Scroll compressor

Abstract

The invention provides a scroll compressor. The scroll compressor comprises a fixed scroll; comprising an orbiting scroll and a centroid adjusting piece, and a driving shaft, the orbiting scroll comprises a hub part, the driving shaft comprises an eccentric crank pin which is matched in the hub part to drive the orbiting scroll to rotate relative to the fixed scroll to generate centrifugal force, and the centroid adjusting piece is configured to rotate along with the driving shaft. Centrifugal force generated by rotation of the driving shaft always acts on the hub part of the movable scroll, the direction of the centrifugal force is roughly opposite to that of the centrifugal force generated by the movable scroll, the mass center adjusting piece comprises a main body part and an adjusting part, and the adjusting part can move in the radial direction of the scroll compressor relative to the main body part along with the change of the rotating speed of the driving shaft; and the mass center of the centrifugal motion assembly changes along with the rotating speed of the driving shaft. According to the scroll compressor, the contact force between the vortexes can be kept within a reasonable interval at different rotating speeds, friction between the vortexes is reduced, noise is lowered, and energy efficiency is improved.

Description

Technical Field

[0001] The present invention relates to the field of compressors, in particular to a centrifugal motion component for a scroll compressor, and more particularly to a centrifugal motion component for a variable frequency scroll compressor. Background Art

[0002] This section provides background information related to the present disclosure which does not necessarily constitute prior art.

[0003] A scroll compressor generally includes a compression mechanism consisting of a fixed scroll and a movable scroll, which mesh with each other to form a series of chambers for compressing the working fluid. Driven by the eccentric component, the movable scroll translates relative to the fixed scroll, thereby compressing the fluid in the chamber. In order to achieve fluid compression, an effective radial seal must be formed between the fixed scroll and the movable scroll, that is, a certain radial contact force needs to be maintained between the fixed scroll and the movable scroll. On the other hand, the movable scroll will generate centrifugal force during its orbit relative to the fixed scroll, which will have a direct impact on the radial contact force between the scrolls.

[0004] When a scroll compressor, especially a variable frequency scroll compressor, runs at high speed, the centrifugal force generated by the movable scroll increases sharply, causing the radial contact force between the movable scroll and the fixed scroll to increase sharply. At this time, the risk of damage to the scroll is very high, and the noise of the compressor operation will also increase. When the scroll compressor runs at a low speed, the centrifugal force generated by the movable scroll decreases, but there needs to be a certain contact force between the movable scroll and the fixed scroll to achieve a radial seal between the two.

[0005] In addition, during the operation of the scroll compressor, the centrifugal force or centrifugal torque generated by the rotation of the eccentric component will cause the vibration of the compressor. Usually, a balancing block is set on the rotating component, such as the upper end of the drive shaft, to provide a reverse centrifugal force or centrifugal torque to balance the imbalance generated by the eccentric component. Obviously, the centrifugal force provided by the balancing block and the centrifugal force generated by the movable scroll constitute a reverse torque, thereby affecting the radial contact force between the movable scroll and the fixed scroll to a certain extent. Therefore, for variable frequency compressors, it is often difficult to select a balancing block of suitable quality, and the balancing block cannot effectively adjust the radial contact force between the movable scroll and the fixed scroll.

[0006] Therefore, it is necessary to provide an improved center of mass adjustment part and a scroll compressor including the center of mass adjustment part, so as to balance the radial contact force between the movable scroll and the fixed scroll of the scroll compressor under high speed and low speed states, ensure that the scroll compressor has good radial sealing under all speed states, reduce the friction loss between the movable scroll and the fixed scroll, reduce the operating noise of the compressor, and have lower design strength requirements for the scroll. Summary of the invention

[0007] This section provides a general summary of the invention, and is not a comprehensive disclosure of its full scope or all of its features.

[0008] The object of the present invention is to provide a scroll compressor equipped with a centrifugal motion component whose center of mass is adjusted with the rotational speed of the scroll compressor, the centrifugal motion component includes a center of mass adjustment part, so as to ensure that the contact force between the scrolls of the compressor at different rotational speeds remains within a reasonable range.

[0009] Another object of the present invention is to provide a scroll compressor equipped with a centrifugal motion component whose center of mass is adjusted with the rotational speed of the scroll compressor, the centrifugal motion component including a center of mass adjustment member to achieve stepless adjustment of the contact force between the scrolls of the compressor.

[0010] According to one aspect of the present invention, a scroll compressor is provided, comprising: a fixed scroll, the fixed scroll comprising a fixed scroll end plate and a fixed scroll blade formed on one side of the fixed scroll end plate; a centrifugal motion component, the centrifugal motion component comprising a movable scroll and a center of mass adjustment member, wherein the movable scroll comprises a movable scroll end plate, a movable scroll blade formed on one side of the movable scroll end plate and a hub formed on the other side of the movable scroll end plate; and a drive shaft, the drive shaft comprising an eccentric crank pin, the eccentric crank pin engaged in the hub to drive the movable scroll to orbit relative to the fixed scroll to generate centrifugal force, wherein the center of mass adjustment member is configured to rotate with the drive shaft, the centrifugal force generated by the rotation of the center of mass adjustment member always acts on the hub of the movable scroll, the direction of the centrifugal force generated by the center of mass adjustment member is substantially opposite to the direction of the centrifugal force generated by the movable scroll, and wherein the center of mass adjustment member comprises a main body and an adjustment member, the adjustment member can move relative to the main body in the radial direction of the scroll compressor as the rotation speed of the drive shaft changes, so that the center of mass of the centrifugal motion component changes in the radial direction of the scroll compressor as the rotation speed of the drive shaft changes.

[0011] Optionally, the main body and the adjustment part are connected to each other via an elastic member, and the mass and position of the adjustment part and the preload force of the elastic member are configured such that when the rotation speed is less than or equal to a preset rotation speed, the adjustment part remains in an initial position.

[0012] Optionally, the mass and position of the adjustment part and the preload force of the elastic member are configured such that when the rotation speed increases to exceed a preset rotation speed, the adjustment part moves from an initial position in a direction away from the main body until reaching a balance position where the centrifugal force generated by the adjustment part is equal to the elastic force of the elastic member.

[0013] Optionally, the mass and position of the adjustment part and the preload force of the elastic member are configured such that when the rotation speed gradually decreases to a preset rotation speed or less than a preset rotation speed, the adjustment part moves toward the initial position until the initial position.

[0014] Optionally, a limiting member is provided on the main body and / or the adjusting portion to prevent the adjusting portion from being completely separated from the main body.

[0015] Optionally, the main body portion includes a recessed portion opened outwardly in the radial direction, and the adjusting portion is completely accommodated in the recessed portion in the initial position.

[0016] Optionally, the adjusting portion includes a groove extending along the radial direction, and the elastic member is at least partially accommodated in the groove.

[0017] Optionally, a first fixing portion is formed at the outer end of the groove in the radial direction, a second fixing portion is formed at the inner end of the recess in the radial direction, hook-shaped members are respectively formed at both ends of the elastic member, the hook-shaped member at one end of the elastic member is connected to the first fixing portion, and the hook-shaped member at the other end of the elastic member is connected to the second fixing portion.

[0018] Optionally, the main body includes a recessed portion provided with a recess and other portions not provided with a recess in the axial direction of the scroll compressor, and the length of the recessed portion in the radial direction is greater than the length of the other portions in the radial direction.

[0019] Optionally, the scroll compressor also includes an unloading bushing arranged between the eccentric crank pin and the hub, so that the eccentric crank pin drives the movable scroll via the unloading bushing, and the center of mass adjustment member also includes an annular mounting portion, and the center of mass adjustment member is fixed to the unloading bushing via the mounting portion, so that the centrifugal force of the center of mass adjustment member can act on the inner side of the hub via the unloading bushing.

[0020] Optionally, a center of mass adjustment member is connected to the drive shaft.

[0021] Optionally, the center of mass adjusting member includes a cylindrical portion, the cylindrical portion is arranged to surround the hub, and at least a portion of the cylindrical portion contacts the outer side of the hub, so that the centrifugal force of the center of mass adjusting member can directly act on the outer side of the hub.

[0022] Optionally, a bearing is disposed in the cylindrical portion, and an inner side of the bearing contacts an outer side of the hub portion.

[0023] Optionally, the scroll compressor is a variable frequency scroll compressor.

[0024] In general, the scroll compressor according to the present invention not only reduces the contact force between the scrolls at high speed, reduces the friction loss between the scrolls, reduces the noise of the compressor operation, and reduces the risk of scroll damage; but also can ensure that the contact force between the fixed scroll and the movable scroll is at an appropriate level at low speed, thereby ensuring the radial seal between the scrolls. In addition, the scroll compressor according to the present invention adjusts the contact force between the fixed scroll and the movable scroll in a stepless manner, and the adjustment is more sensitive and accurate, thereby improving the performance of the compressor. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] The features and advantages of one or more embodiments of the present invention will become more easily understood through the following description with reference to the accompanying drawings, in which:

[0026] Figure 1 is a partial longitudinal sectional view of a scroll compressor according to a first embodiment of the present invention;

[0027] Figure 2 is a three-dimensional schematic diagram of a mass center adjusting member and an unloading bushing assembled together according to a first embodiment of the present invention;

[0028] Figure 3 is an exploded view of a mass center adjustment member according to a first embodiment of the present invention;

[0029] Figure 4a is a three-dimensional cross-sectional view of a mass center adjustment member according to a first embodiment of the present invention, with its adjustment portion being in an initial position;

[0030] Figure 4b is a three-dimensional cross-sectional view of a mass center adjustment member according to a first embodiment of the present invention, with its adjustment portion being in a balanced position;

[0031] Figure 5a and Figure 5b They are Figure 4a and Figure 4b Side view of

[0032] Figure 6 is a perspective schematic diagram of a center of mass adjustment member according to a second embodiment of the present invention;

[0033] Figure 7a is a three-dimensional cross-sectional view of a mass center adjustment member according to a second embodiment of the present invention, with its adjustment portion being in an initial position; and

[0034] Figure 7b 4 is a three-dimensional cross-sectional view of a mass center adjusting member according to a second embodiment of the present invention, in a state where an adjusting portion thereof is in a balanced position. DETAILED DESCRIPTION

[0035] Now we will combine the Figures 1 to 7b The preferred embodiments of the present invention are described in detail. The following description is merely exemplary in nature and is not intended to limit the present invention and its application or use. In each view, corresponding components or parts are marked with the same reference numerals.

[0036] Figure 1 FIG. 2 shows a partial structure of a scroll compressor according to the present invention. Figure 1As shown, the scroll compressor 100 according to the first embodiment of the present invention generally includes a housing 10, a compression mechanism arranged in a cavity enclosed by the housing 10, a drive shaft 70 and a motor (not shown) for driving the compression mechanism, and a main bearing seat 50 for supporting the drive shaft 70 and the compression mechanism. Among them, the compression mechanism is composed of a movable scroll 30 and a fixed scroll 20, and the movable scroll 30 includes a movable scroll end plate 31, a spiral movable scroll blade 32 formed on one side of the movable scroll end plate 31, and a hub 33 formed on the other side of the movable 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 meshed with each other, so that a series of compression chambers whose volumes gradually decrease from the radial outer side to the radial inner side are formed between the fixed scroll blade 22 and the movable scroll blade 32.

[0037] A portion of the drive shaft 70 is supported by a main bearing disposed in the main bearing seat 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 along its rotation axis direction. The eccentric crank pin 71 is engaged in the hub 33 of the movable scroll 30 to drive the movable scroll 30. A bushing is also provided between the eccentric crank pin 71 and the hub 33 of the movable scroll 30. In some embodiments, the bushing is an unloading bushing 40. The eccentric crank pin 71 is inserted into the assembly hole 42 in the center of the unloading bushing 40, thereby engaging in the hub 33 of the movable scroll 30 via the unloading bushing 40 to drive the movable scroll 30. As shown in FIG. Figure 2 As shown, the eccentric crank pin 71 includes a flat surface portion (not shown) extending parallel to the rotation axis of the drive shaft 70, and the unloading bushing 40 includes a flat surface portion 41 (as shown in FIG. 4 ) corresponding to the flat surface portion of the eccentric crank pin 71. Figure 2 As shown, the mounting hole 42 is generally "D" shaped).

[0038] A thrust plate 52 is provided on the main bearing seat 50. One side of the movable scroll 30 is supported by the thrust plate 52. The drive shaft 70 is driven to rotate by the motor, and the drive shaft 70 drives the movable scroll 30 through the eccentric crank pin 71, so that the movable scroll 30 revolves relative to the fixed scroll 20 (that is, the central axis of the movable scroll 30 rotates around the central axis of the fixed scroll 20, but the movable scroll 30 itself does not rotate around its own central axis) to achieve fluid compression. The above-mentioned revolving is achieved by a cross slip ring (not shown) provided between the fixed scroll 30 and the movable scroll 20.

[0039] In order to achieve axial sealing between the top of the fixed scroll blade 22 and the movable scroll end plate 31 and between the top of the movable scroll blade 32 and the fixed scroll end plate 21, a back pressure chamber 23 is usually provided on the side of the fixed scroll end plate 21 opposite to the fixed scroll blade 22. Since one side of the movable scroll 30 is supported by the main bearing seat 50 and the thrust plate 52, the fixed scroll 20 and the movable scroll 30 can be effectively pressed together by the pressure in the back pressure chamber 23. When the pressure in the compression chamber between the movable scroll and the fixed scroll exceeds the set value, the resultant force generated by the pressure in these compression chambers will exceed the downward pressure provided in the back pressure chamber 23, so that the fixed scroll 20 moves 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 top of the fixed scroll blade 22 and the movable scroll end plate 31 and the gap between the top of the movable scroll blade 32 and the fixed scroll end plate 21 to achieve unloading, thereby providing axial flexibility for the scroll compressor.

[0040] On the other hand, in order to achieve radial sealing between the side surface of the fixed scroll blade 22 and the side surface of the movable scroll blade 32 and in order to enable such radial sealing between the two to maintain an appropriate value under both high-speed and low-speed conditions, the scroll compressor 10 according to the first embodiment of the present invention is further provided with a center of mass adjustment member 60. The center of mass adjustment member 60 is configured to be able to rotate with the drive shaft 30 and the centrifugal force (via the unloading bushing 40) generated by the rotation of the center of mass adjustment member 60 always acts on the hub 33 of the movable scroll 30. The center of mass adjustment member 60 and the movable scroll 30 constitute a centrifugal motion component CM. Preferably, the direction of the centrifugal force of the center of mass adjustment member 60 can be set to be substantially opposite to the direction of the centrifugal force of the movable scroll 30. Therefore, the center of mass adjustment member 60 can most effectively offset the centrifugal force of the movable scroll 30.

[0041] like Figure 2 As shown in FIG. 1 , the mass center adjusting member 60 includes a main body portion 62 that is generally arc-shaped and a mounting portion 64 that is generally annular, and the main body portion 62 extends beyond the mounting portion 64 in the axial direction. The mass center adjusting member 60 is fixed to the unloading bushing 40 through the mounting portion 64, so that the centrifugal force of the mass center adjusting member 60 can act on the inner side of the hub portion 33 via the unloading bushing 40. Specifically, as shown in FIG. Figure 3As shown, the center of mass adjustment member 60 also includes an adjustment portion 65, and the main body 62 includes a recessed portion 611 that opens outwardly along the radial direction of the scroll compressor to accommodate the adjustment portion 65 and guide the movement of the adjustment portion 65. Preferably, the shape and size of the adjustment portion 65 are adapted to the recessed portion 611 of the main body 62, so as to facilitate installation and processing, guide the movement of the adjustment portion 65, and maximize the mass of the center of mass adjustment member 60 to increase the adjustment range of the abutment force between the vortices. Preferably, the recessed portion 611 and the adjustment portion 65 are arranged at a middle position of the main body 62 in its circumferential direction, so that the adjustment portion 65 can more effectively adjust the center of mass position of the center of mass adjustment member 60 and the centrifugal force generated by the center of mass adjustment member 60. The main body 62 and the adjustment portion 65 are connected by an elastic member 63, and the elastic member 63 is, for example, a spring. More specifically, see Figure 4a The adjusting portion 65 includes a groove 651 extending along the radial direction of the scroll compressor and penetrating the adjusting portion 65. The groove 651 is, for example, configured to have a circular cross section in a direction perpendicular to its extending direction (i.e., the radial direction of the scroll compressor) to at least partially accommodate the elastic member 63. The groove 651 is formed with a first fixing portion 652 at the outer end in the radial direction. The first fixing portion 652 can be formed as a rod-shaped portion having a circular cross section across the groove 651. Preferably, as Figure 3 As shown, the rod-shaped portion is located at the center of the radial outer end of the groove 651 and extends in the axial direction across the radial outer end of the entire groove 651, thereby facilitating the central installation of the elastic member, saving assembly space and facilitating processing. Figure 4b , the recess 611 of the main body 62 is formed with an orifice 613 corresponding to the groove 651 at the inner end side in the radial direction of the compressor (i.e., the side wall at the radial inner side of the recess 611), and the orifice 613 is configured to align with the radial inner port of the groove 651, and can also have the same shape as the circular cross section of the groove 651. The recess 611 of the main body 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 fixing portion 612 can be formed as a rod-shaped portion with a circular cross section across the orifice 613. Preferably, the rod-shaped portion is located at the center of the orifice 613 and extends across the entire orifice 613 in the axial direction, so as to facilitate the central installation of the elastic member, save assembly space and facilitate processing. Preferably, hooks are formed at both ends of the elastic member 63, wherein the hook at one end is connected to (hooked on) the first fixing member 652, and the hook at the other end passes through the radial inner port of the channel 651 and is connected to (hooked on) the second fixing member 612. The elastic member assembled in this way can not only be always at least partially accommodated in the channel, thereby preventing the stretching and compression of the elastic member from deviating from the radial direction, but also is simple and convenient to assemble and saves space.

[0042] Refer to the following Figure 4a , Figure 4b , Figure 5a and Figure 5b The process of adaptively adjusting the radial sealing force between the vortices by the center of mass adjustment member 60 as the rotation speed of the drive shaft 70 changes is described. When the drive shaft 70 drives the movable scroll 30 through the eccentric crank pin 71 and the unloading bushing 40, the center of mass adjustment member 60 rotates synchronously with the unloading bushing 40 because it is fixed to the unloading bushing 40. The centrifugal force generated by the center of mass adjustment member 60 will be transmitted to the hub 33 of the movable scroll 30 through the unloading bushing 40. Since the center of mass of the center of mass adjustment member 60 and the center of mass of the movable scroll 30 are located on both sides of the rotation axis of the drive shaft 70 and are close in the axial direction, the center of mass adjustment member 60 is assembled so that the direction of its centrifugal force is roughly opposite to the direction of the centrifugal force of the movable scroll 30, so the centrifugal force of the center of mass adjustment member 60 can offset at least a part of the centrifugal force of the movable scroll 30.

[0043] 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 invention can be expressed by the following formula:

[0044] F=M*R*w 2 -m*r*w 2 Formula (1)

[0045] Wherein, F is the contact force between the fixed scroll 20 and the movable scroll 30;

[0046] M is the mass of the movable scroll 30;

[0047] m is the mass of the center of mass adjustment member 60 and the unloading bushing 40;

[0048] R is the radius of gyration of the movable scroll 30 around the drive shaft 70;

[0049] r is the radius of gyration of the center of mass of the center of mass adjustment member 60 and the unloading bushing 40; and

[0050] ω is the rotation speed of the drive shaft 70 .

[0051] Since the adjustment portion 65 of the center of mass adjustment member 60 is interconnected with the main body 62 through the elastic member 63, it can move in the radial direction of the scroll compressor relative to the main body 62 as the rotation 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 rotation speed of the drive shaft 70 changes. Specifically, the mass and position of the adjustment portion 65 and the preload force of the elastic member 63 are configured so that the adjustment portion 65 remains in its initial position when the rotation speed is less than or equal to the preset rotation speed. In this initial position, the adjustment portion 65 is completely accommodated in the recess 611 of the main body 62 to form a smooth outer contour of the main body 62. Preferably, in this initial position, the radial inner port of the groove 651 of the adjustment portion 65 is in close contact with the orifice 613 at the inner end side of the recess 611 of the main body 62 in the radial direction (i.e., the side wall at the radial inner side of the recess 611) (such as Figure 4a and Figure 5a As shown in the figure, the elastic member 63 is almost completely accommodated in the groove 651 (that is, except for the hook-shaped members at both ends of the elastic member 63, the rest are accommodated in the groove 651), thereby making full use of the installation space and maximizing the travel range of the adjustment part 65.

[0052] When the rotation speed increases to exceed the preset rotation speed, the adjusting portion 65 moves from the initial position in the radial direction toward the direction away from the main body 62 (i.e., toward the radial outside), thereby further stretching the elastic member 63 until the adjusting portion 65 moves to a balanced position (such as the position at which the centrifugal force generated by the adjusting portion 65 is equal to the elastic force of the elastic member 63). Figure 4b and Figure 5bAs shown); when the rotation speed changes within a range greater than the preset rotation speed, the adjustment portion 65 moves in the radial direction from the front equilibrium position until the adjustment portion 65 moves to a new equilibrium position where the centrifugal force generated by the adjustment portion 65 is equal to the elastic force of the elastic member 63; thereafter, when the rotation speed gradually decreases to below the preset rotation speed (equal to the preset rotation speed or less than the preset rotation speed), the adjustment portion 65 moves in the radial direction from the front equilibrium position toward the initial position (i.e., toward the radial inside) until the initial position. It can be understood that the greater the rotation speed, the greater the centrifugal force generated by the adjustment portion 65, and therefore the corresponding equilibrium position of the adjustment portion 65 is further away from the main body 62, and then the center of mass of the center of mass adjustment member 60 and the unloading bushing 40 as a whole moves radially outward, that is, the greater the rotation radius of the center of mass of the center of mass adjustment member 60 and the unloading bushing 40. According to the above formula (1), when the compressor is running at a high speed, the centrifugal force of the movable scroll increases sharply, and the increase in the rotation radius of the center of mass of the center of mass adjustment member 60 and the unloading bushing 40 enables the use of the center of mass adjustment member to effectively offset the centrifugal force of the movable scroll, thereby reducing the contact force between the fixed scroll and the movable scroll, reducing operating noise, reducing friction between the scrolls, and improving the performance of the compressor and reducing the risk of vortex damage. When the compressor is running at a low speed, the centrifugal force of the movable scroll is reduced, and the center of mass of the center of mass adjustment member 60 and the unloading bushing 40 as a whole moves radially inward. The reduction in the rotation radius of the center of mass of the center of mass adjustment member 60 and the unloading bushing 40 allows the contact force between the fixed scroll and the movable scroll to be maintained at an appropriate level, effectively ensuring the radial seal between the scrolls.

[0053] In particular, in the related art, a balancing block with an unadjustable center of mass can be used to balance the centrifugal force or centrifugal torque of the movable scroll. In order to ensure the sealing requirements between the movable scroll and the fixed scroll at low speed, usually only a balancing block with a smaller mass can be selected. Since it is known that there is a linear relationship between the radial contact force between the vortices and the square of the rotational speed, a balancing block with a smaller mass will still cause a higher radial contact force between the vortices at a high speed, resulting in poor performance of the scroll compressor when running at high speed. At the same time, the scroll compressor needs to design a stronger vortex to counter the risk of damage. In contrast, the center of mass of the centrifugal motion assembly including the center of mass adjustment member according to the present invention can change with the rotational speed of the compressor, so that the radial contact force between the movable scroll and the fixed scroll can be directly adjusted according to the change in rotational speed, ensuring that the contact force between the vortices of the compressor at different rotational speeds remains within a reasonable range.

[0054] In particular, in the related art, the balancing block is fixed to the rotating shaft and has no continuous contact with the movable scroll, or the balancing block is fixed to the rotating shaft and there is a large distance between the center of mass of the balancing block and the center of mass of the movable scroll in the axial direction (thereby allowing the formation of a reverse torque). Therefore, even if the balancing block also has an adjustment portion, since the balancing block cannot effectively act the centrifugal force generated by it on the hub of the movable scroll at most speeds, the balancing block in the related art cannot infinitely adjust the contact force between the vortices as the speed changes. In contrast, the centrifugal force generated by the rotation of the center of mass adjustment member according to the present invention always acts on the hub of the movable scroll, so the contact force between the vortices can be infinitely adjusted as the speed changes.

[0055] Preferably, in order to prevent the adjusting portion 65 from being completely separated from the recess 611 of the main body 62 and unable to maintain the reciprocating motion in the radial direction, a limiting member may be provided on the main body 62 and / or the adjusting portion 65. For example, mutually matching buckles may be provided at the radial inner end of the adjusting portion 65 and the radial outer end of the main body 62, thereby limiting the limit position of the adjusting portion 65 moving toward the radial outer side.

[0056] Preferably, the length of the portion of the main body 62 surrounding the recess 611 in the radial direction is greater than the length of the other portions of the main body 62 in the radial direction. Figure 3 As shown, the main body 62 includes a recessed portion 61 provided with a recessed portion 611 and other portions not provided with the recessed portion 611 in the axial direction of the scroll compressor 100, and the length of the recessed portion 61 in the radial direction is greater than the length of the other portions in the radial direction. As a result, the adjustment portion 65 has a larger travel range in the recessed portion 611 along the radial direction, thereby increasing the adjustment range of the contact force between the scrolls.

[0057] Figure 6 The center of mass adjustment member 60a according to the second embodiment of the present invention is shown. The main structure and working principle of the compressor equipped with the center of mass adjustment member 60a are the same as those of the first embodiment of the present invention, and will not be repeated here.

[0058] The centroid adjusting member 60a is configured to rotate with the drive shaft and the centrifugal force generated by the centroid adjusting member 60a due to the rotation always acts on the hub of the movable scroll. Figure 6 As shown, the mass center adjustment member 60a includes a main body portion 62a that is substantially arc-shaped and an adjustment portion 65a that can move relative to the main body portion 62a in the radial direction of the scroll compressor as the rotation speed of the drive shaft changes. Figure 7a , Figure 7bAs shown, the main body 62a and the adjusting part 65a are connected to each other through the elastic member 63a. The specific structure and position connection relationship of the main body 62a, the adjusting part 65a and the elastic member 63a are similar to those of the first embodiment of the present invention, so they are not repeated here.

[0059] Different from the first embodiment of the present invention, Figure 6 As shown, the center of mass adjustment member 60a includes a cylindrical portion 64a, the cylindrical portion 64a is arranged to surround the hub 33 of the movable scroll 30, and the main body 62a protrudes from a portion of the outer peripheral wall of the cylindrical portion 64a. A bearing 66a is provided in the cylindrical portion 64a of the center of mass adjustment member 60a, and the inner side of the bearing 66a contacts the outer side of the hub 33. The bearing 66a can be a rolling bearing or a sliding bearing or any other suitable bearing. The bearing 66a helps to transmit the force between the center of mass adjustment member 60a and the hub 33 of the movable scroll 30 and helps to reduce the wear between the two. However, it can be understood by those skilled in the art that the bearing 66a can also be omitted, as long as at least a portion of the cylindrical portion 64a of the center of mass adjustment member 60a contacts the outer side of the hub 33, so that the centrifugal force of the center of mass adjustment member 60a can directly act on the outer side of the hub 33.

[0060] Furthermore, the mass adjustment member 60a can be connected to the drive shaft 70 so that the mass adjustment member 60 rotates with the rotation of the drive shaft 70. In some embodiments, the mass adjustment member 60a is connected to the body portion 72 of the drive shaft 70 adjacent to the eccentric crank pin 71 (shoulder).

[0061] Refer to the following Figure 7a and Figure 7b The process of adaptively adjusting the radial sealing force between the vortices by the mass center adjustment member 60a as the rotation speed of the drive shaft 70 changes is described. When the drive shaft 70 drives the movable scroll 30 through the eccentric crank pin 71 and the unloading bushing 40, the mass center adjustment member 60a rotates synchronously with the drive shaft 70 due to being connected to the drive shaft 70. The centrifugal force generated by the mass center adjustment member 60a will be transmitted to the hub 33 of the movable scroll 30 through the cylindrical portion 64a (or the bearing 66a). Since the mass center of the mass center adjustment member 60a and the mass center of the movable scroll 30 are located on both sides of the rotation axis of the drive shaft 70, the mass center adjustment member 60a is assembled so that the direction of its centrifugal force is roughly opposite to the direction of the centrifugal force of the movable scroll 30, so the centrifugal force of the mass center adjustment member 60a can offset at least a part of the centrifugal force of the movable scroll 30.

[0062] Since the adjusting portion 65a of the mass center adjusting member 60a is connected to the main body 62a through the elastic member 63a, it can move relative to the main body 62a in the radial direction of the scroll compressor as the speed of the drive shaft 70 changes. Figure 7a As shown in FIG. 1 , the adjusting portion 65a moves in a direction away from the main body portion 62a in the radial direction (i.e., toward the radial outside), thereby stretching the elastic member 63a, until the adjusting portion 65a moves to a balanced position (as shown in FIG. 1 ) where the centrifugal force generated by the adjusting portion 65a is equal to the elastic force of the elastic member 63a. Figure 7b as shown); when the rotation speed changes within a range greater than a preset rotation speed, the adjusting portion 65a moves in the radial direction from the front equilibrium position until the adjusting portion 65a moves to a new equilibrium position where the centrifugal force generated by the adjusting portion 65a is equal to the elastic force of the elastic member 63a; when the rotation speed decreases to below the preset rotation speed, the adjusting portion 65a moves in the radial direction from the front equilibrium position toward the initial position (i.e., toward the radial inside) until it returns to the initial position.

[0063] Compared with the first embodiment of the present invention, the center of mass adjustment member shown in the second embodiment of the present invention can not only effectively offset the centrifugal force of the movable scroll when the compressor is running at a high speed, thereby reducing the contact force between the fixed scroll and the movable scroll, reducing operating noise, reducing friction between the scrolls, and improving compressor performance and reducing the risk of vortex damage; when the compressor is running at a low speed, the contact force between the fixed scroll and the movable scroll is allowed to be maintained at an appropriate level, effectively ensuring the radial seal between the scrolls, and because the center of mass adjustment member is in direct contact with the hub of the movable scroll, the centrifugal force generated by the center of mass adjustment member can be more effectively transmitted to the hub of the movable scroll, thereby more effectively adjusting the contact force between the fixed scroll and the movable scroll.

[0064] The above describes the center of mass adjustment member for a scroll compressor and the scroll compressor including the center of mass adjustment member according to the preferred embodiment of the present invention in combination with the specific embodiments. It is understood that the above description is only exemplary and not restrictive, and those skilled in the art can think of various variations and modifications with reference to the above description without departing from the scope of the present invention. These variations and modifications are also included in the protection scope of the present invention.

Claims

1. A scroll compressor (100), characterized in that: include: A fixed scroll (20), the fixed scroll comprising a fixed scroll end plate (21) and a fixed scroll blade (22) formed on one side of the fixed scroll end plate; A centrifugal motion assembly (CM), the centrifugal motion assembly comprising a movable scroll (30) and a mass center adjustment member (60, 60a), wherein the movable scroll comprises a movable scroll end plate (31), a movable scroll blade (32) formed on one side of the movable scroll end plate, and a hub (33) formed on the other side of the movable scroll end plate; and A drive shaft (70), the drive shaft comprising an eccentric crank pin (71), the eccentric crank pin being engaged in the hub to drive the movable scroll to orbit relative to the fixed scroll to generate centrifugal force, 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 of the movable 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 movable scroll, and Wherein, the center of mass adjustment member includes a main body portion (62, 62a) and an adjustment portion (65, 65a), and the adjustment portion can move relative to the main body portion in the radial direction of the scroll compressor as the rotational speed of the drive shaft changes, so that the center of mass of the centrifugal motion component changes in the radial direction of the scroll compressor as the rotational speed of the drive shaft changes.

2. The scroll compressor according to claim 1, wherein: The main body (62, 62a) and the adjustment part (65, 65a) are connected to each other via an elastic member (63, 63a), and the mass and position of the adjustment part and the preload force of the elastic member are configured such that when the rotation speed is less than or equal to a preset rotation speed, the adjustment part remains in an initial position.

3. The scroll compressor according to claim 2, wherein: The mass and position of the adjustment part and the preload force of the elastic member are configured such that, when the rotation speed increases to exceed the preset rotation speed, the adjustment part (65, 65a) moves from the initial position toward a direction away from the main body until reaching a balance position where the centrifugal force generated by the adjustment part is equal to the elastic force of the elastic member.

4. The scroll compressor according to claim 3, wherein: The mass and position of the adjustment part and the preload force of the elastic member are configured such that when the rotation speed gradually decreases to the preset rotation speed or less than the preset rotation speed, the adjustment part moves toward the initial position until the initial position.

5. The scroll compressor according to claim 4, wherein: The main body (62, 62a) and / or the adjustment part (65, 65a) are provided with a limiting component to prevent the adjustment part from completely separating from the main body.

6. The scroll compressor according to claim 2, wherein: The main body portion (62, 62a) includes a recessed portion (611) opened outwardly along the radial direction, and the adjustment portion is completely accommodated in the recessed portion in the initial position.

7. The scroll compressor according to claim 6, wherein: The adjusting portion (65, 65a) comprises a groove (651) extending along the radial direction, and the elastic member (63) is at least partially accommodated in the groove.

8. The scroll compressor according to claim 7, wherein: The groove (651) is formed with a first fixing portion (652) at the outer end in the radial direction, and the recess (611) is formed with a second fixing portion (612) at the inner end in the radial direction. Hook-shaped members are respectively formed at both ends of the elastic member, and the hook-shaped member at one end of the elastic member is connected to the first fixing portion, and the hook-shaped member at the other end of the elastic member is connected to the second fixing portion.

9. The scroll compressor according to claim 6, wherein: The main body (62, 62a) includes a recess setting portion (61) provided with the recess and other portions not provided with the recess in the axial direction of the scroll compressor, and the length of the recess setting portion in the radial direction is greater than the length of the other portions in the radial direction.

10. The scroll compressor according to any one of claims 1 to 9, wherein: The scroll compressor also includes an unloading bushing (40) arranged between the eccentric crank pin (71) and the hub (33), so that the eccentric crank pin (71) drives the movable scroll (30) via the unloading bushing (40), and the center of mass adjustment member (60) also includes an annular mounting portion (64), and the center of mass adjustment member (60) is fixed to the unloading bushing via the mounting portion, so that the centrifugal force of the center of mass adjustment member can act on the inner side of the hub via the unloading bushing.

11. The scroll compressor according to any one of claims 1 to 9, wherein: The center of mass adjustment member (60a) is connected to the drive shaft (70).

12. The scroll compressor according to claim 11, wherein: The center of mass adjustment member (60a) includes a cylindrical portion (64a) which is arranged to surround the hub portion (33), and at least a portion of the cylindrical portion contacts the outer side of the hub portion (33), so that the centrifugal force of the center of mass adjustment member can directly act on the outer side of the hub portion.

13. The scroll compressor according to claim 12, wherein: A bearing (66a) is disposed in the cylindrical portion (64a), and the inner side of the bearing contacts the outer side of the hub portion (33).

14. The scroll compressor according to any one of claims 1 to 9, wherein: The scroll compressor (100) is a variable frequency scroll compressor.

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