member being at least partially received in the channel.

Alternatively, the groove is formed with a first fixing portion at an outer end in a radial direction, the recess is formed with a second fixing portion at an inner end in the radial direction, both ends of the elastic member are respectively formed with a hook, the hook at one end of the elastic member is connected to the first fixing portion, and the hook at the other end of the elastic member is connected to the second fixing portion.

Optionally, the main body portion includes a recess setting portion provided with a recess and other portions not provided with a recess in an axial direction of the scroll compressor, and a length of the recess setting portion in a radial direction is greater than a length of the other portions in the radial direction.

Optionally, the scroll compressor further comprises an unloading bushing provided between the eccentric crank pin and the hub such that the eccentric crank pin drives the orbiting scroll via the unloading bushing, and the centroid adjuster further comprises a mounting portion in the shape of a ring, by which the centroid adjuster is fixed to the unloading bushing such that a centrifugal force of the centroid adjuster can act on an inner side of the hub via the unloading bushing.

Optionally, the mass center adjuster is connected to the drive shaft.

Optionally, the mass centre adjusting member comprises a cylindrical portion arranged around the hub portion, at least a portion of the cylindrical portion contacting the outside of the hub portion such that centrifugal force of the mass centre adjusting member can act directly on the outside of the hub portion.

Optionally, a bearing is provided in the cylindrical portion, an inner side of the bearing contacting an outer side of the hub portion.

Optionally, the scroll compressor is a variable frequency scroll compressor.

In general, according to the scroll compressor of the present utility model, not only is the contact force between the scrolls reduced in a high rotational speed state, the frictional loss between the scrolls is reduced, the compressor operation noise is reduced, and the risk of scroll destruction is reduced; and the contact force between the fixed vortex and the movable vortex can be ensured to be at a proper level in a low rotation speed state, so that the radial seal between the vortices is ensured. In addition, the scroll compressor adjusts the contact force between the fixed scroll and the movable scroll in an electrodeless manner, and the adjustment is more sensitive and accurate, so that the performance of the compressor is improved.

Drawings

The features and advantages of one or more embodiments of the present utility model will become more readily appreciated from the following description, taken in conjunction with the accompanying drawings, in which:

FIG. 1 is a partial longitudinal cross-sectional view of a scroll compressor according to a first embodiment of the present utility model;

FIG. 2 is a schematic perspective view of a center of mass adjuster and an unloader bushing in accordance with a first embodiment of the present utility model assembled together;

FIG. 3 is an exploded view of a mass center adjuster according to a first embodiment of the present utility model;

Fig. 4a is a perspective cross-sectional view of the mass center adjuster according to the first embodiment of the present utility model in a state in which the adjusting portion thereof is in the initial position;

Fig. 4b is a perspective cross-sectional view of the mass center adjuster according to the first embodiment of the present utility model in a state in which the adjusting portion thereof is at a balance position;

fig. 5a and 5b are side views of fig. 4a and 4b, respectively;

Fig. 6 is a schematic perspective view of a center of mass adjuster according to a second embodiment of the present utility model;

Fig. 7a is a perspective cross-sectional view of a center of mass adjuster according to a second embodiment of the present utility model in a state in which an adjusting portion thereof is in an initial position; and

Fig. 7b is a perspective cross-sectional view of a center of mass adjuster according to a second embodiment of the present utility model in a state in which an adjusting portion thereof is in a balanced position.

Detailed Description

Preferred embodiments of the present utility model will now be described in detail with reference to fig. 1 to 7 b. The following description is merely exemplary in nature and is in no way intended to limit the utility model, its application, or uses. Corresponding components or parts are denoted by the same reference numerals throughout the various views.

Fig. 1 shows a partial configuration of a scroll compressor according to the present utility model. As shown in fig. 1, a scroll compressor 100 according to a first embodiment of the present utility model generally includes a housing 10, a compression mechanism disposed in a cavity enclosed by the housing 10, a drive shaft 70 and a motor (not shown) for driving the compression mechanism, a main bearing housing 50 for supporting the drive shaft 70 and the compression mechanism, and the like. The compression mechanism is composed of an orbiting scroll 30 and a fixed scroll 20, wherein the orbiting scroll 30 includes an orbiting scroll end plate 31, a spiral orbiting scroll blade 32 formed on one side of the orbiting scroll end plate 31, and a boss 33 formed on the other side of the orbiting scroll end plate 31. The fixed scroll 20 includes a fixed scroll end plate 21 and a spiral fixed scroll blade 22 formed on one side of the fixed scroll end plate 21. The fixed scroll 20 and the movable scroll 30 are engaged with each other, thereby forming a series of compression chambers between the fixed scroll blade 22 and the movable scroll blade 32, the volumes of which gradually decrease from the radially outer side to the radially inner side.

A portion of the drive shaft 70 is supported by a main bearing provided in the main bearing housing 50. The drive shaft 70 includes a main body portion 72 and an eccentric crank pin 71 formed at one end of the main body portion 72 in the direction of the rotational axis thereof. An eccentric crank pin 71 is fitted in the hub portion 33 of the orbiting scroll 30 to drive the orbiting scroll 30. A bushing is further provided between the eccentric crank pin 71 and the hub 33 of the orbiting scroll 30. In some embodiments, the liner is an unloading liner 40. The eccentric crank pin 71 is inserted into the fitting hole 42 in the center of the unloading bushing 40 so as to be fitted in the hub portion 33 of the orbiting scroll 30 via the unloading bushing 40 to drive the orbiting scroll 30. As shown in fig. 2, the eccentric crank pin 71 includes a planar portion (not shown) extending parallel to the rotational axis of the drive shaft 70, and the unloading bushing 40 includes a planar portion 41 (as shown in fig. 2, the fitting hole 42 has a substantially "D" shape) corresponding to the planar portion of the eccentric crank pin 71.

The main bearing housing 50 is provided with a thrust plate 52. One side of orbiting scroll 30 is supported by thrust plate 52. The driving shaft 70 is rotated by a motor, and the driving shaft 70 drives the orbiting scroll 30 through the eccentric crank pin 71, so that the orbiting scroll 30 orbits with respect to the non-orbiting scroll 20 (i.e., the central axis of the orbiting scroll 30 orbits the central axis of the non-orbiting scroll 20, but the orbiting scroll 30 itself does not orbit the central axis of itself) to achieve compression of a fluid. The above-mentioned orbiting is achieved by an oldham ring (not shown) provided between the fixed scroll 30 and the movable scroll 20.

In order to achieve axial sealing between the tip of the fixed scroll blade 22 and the movable scroll end plate 31 and between the tip of the movable scroll blade 32 and the fixed scroll end plate 21, a back pressure chamber 23 is generally provided on the side of the fixed scroll end plate 21 opposite to the fixed scroll blade 22. Since one side of the orbiting scroll 30 is supported by the main bearing housing 50 and the thrust plate 52, the non-orbiting scroll 20 and the orbiting scroll 30 can be effectively pressed together by the pressure in the back pressure chamber 23. When the pressure in the compression chambers between the orbiting and non-orbiting scrolls exceeds a set value, the resultant force generated by the pressures in these compression chambers will exceed the down-pressure provided in the back pressure chamber 23 to move the non-orbiting scroll 20 upward. At this time, the fluid in the compression chamber will leak to the low pressure side of the compressor through the gap between the tips of the non-orbiting scroll blade 22 and the orbiting scroll end plate 31 and the gap between the tips of the orbiting scroll blade 32 and the non-orbiting scroll end plate 21 to achieve unloading, thereby providing axial flexibility to the scroll compressor.

On the other hand, in order to achieve a radial seal between the side surface of the fixed scroll blade 22 and the side surface of the movable scroll blade 32 and to enable such a radial seal therebetween to be maintained at a proper value both in a high rotation speed condition and a low rotation speed condition, the scroll compressor 10 according to the first embodiment of the present utility model is further provided with a centroid adjuster 60. The centroid adjuster 60 is configured to be rotatable with the drive shaft 30 and centrifugal force (via the unloading bushing 40) generated by the centroid adjuster 60 due to rotation acts on the hub portion 33 of the orbiting scroll 30 at all times. The center of mass adjuster 60 and the orbiting scroll 30 form a centrifugal motion assembly CM. Preferably, the direction of the centrifugal force of the center of mass adjuster 60 may be set to be substantially opposite to the direction of the centrifugal force of the orbiting scroll 30. Thus, the center of mass adjuster 60 most effectively counteracts the centrifugal force of the orbiting scroll 30.

As shown in fig. 2, the centroid adjuster 60 includes a substantially circular arc-shaped main body portion 62 and a substantially annular mounting portion 64, the main body portion 62 extending beyond the mounting portion 64 in the axial direction. The mass center adjuster 60 is fixed to the unloading bushing 40 by a mounting portion 64 such that the centrifugal force of the mass center adjuster 60 can act on the inner side of the hub portion 33 via the unloading bushing 40. Specifically, as shown in fig. 3, the centroid adjuster 60 further includes an adjusting portion 65, and the main body portion 62 includes a recess 611 that opens outwardly in the radial direction of the scroll compressor to accommodate the adjusting portion 65 and guide the movement of the adjusting portion 65. Preferably, the shape and size of the adjustment portion 65 is adapted to the recess 611 of the main body portion 62 to facilitate installation and machining, to facilitate guiding movement of the adjustment portion 65, and to maximize the mass of the mass center adjuster 60 to increase the range of adjustment of the abutment force between the scrolls. Preferably, the recess 611 and the adjustment portion 65 are provided at intermediate positions of the main body portion 62 in the circumferential direction thereof, so that the adjustment portion 65 can more effectively adjust the centroid position of the centroid adjuster 60 and the centrifugal force generated by the centroid adjuster 60. The main body 62 and the adjusting portion 65 are connected to each other by an elastic member 63, and the elastic member 63 is, for example, a spring. More specifically, referring to fig. 4a, the adjustment portion 65 includes a channel 651 extending in a radial direction of the scroll compressor and penetrating the adjustment portion 65, the channel 651 being configured, for example, to have a circular cross-section in a direction perpendicular to a direction in which it extends (i.e., a radial direction of the scroll compressor) to at least partially accommodate the elastic member 63. The channel 651 is formed at an outer end in the radial direction with a first fixing portion 652, and the first fixing portion 652 may be formed as a rod-shaped portion crossing a circular cross section of the channel 651. Preferably, as shown in fig. 3, the stem is centrally located in the radially outer port of the channel 651 and extends across the entire radially outer port of the channel 651 in an axial direction, thereby facilitating centered installation of the spring, saving assembly space and ease of machining. Referring to fig. 4b, the recess 611 of the main body portion 62 is formed with an aperture 613 corresponding to the channel 651 at an inner end side (i.e., a side wall at a radially inner side of the recess 611) in the radial direction of the compressor, the aperture 613 being configured to be aligned with a radially inner port of the channel 651, and may also have the same shape as a circular cross section of the channel 651. The concave portion 611 of the main body portion 62 is also formed with a second fixing portion 612 at the inner end side in the radial direction of the compressor (i.e., at the position of the orifice 613). The second fixation portion 612 may be formed as a rod-shaped portion of circular cross-section across the aperture 613. Preferably, the stem is located centrally of the aperture 613 and extends across the entire aperture 613 in the axial direction, thereby facilitating a centrally mounted spring, saving assembly space and ease of machining. Preferably, both ends of the elastic member 63 are formed with hooks, respectively, in which the hooks at one end are connected to (hooked on) the first fixing member 652 and the hooks at the other end pass through the radially inner port of the channel 651 and are connected to (hooked on) the second fixing member 612. The elastic member assembled in this way can be at least partially accommodated in the channel at all times, thereby avoiding stretching and compression of the elastic member deviating from the radial direction, and the assembly is simple and convenient and saves space.

The process of adaptively adjusting the radial sealing force between the scrolls by the mass center adjuster 60 according to the rotational speed of the drive shaft 70 will be described with reference to fig. 4a, 4b, 5a and 5 b. When the driving shaft 70 drives the orbiting scroll 30 through the eccentric crank pin 71 and the unloading bushing 40, the centroid adjuster 60 rotates in synchronization with the unloading bushing 40 by being fixed to the unloading bushing 40. The centrifugal force generated by the mass center adjuster 60 will be transmitted to the hub portion 33 of the orbiting scroll 30 through the unloading bushing 40. Since the centroid of the centroid adjusting member 60 and the centroid of the orbiting scroll 30 are located on both sides of the rotational axis of the driving shaft 70 and are close in the axial direction, the centroid adjusting member 60 is assembled such that the direction of the centrifugal force thereof is substantially opposite to the centrifugal force direction of the orbiting scroll 30, and thus the centrifugal force of the centroid adjusting member 60 can cancel at least a portion of the centrifugal force of the orbiting scroll 30.

Specifically, the contact force between the fixed scroll 20 and the movable scroll 30 of the scroll compressor 100 according to the first embodiment of the present utility model can be expressed by the following formula:

F=m×r×w ²-m*r*w² formula (1)

Wherein F is the contact force between the fixed scroll 20 and the movable scroll 30;

M is the mass of orbiting scroll 30;

m is the mass of the mass center adjuster 60 and the unloader bushing 40;

R is the radius of gyration of orbiting scroll 30 about drive shaft 70;

r is the radius of gyration of the centroid adjuster 60 and the unloader bushing 40; and

Ω is the rotational speed of the drive shaft 70.

Since the adjustment portion 65 of the center of mass adjustment member 60 is interconnected with the main body portion 62 by the elastic member 63, it is possible to move in the radial direction of the scroll compressor with respect to the main body portion 62 as the rotational speed of the drive shaft 70 changes, so that the center of mass of the centrifugal motion assembly CM as a whole changes in the radial direction of the scroll compressor as the rotational speed of the drive shaft 70 changes. Specifically, the mass and position of the adjustment portion 65 and the preload of the elastic member 63 are set to: in the case where the rotation speed is less than or equal to the preset rotation speed, the adjusting portion 65 is maintained at its initial position. In this initial position, the adjustment portion 65 is fully accommodated in the recess 611 of the main body portion 62 so as to form a smooth outer contour of the main body portion 62. Preferably, in this initial position, the radially inner side port of the channel 651 of the adjustment portion 65 is in close contact with the aperture 613 at the radially inner side of the recess 611 of the main body portion 62 (i.e., the side wall at the radially inner side of the recess 611) (as shown in fig. 4a and 5 a), the elastic member 63 is almost completely accommodated in the channel 651 (i.e., the rest is accommodated in the channel 651 except for the hooks at both ends of the elastic member 63), thereby fully utilizing the installation space and increasing the stroke range of the adjustment portion 65 as much as possible.

When the rotational speed increases beyond the preset rotational speed, the adjusting portion 65 moves from the initial position in the radial direction toward the direction away from the main body portion 62 (i.e., toward the radially outer side), thereby further stretching the elastic member 63 until the adjusting portion 65 moves to an equilibrium position where the centrifugal force generated by the adjusting portion 65 is equal to the elastic force of the elastic member 63 (as shown in fig. 4b and 5 b); when the rotation speed is changed within a range greater than the preset rotation speed, the adjusting portion 65 is moved in the radial direction from the front balance position until the adjusting portion 65 is moved to a new balance position where the centrifugal force generated by the adjusting portion 65 is equal to the elastic force of the elastic member 63; then, when the rotational speed gradually decreases below the preset rotational speed (equal to or smaller than the preset rotational speed), the adjusting portion 65 moves from the front equilibrium position in the radial direction toward the initial position (i.e., toward the radially inner side) until the initial position. It will be appreciated that the greater the rotational speed, the greater the centrifugal force generated by the adjustment portion 65 and therefore the further the equilibrium position of the corresponding adjustment portion 65 is from the main body portion 62, the greater the radially outward movement of the centroid adjuster 60 and the unloader bushing 40 as a whole, i.e., the greater the radius of gyration of the centroids of the centroid adjuster 60 and the unloader bushing 40. According to the above formula (1), in the case where the compressor is operated at a high rotational speed, the centrifugal force of the orbiting scroll increases sharply, and the increase of the radius of gyration of the centroid adjusting part 60 and the unloading bushing 40 enables the centrifugal force of the orbiting scroll to be effectively offset by using the centroid adjusting part, thereby reducing the contact force between the fixed scroll and the orbiting scroll, reducing the operation noise, reducing the friction between the scrolls, and improving the performance of the compressor and reducing the risk of the damage of the scrolls. In the case of the compressor running at a low rotational speed, the centrifugal force of the orbiting scroll is reduced, and the centroid of the centroid adjuster 60 and the unloading bushing 40 as a whole moves radially inward, the reduction in the radius of gyration of the centroid adjuster 60 and the unloading bushing 40 allows the contact force between the fixed scroll and the orbiting scroll to be maintained at an appropriate level, effectively ensuring radial sealing between the scrolls.

In particular, in the related art, a weight whose center of mass is not adjustable may be employed to balance the centrifugal force or centrifugal moment of the orbiting scroll. In order to ensure the sealing requirement between the movable vortex and the fixed vortex at low rotation speed, only a balance block with smaller mass can be selected. Since the radial contact force between the scrolls and the square of the rotational speed are known to be linear, a weight of smaller mass still results in a higher radial contact force between the scrolls at high rotational speeds, resulting in a scroll compressor that has low performance at high speeds, while the scroll compressor requires a scroll of higher strength to be designed to counter the risk of failure. In contrast, the centroid of the centrifugal motion assembly comprising the centroid adjusting piece can change along with the change of the rotating speed of the compressor, so that the radial contact force between the movable vortex and the fixed vortex can be directly adjusted according to the change of the rotating speed, and the contact force between the vortices of the compressor at different rotating speeds is ensured to be kept within a reasonable interval.

In particular, in the related art, the weight is fixed to the rotation shaft without continuous contact with the orbiting scroll, or the weight is fixed to the rotation shaft with a large distance in the axial direction from the centroid of the weight and the centroid of the orbiting scroll (thereby allowing a counter moment to be formed), and therefore, even if the weight also has an adjustment portion, the weight in the related art cannot steplessly adjust the contact force between scrolls with a change in rotation speed since the weight cannot effectively act the centrifugal force generated by the weight on the hub of the orbiting scroll at most rotation speeds. In contrast, the centrifugal force generated by the rotation of the centroid adjusting member according to the present utility model always acts on the hub portion of the orbiting scroll, so that the contact force between the scrolls can be adjusted steplessly with the change of the rotational speed.

Preferably, in order to avoid complete disengagement of the adjustment portion 65 from the recess 611 of the main body portion 62 and failure to maintain the reciprocating movement in the radial direction, a limit member may be provided on the main body portion 62 and/or the adjustment portion 65. For example, the radially inner end of the adjustment portion 65 and the radially outer end of the main body 62 are provided with mutually engaging snaps, so as to limit the limit position at which the adjustment portion 65 moves radially outward.

Preferably, the length of the portion of the main body portion 62 surrounding the concave portion 611 in the radial direction is greater than the length of the other portions of the main body portion 62 in the radial direction. For example, as shown in fig. 3, the main body portion 62 includes, in the axial direction of the scroll compressor 100, a recess-provided portion 61 in which the recess 611 is provided and other portions in which the recess 611 is not provided, the length of the recess-provided portion 61 in the radial direction being longer than the length of the other portions in the radial direction. Thereby, the range of travel of the adjustment portion 65 in the recess 611 in the radial direction is larger, so that the adjustment range of the contact force between the scrolls can be increased.

Fig. 6 shows a centroid adjuster 60a according to a second embodiment of the utility model. The main structure and operation principle of the compressor mounted with the center of mass adjuster 60a are the same as those of the first embodiment of the present utility model, and will not be described again.

The centroid adjuster 60a is configured to be rotatable with the drive shaft and centrifugal force generated by the centroid adjuster 60a due to rotation always acts on the hub portion of the orbiting scroll. As shown in fig. 6, the centroid adjuster 60a includes a main body portion 62a having a substantially circular arc shape and an adjusting portion 65a movable in the radial direction of the scroll compressor with respect to the main body portion 62a as the rotational speed of the drive shaft changes. As shown in fig. 7a and 7b, the main body 62a and the adjusting portion 65a are connected to each other by an elastic member 63 a. The specific structure and positional connection relation of the main body portion 62a, the adjusting portion 65a and the elastic member 63 are similar to those of the first embodiment of the present utility model, and thus will not be described again.

Unlike the first embodiment of the present utility model, as shown in fig. 6, the centroid adjuster 60a includes a cylindrical portion 64a, the cylindrical portion 64a is provided so as to surround the hub portion 33 of the orbiting scroll 30, and the main body portion 62a is extended so as to protrude from a part of the outer peripheral wall of the cylindrical portion 64 a. A bearing 66a is provided in the cylindrical portion 64a of the centroid adjuster 60a, and an inner side of the bearing 66a contacts an outer side of the hub portion 33. The bearing 66a may be a rolling or sliding bearing or any other suitable bearing. Bearing 66a facilitates the transfer of force between centroid adjuster 60a and hub 33 of orbiting scroll 30 and reduces wear therebetween. However, those skilled in the art will appreciate that the bearing 66a may be omitted so long as at least a portion of the cylindrical portion 64a of the mass center adjuster 60a contacts the outside of the hub 33 so that the centrifugal force of the mass center adjuster 60a can directly act on the outside of the hub 33.

Further, the mass center adjuster 60a may be connected to the driving shaft 70 such that the mass center adjuster 60 rotates with the rotation of the driving shaft 70. In some embodiments, the mass center adjuster 60a is connected to a portion (shoulder) of the body portion 72 of the drive shaft 70 adjacent to the eccentric crankpin 71.

The process of adaptively adjusting the radial sealing force between the scrolls by the mass adjusting member 60a according to the rotational speed of the drive shaft 70 will be described with reference to fig. 7a and 7 b. When the driving shaft 70 drives the orbiting scroll 30 through the eccentric crank pin 71 and the unloading bushing 40, the centroid adjuster 60a rotates in synchronization with the driving shaft 70 due to the connection to the driving shaft 70. Centrifugal force generated by mass center adjuster 60a will be transferred to hub 33 of orbiting scroll 30 through cylindrical portion 64a (or bearing 66 a). Since the centroid of the centroid adjuster 60a and the centroid of the orbiting scroll 30 are located on both sides of the rotational axis of the drive shaft 70, the centroid adjuster 60a is assembled such that the direction of the centrifugal force thereof is substantially opposite to the direction of the centrifugal force of the orbiting scroll 30, and thus the centrifugal force of the centroid adjuster 60a can cancel at least a portion of the centrifugal force of the orbiting scroll 30.

Since the adjustment portion 65a of the center of mass adjustment member 60a is connected to the main body portion 62a via the elastic member 63a, it is possible to move in the radial direction of the scroll compressor with respect to the main body portion 62a as the rotational speed of the drive shaft 70 changes. When the rotational speed increases beyond the preset rotational speed, the adjustment portion 65a moves from the initial position (as shown in fig. 7 a) in the radial direction toward the direction away from the main body portion 62a (i.e., toward the radial outside), thereby stretching the elastic member 63a until the adjustment portion 65a moves to an equilibrium position (as shown in fig. 7 b) where the centrifugal force generated by the adjustment portion 65a is equal to the elastic force of the elastic member 63 a; when the rotation speed is changed within a range greater than the preset rotation speed, the adjusting portion 65a is moved in the radial direction from the front balance position until the adjusting portion 65a is moved to a new balance position where the centrifugal force generated by the adjusting portion 65a is equal to the elastic force of the elastic member 63 a; when the rotation speed decreases below the preset rotation speed, the adjusting portion 65a moves from the front equilibrium position toward the initial position (i.e., toward the radially inner side) in the radial direction until returning to the initial position.

Compared with the first embodiment of the utility model, the centroid adjusting piece disclosed by the second embodiment of the utility model not only can effectively offset the centrifugal force of the movable vortex under the condition that the compressor runs at a high rotating speed, thereby reducing the contact force between the fixed vortex and the movable vortex, reducing the running noise, reducing the friction between the vortices, improving the performance of the compressor and reducing the risk of vortex damage; under the condition that the compressor runs at a low rotating speed, the contact force between the fixed scroll and the movable scroll is allowed to be kept at a proper level, radial sealing between the scrolls is effectively ensured, and the centrifugal force generated by the mass center adjusting piece can be more effectively transmitted to the hub of the movable scroll due to the fact that the mass center adjusting piece is in direct contact with the hub of the movable scroll, so that the contact force between the fixed scroll and the movable scroll is more effectively adjusted.

A centroid adjuster for a scroll compressor and a scroll compressor including the centroid adjuster according to a preferred embodiment of the present utility model are described above in connection with the specific embodiments. It will be understood that the above description is by way of example only and not by way of limitation, and that various modifications and alterations will occur to those skilled in the art in light of the above description without departing from the scope of the utility model. Such variations and modifications are intended to be included within the scope of the present utility model.

Claims (14)

1. A scroll compressor, comprising:

The fixed vortex comprises a fixed vortex end plate and a fixed vortex blade formed on one side of the fixed vortex end plate;

The centrifugal motion assembly comprises an movable vortex and a mass center adjusting piece, wherein the movable vortex comprises a movable vortex end plate, movable vortex blades formed on one side of the movable vortex end plate and a hub part formed on the other side of the movable vortex end plate; and

A drive shaft including an eccentric crank pin fitted in the hub to drive the orbiting scroll to orbit relative to the fixed scroll to generate centrifugal force,

Wherein the mass center adjusting member is configured to rotate with the driving shaft, a centrifugal force generated by the rotation of the mass center adjusting member always acts on the hub portion of the movable scroll, the direction of the centrifugal force generated by the mass center adjusting member is substantially opposite to that of the centrifugal force generated by the movable scroll, and

Wherein the centroid adjusting member includes a main body portion and an adjusting portion that is movable in a radial direction of the scroll compressor with respect to the main body portion as a rotational speed of the drive shaft changes, so that a centroid of the centrifugal motion assembly changes in the radial direction of the scroll compressor as the rotational speed of the drive shaft changes.

2. The scroll compressor of claim 1, wherein the main body portion and the adjustment portion are interconnected by an elastic member, the mass and position of the adjustment portion and the preload of the elastic member being set to: the adjusting portion is maintained at an initial position in a case where the rotational speed is less than or equal to a preset rotational speed.

3. The scroll compressor of claim 2, wherein the mass and position of the adjustment portion and the preload of the resilient member are set to: when the rotational speed increases beyond the preset rotational speed, the adjustment portion moves from the initial position in a direction away from the main body portion until reaching a balance position where the centrifugal force generated by the adjustment portion is equal to the elastic force of the elastic member.

4. A scroll compressor as claimed in claim 3, wherein the mass and position of the adjustment portion and the preload of the resilient member are arranged to: and under the condition that the rotating speed gradually decreases to the preset rotating speed or less, the adjusting part moves towards the initial position until the initial position.

5. A scroll compressor as claimed in claim 4, wherein the main body portion and/or the adjustment portion is provided with a stop member to prevent the adjustment portion from being completely disengaged from the main body portion.

6. The scroll compressor of claim 2, wherein the main body portion includes a recess opening outwardly in the radial direction, the adjustment portion being fully received in the recess in the initial position.

7. The scroll compressor of claim 6, wherein the adjustment portion includes a channel extending in the radial direction, the resilient member being at least partially received in the channel.

8. The scroll compressor according to claim 7, wherein a first fixing portion is formed at an outer end of the channel in the radial direction, a second fixing portion is formed at an inner end of the recess in the radial direction, both ends of the elastic member are respectively formed with hooks, the hooks at one end of the elastic member are connected to the first fixing portion, and the hooks at the other end of the elastic member are connected to the second fixing portion.

9. The scroll compressor according to claim 6, wherein the main body portion includes a recess-provided portion provided with the recess and other portions not provided with the recess in an axial direction of the scroll compressor, a length of the recess-provided portion in the radial direction being greater than a length of the other portions in the radial direction.

10. The scroll compressor of any one of claims 1 to 9, further comprising an unloading bushing disposed between the eccentric crankpin and the hub such that the eccentric crankpin drives the orbiting scroll via the unloading bushing, the centroid adjuster further comprising a mounting portion in the shape of a ring by which the centroid adjuster is secured to the unloading bushing such that centrifugal force of the centroid adjuster can act on an inner side of the hub via the unloading bushing.

11. The scroll compressor of any one of claims 1 to 9, wherein the centroid adjuster is connected to the drive shaft.

12. The scroll compressor of claim 11, wherein the centroid adjuster comprises a cylindrical portion disposed about the hub, at least a portion of the cylindrical portion contacting an outer side of the hub such that centrifugal force of the centroid adjuster can act directly on the outer side of the hub.

13. The scroll compressor of claim 12, wherein a bearing is disposed in the cylindrical portion, an inner side of the bearing contacting an outer side of the hub.

14. The scroll compressor of any one of claims 1 to 9, wherein the scroll compressor is a variable frequency scroll compressor.