Scroll compressor

Abstract

A scroll compressor includes a motor, a compression mechanism, a drive shaft and a bushing. The compression mechanism includes a fixed scroll and an orbiting scroll. The drive shaft has an eccentric journal. The bushing is designed to be movable relative to the eccentric journal to enable the orbiting scroll to have a variable eccentricity, wherein one axial section of the bushing is arranged between the orbiting scroll and the eccentric journal to enable the drive shaft to transmit power to the orbiting scroll via the one axial section of the bushing, and another axial section of the bushing is designed to limit the range of movement of the bushing relative to the eccentric journal to further define the range of variation of the variable eccentricity of the orbiting scroll. The bushing with the above configuration cooperates with the corresponding structure to reliably and effectively limit the range of movement thereof to enable the orbiting scroll to have a proper variable eccentricity, which reduces the requirement for assembly accuracy of the scroll compressor and thereby reduces the cost of the compressor.

Description

Technical Field

[0001] This utility model relates to the field of compressors, and in particular to a through-shaft scroll compressor that can reduce the requirements for machining accuracy and assembly accuracy. Background Technology

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

[0003] Compressors (such as scroll compressors) can be used in, for example, refrigeration systems, air conditioning systems, and heat pump systems. A scroll compressor includes a compression mechanism for compressing a working fluid (such as a refrigerant), and this compression mechanism includes a moving scroll and a stationary scroll. During operation of the scroll compressor, a drive shaft drives the moving scroll to perform a circumferential motion relative to the stationary scroll. Specifically, in one type of scroll compressor, an eccentric journal is provided on the drive shaft, and the eccentric journal engages with the moving scroll. Those skilled in the art generally refer to a compressor in which the drive shaft extends through both the moving and stationary scrolls as a through-scroll compressor.

[0004] In existing technologies, the eccentricity of the moving scroll in a through-shaft scroll compressor is controlled solely by the fixed eccentricity of the eccentric journal. When the eccentricity of the eccentric journal is less than the eccentricity of the moving scroll, a radial leakage gap exists in the scroll profile, leading to a decrease in compressor performance. Conversely, when the eccentricity of the eccentric journal is greater than the eccentricity of the moving scroll, interference occurs in the scroll profile, causing reliability issues. The need for precise control of the scroll profile gap range necessitates high precision in component machining and compressor assembly, resulting in increased costs.

[0005] The above issues need to be resolved. Utility Model Content

[0006] This invention aims to solve at least one of the aforementioned technical problems. Specifically, one technical problem this invention aims to solve is to reduce the machining accuracy requirements of the components of a scroll compressor and to reduce the assembly accuracy requirements of the compressor, thereby reducing the manufacturing cost of the scroll compressor and improving its reliability. Another technical problem this invention aims to solve is to reduce the machining accuracy requirements of the components and the assembly accuracy requirements of a through-shaft scroll compressor (e.g., a through-shaft scroll compressor with a single compression mechanism). Yet another technical problem this invention aims to solve is to provide a reliable and effective range of motion limiting structure for components (especially bushings) that can reduce the machining accuracy requirements of the components and the assembly accuracy requirements of a through-shaft scroll compressor.

[0007] This invention provides a scroll compressor, including a motor, a compression mechanism, a drive shaft, and a bushing. The motor is designed to power the scroll compressor. The compression mechanism includes a stationary scroll and a moving scroll, the moving scroll engaging with the stationary scroll to define a compression chamber between the moving scroll and the stationary scroll. The drive shaft has a first central axis and extends along the first central axis through the stationary scroll and the moving scroll. One end of the drive shaft is connected to the motor so that the drive shaft can rotate about the first central axis under the drive of the motor. The drive shaft has an eccentric journal with a second central axis radially offset from the first central axis, the eccentric journal engaging with the moving scroll to drive the moving scroll's motion. The bushing is designed to move relative to the eccentric journal so that the moving scroll has a variable eccentricity. One axial section of the bushing is arranged between the moving scroll and the eccentric journal so that the power of the drive shaft can be transmitted to the moving scroll via one axial section of the bushing. Another axial section of the bushing is designed to limit the range of motion of the bushing relative to the eccentric journal to further limit the range of variation of the variable eccentricity of the moving scroll.

[0008] By ingeniously introducing radial flexibility into the scroll compressor, especially the through-shaft scroll compressor, the moving scroll exhibits variable eccentricity. This reduces the precision requirements for component machining and compressor assembly, lowers the manufacturing cost of the through-shaft scroll compressor, and further improves reliability. In particular, this invention provides a novel bushing, especially suitable for through-shaft scroll compressors. It offers reliable operation, fewer parts, a compact structure, and lower cost. It effectively introduces radial flexibility into the moving scroll and features a specially designed structure that reliably and effectively limits its range of motion, thereby enabling the moving scroll to have an appropriate variable eccentricity.

[0009] Preferably, the bushing is designed to rotate circumferentially relative to the eccentric journal, and another axial section of the bushing is designed to limit the range of circumferential rotation angle of the bushing relative to the eccentric journal.

[0010] Preferably, the scroll compressor includes a single compression mechanism.

[0011] Preferably, the compression mechanism is arranged axially below the motor, the moving scroll meshes with the fixed scroll axially below the fixed scroll, and the upper end of the drive shaft is connected to the motor.

[0012] Preferably, the scroll compressor further includes a bearing housing arranged axially below the compression mechanism, through which the drive shaft passes.

[0013] Preferably, the scroll compressor further includes an oil sump arranged axially below the bearing housing, with the lower end of the drive shaft extending into the oil sump.

[0014] Preferably, the bushing is configured to include a first cylindrical portion and a second cylindrical portion arranged axially adjacent to the first cylindrical portion, the first cylindrical portion being sleeved on the outer periphery of the eccentric journal, wherein the first cylindrical portion serves as one axial segment of the bushing and the second cylindrical portion serves as another axial segment of the bushing.

[0015] Preferably, the second cylindrical portion is arranged axially below the first cylindrical portion. Preferably, the inner peripheral wall of the first cylindrical portion defines a first circular through hole, the eccentric journal passes coaxially through the first circular through hole about the first circular through hole, and the outer peripheral wall of the first cylindrical portion extends about a third central axis that is radially offset about the second central axis.

[0016] Preferably, the inner peripheral wall of the second cylindrical portion defines a second circular through hole, and the section of the drive shaft located axially below the eccentric journal passes through the second circular through hole coaxially with respect to the second circular through hole, and the outer peripheral wall of the second cylindrical portion also extends around the first central axis.

[0017] Preferably, the upper end face of the bearing seat of the scroll compressor arranged axially below the compression mechanism is provided with an upwardly open receiving recess so that the second cylindrical part can be conformally seated in the receiving recess.

[0018] Preferably, the radial clearance between the first cylindrical portion and the eccentric journal is R1, and the radial clearance between the second cylindrical portion and the corresponding section of the drive shaft is R2, where R2 > 0. R2 is designed to allow the first cylindrical portion to rotate less than 180° relative to the eccentric journal.

[0019] By employing the aforementioned second cylindrical section, the circumferential rotation angle of the first cylindrical section is effectively controlled. This achieves effective control of the swing range of the swing bushing with a design that features fewer parts, a compact structure, and lower cost, thus preventing the swing bushing from swinging excessively and causing the compressor to malfunction.

[0020] Preferably, R2 > 10R1.

[0021] This design allows for a sufficiently large gap between the second cylindrical section and the drive shaft, ensuring that the swing bushing can achieve a sufficiently large swing range, that the moving vortex has sufficiently large radial flexibility, and that the profile of the moving vortex smoothly matches the profile of the stationary vortex. Attached Figure Description

[0022] The foregoing and other features and characteristics of this application will become clearer from the following detailed description with reference to the accompanying drawings, which are merely illustrative and not necessarily drawn to scale. The same reference numerals are used in the drawings to indicate the same parts, in which:

[0023] Figure 1 A cross-sectional schematic diagram of a first embodiment of a scroll compressor according to the present invention is shown.

[0024] Figure 2 It shows Figure 1 Enlarged view of the area within the dashed box.

[0025] Figure 3 It shows Figure 1 A sectional view taken along section line AA.

[0026] Figure 4 A perspective view of the first bushing in a first embodiment of a scroll compressor is shown.

[0027] Figure 5 A perspective view of the first cylindrical portion of the first bushing is shown, with the retaining ring omitted.

[0028] Figure 6 and Figure 7 The two extreme positions of the second cylindrical section relative to the drive shaft are schematically shown.

[0029] Figure 8 A partial view of a cross-sectional schematic diagram of a second embodiment of a scroll compressor according to the present invention is shown, in which the second bushing is fitted onto an eccentric journal.

[0030] Figure 9 It shows Figure 8 A sectional view taken along section line BB.

[0031] Figure 10 It shows Figure 9 Enlarged view of the area within the dashed box.

[0032] List of reference numerals

[0033] 100. Scroll compressor; 1. Motor; 11. Rotor; 12. Stator; CM. Compression mechanism; 2. Fixed scroll; 21. Fixed scroll end plate; 22. Fixed scroll; 3. Moving scroll; 31. Moving scroll end plate; 32. Moving scroll; 33. Drive connection part; 4. Drive shaft; 41. Eccentric journal; 411. Drive plane section; 42. Upper shaft end of drive shaft; 43. Lower shaft end of drive shaft; 5. Bearing housing; 51. Accommodating recess; 6. Oil sump; 7. First bushing; 71. First Cylindrical section; 711. First circular through hole; 712. Outer peripheral wall of the first cylindrical section; 72. Second cylindrical section; 721. Second circular through hole; 722. Outer peripheral wall of the second cylindrical section; 73. Retaining ring; 731. Oil guide groove; 8. Second bushing; 81. Main body; 82. D-shaped through hole; 9. Outer shell; 91. Housing; 92. Top cover; 93. Bottom cover; L. Axial direction; R. Radial direction; L1. First central axis; L2. Second central axis; L3. Third central axis; M. Filter screen. Detailed Implementation

[0034] Now we will combine Figures 1 to 10 The preferred embodiments of this utility model will be described in detail below. The following description is exemplary in nature and is not intended to limit the utility model or its application or use.

[0035] Certain directional terms used in the description of the accompanying drawings below will be understood to have normal meaning and refer to those directions involved in the normal observation of the drawings, but not necessarily the orientation of the device in actual use. For example, "axial" and "radial" respectively refer to Figure 1 The directions indicated by "L" and "R" are "up" and "down". Figure 1 The top and bottom angles when viewed from different perspectives.

[0036] Figure 1 A longitudinal cross-sectional view of a first embodiment of the scroll compressor 100 according to the present invention is shown. Figure 1 As shown, the scroll compressor 100 includes a housing 91, a top cover 92 disposed at the upper shaft end of the housing 91, and a bottom cover 93 disposed at the lower shaft end of the housing 91. The housing 91, the top cover 92, and the bottom cover 93 together form the outer shell 9 of the scroll compressor 100 and define a sealed internal space inside the outer shell 9.

[0037] The scroll compressor 100 is configured to also include a motor 1, a compression mechanism CM, a bearing housing 5, and an oil sump 6 arranged within the internal space of the housing 9. Figure 1 In the example shown, the motor 1, compression mechanism CM, bearing housing 5, and oil sump 6 are arranged from top to bottom along the axial direction L within the internal space of the housing 9. These components will be described in detail below.

[0038] Motor 1 is provided to power the scroll compressor 100 to perform compression operations. The motor is configured to include a rotor 11 and a stator 12. When motor 1 is arranged in the interior space of housing 9, stator 12 can be fixedly attached to the inner peripheral wall of housing 91, and rotor 11 can be arranged radially inside stator 12 and perform rotational motion relative to stator 12.

[0039] The scroll compressor preferably includes a single compression mechanism CM. The compression mechanism CM includes a stationary scroll 2 and a moving scroll 3. The moving scroll 3 engages axially downwards with the stationary scroll 2 to define a compression chamber between the moving scroll 3 and the stationary scroll 2. Specifically, see [reference needed]. Figure 2 The fixed scroll 2 includes a fixed scroll end plate 21 and a fixed scroll 22 extending downward along the axial direction L from the fixed scroll end plate 21. The moving scroll 3 includes a moving scroll end plate 31 and a moving scroll 32 extending upward along the axial direction from the moving scroll end plate 31. The moving scroll 3 also includes a drive coupling part 33 for cooperating with the drive shaft described below. The moving scroll 32 is radially engaged with the fixed scroll 22. The specific meshing method and working principle of the moving scroll 3 and the fixed scroll 2 are well known to those skilled in the art and will not be described in detail herein.

[0040] The bearing housing 5 is arranged axially below the moving scroll 3. The bearing housing 5 supports the drive shaft (described in detail below) and also provides axial thrust protection for the compression mechanism CM. Furthermore, when a cross-slip ring is used, the moving scroll 3 can avoid rotation by means of the cross-slip ring, thus enabling it to perform a circumferential motion relative to the stationary scroll 2. The bearing housing 5 allows the cross-slip ring to be attached to it. Additionally, an upwardly opening receiving recess 51 is provided on the upper end face of the bearing housing 5 to accommodate the second cylindrical portion of the first bushing (described in detail below).

[0041] An oil sump 6 is located at the axial bottom of the interior space of the housing 9. A lubricant, such as lubricating oil, can be stored in the oil sump 6 for lubricating the various components of the scroll compressor 100. The scroll compressor 100 also includes a filter screen M disposed in the oil sump 6, which is capable of filtering oil flowing into the interior of the filter screen M from the outside.

[0042] The scroll compressor 100 also includes a drive shaft 4, which has a first central axis L1 and extends along the first central axis L1. The motor 1 transmits driving force to the compression mechanism CM by means of the drive shaft 4. The upper end 42 of the drive shaft 4 is fixedly connected (e.g., by interference fit) to the rotor 11 so that the drive shaft 4 can rotate about its own axis of rotation (i.e., the first central axis L1) under the drive of the rotor 11. The lower end 43 of the drive shaft 4 extends into the oil sump 6, particularly into the filter screen M. A guide pipe for guiding lubricating oil can be provided at the lower end 43 of the drive shaft 4. In the illustrated embodiment, the lower end 43 for oil suction is constructed as an additional component separate from the body of the drive shaft 4, which is attached to the body of the drive shaft 6. The section of the drive shaft 4 located between the upper end 42 and the lower end 43 passes sequentially from top to bottom in the axial direction L through the fixed scroll 2, the moving scroll 3, and the bearing housing 5. In this document, "through" means through, that is, extending from one end of a component and extending from the opposite end of the component. Thus, the scroll compressor 100 in this application is a through-shaft scroll compressor.

[0043] The drive shaft 4 has an eccentric journal 41 that engages with the moving vortex 3 (especially the drive coupling 33 of the moving vortex 3) to drive the moving vortex 3. The eccentric journal 41 has a second central axis L2 that is radially offset from the first central axis L1. When the drive shaft 4 rotates, the moving vortex 3 can revolve relative to the stationary vortex 2 under the drive of the eccentric journal 41 to perform the operation of compressing the working fluid between the moving vortex 3 and the stationary vortex 2. The specific principle of the eccentric journal 41 driving the moving vortex 3 to revolve relative to the stationary vortex 2 is well known to those skilled in the art and will not be described in detail herein.

[0044] The scroll compressor 100 also includes a bushing. The bushing provides a certain radial flexibility for the movement of the moving scroll 3. This radial flexibility can be understood as allowing the moving scroll 3 to have a slight radial displacement tolerance in the radial direction. Thus, during the operation of the scroll compressor 100, the bushing autonomously moves about the eccentric journal 41, causing the moving scroll to move closer to or away from the fixed scroll, thereby giving the moving scroll a variable eccentricity.

[0045] In this document, the bushing is preferably one of the first bushing 7 and the second bushing 8, which are described in detail below. The first bushing 7 (also referred to as the swing bushing) is designed to rotate circumferentially relative to the eccentric journal 41, and the second bushing 8 is designed to slide radially relative to the eccentric journal 41.

[0046] Figures 1 to 3The diagram shows the fit between the first bushing 7 and the drive shaft 4. An axial section of the first bushing 7 is arranged between the moving scroll 3 and the eccentric journal 41, allowing the movement of the eccentric journal 41 to be transmitted to the moving scroll 3 via this axial section. The first bushing 7 also includes another axial section adjacent to the aforementioned axial section, designed to limit the circumferential rotation angle range of the first bushing 7 relative to the eccentric journal 41.

[0047] Specifically, the first bushing 7 is constructed to include a first cylindrical portion 71 and a second cylindrical portion 72. The first cylindrical portion 71 serves as one axial segment of the first bushing 7 as described above, and the second cylindrical portion 72 serves as another axial segment of the first bushing 7 as described above. In the example shown in this application, the second cylindrical portion 72 is arranged axially below the first cylindrical portion 71. The first cylindrical portion 71 is fitted onto the outer periphery of the eccentric journal 41 of the drive shaft 4, and the second cylindrical portion 72 is fitted onto the segment of the drive shaft 4 located axially below the eccentric journal 41 and seated in the receiving recess 51 of the bearing seat 5 described above. In this application, it is preferred that the first cylindrical portion 71 and the second cylindrical portion 72 are integral pieces. In other embodiments, the first cylindrical portion 71 and the second cylindrical portion 72 may also be manufactured separately and then the second cylindrical portion 72 is fixedly connected to the first cylindrical portion 71.

[0048] See also Figure 4 and Figure 5 The first cylindrical portion 71 has a larger diameter outer peripheral wall 712 and a smaller diameter inner peripheral wall. The inner peripheral wall of the first cylindrical portion 71 defines a first circular through-hole 711 extending through from one end of the first cylindrical portion 71 to the opposite end. When the first bushing 7 is assembled to the scroll compressor 100, the eccentric journal 41 of the drive shaft 4 passes coaxially through the first circular through-hole 711 about the first circular through-hole 711. Thus, the first circular through-hole 711 extends about a second central axis L2. In this document, the radial clearance between the first cylindrical portion 71 (specifically the inner peripheral wall of the first cylindrical portion 71) and the eccentric journal 41 during normal operation of the compression mechanism is referred to as R1.

[0049] The outer peripheral wall 712 of the first cylindrical portion 71 has a circular cross-section, and the outer peripheral wall 712 of the first cylindrical portion 71 extends around the third central axis L3. The third central axis L3 is offset radially by a certain distance relative to the second central axis L2, thereby causing the first cylindrical portion 71 to have a varying wall thickness along the circumferential direction (from...). Figure 3 (This is shown more clearly in the image). In other words, the first circular through-hole 711 of the first cylindrical portion 71 is eccentric.

[0050] The second cylindrical portion 72 also has a larger diameter outer peripheral wall 722 and a smaller diameter inner peripheral wall. The inner peripheral wall of the second cylindrical portion 72 defines a second circular through hole 721 extending through from one shaft end of the second cylindrical portion 72 to the opposite shaft end. When the first bushing 7 is assembled to the scroll compressor 100, the corresponding section of the drive shaft 4 located below the eccentric journal 41 passes coaxially through the second circular through hole 721 with respect to it. This section below the eccentric journal 41 may be a section concentric with respect to a first central axis L1, and correspondingly, the second circular through hole 721 extends around the first central axis L1. In this document, the radial clearance between the second cylindrical portion 72 (specifically, the inner peripheral wall of the second cylindrical portion 72) and the corresponding section of the drive shaft 4 during normal operation of the compression mechanism is referred to as R2.

[0051] The outer peripheral wall 722 of the second cylindrical portion 72 has a circular cross-section, and the outer peripheral wall 722 of the second cylindrical portion 72 also extends around the first central axis L1, so that the second cylindrical portion 72 has a constant wall thickness in the circumferential direction.

[0052] In this application, the second cylindrical portion 72 is provided for controlling the circumferential rotation angle of the first cylindrical portion 71 relative to the eccentric journal 41. The first circular through hole 711 and the second circular through hole 721 are arranged radially offset from each other, that is, the second circular through hole 721 around the first central axis L1 is eccentric relative to the center of the first circular through hole 711 (i.e., the second central axis L2). In order to allow the first bushing to swing while appropriately controlling its swing range (i.e., controlling the circumferential rotation angle of the first cylindrical portion 71), R2 needs to be appropriately set, and in particular, R2 needs to be greater than 0. The larger the value of R2, the larger the range of circumferential rotation angles that the first cylindrical portion 71 can achieve. Typically, the maximum value of R2 needs to be adjusted / limited according to the size of the actual drive shaft 4 and the size of each axial segment of the first bushing 7 to ensure that the rotation angle of the first cylindrical portion 71 relative to the eccentric journal 41 does not exceed 180°, otherwise it may have the adverse effect of the vortex profile not being able to fit properly.

[0053] Figure 6 and Figure 7 A schematic diagram is shown showing how the second cylindrical section 72 controls the swing range when the first cylindrical section 71 swings relative to the eccentric journal 41. Figure 6 The schematic diagram shows the limit rotational position of the first bushing 7 relative to the eccentric journal 41 in the first direction. Figure 7The diagram schematically illustrates the limit of rotation of the first bushing 7 relative to the eccentric journal 41 in the second direction. Specifically, when it is necessary to rotate the first cylindrical portion 71 relative to the eccentric journal 41 in the first direction to adjust the eccentricity of the moving vortex 3, the second cylindrical portion 72 is stopped at point A when it reaches point A, thus preventing the first cylindrical portion 71 from rotating further in the first direction. Similarly, when it is necessary to rotate the first cylindrical portion 71 relative to the eccentric journal 41 in the second direction, opposite to the first direction, to adjust the eccentricity of the moving vortex 3, the second cylindrical portion 72 is stopped at point B when it reaches point B, thus preventing the first cylindrical portion 71 from rotating further in the second direction. In other words, in this invention, the second cylindrical portion 72 is only allowed to oscillate within the range from point A to point B. By designing R2, the circumferential angle interval between points A and B can be adjusted so that the circumferential interval between points A and B is less than 180°, thereby controlling the rotation angle of the first cylindrical part 71 relative to the eccentric journal to not exceed 180°.

[0054] In this paper, R2 is further preferably designed to be greater than 10×R1. This ensures that there is a suitablely large gap between the second cylindrical part 72 and the drive shaft 4, so as to ensure that the swing bushing (i.e. the first bushing 7) can achieve a suitablely large swing range to ensure that the moving vortex 3 has a suitablely large radial flexibility, and to ensure that the profile of the moving vortex 3 fits smoothly with the profile of the fixed vortex 2.

[0055] By employing the second cylindrical portion 72, the circumferential rotation angle of the first cylindrical portion 71 is effectively controlled. This achieves effective control of the swing range of the swing bushing with a design that is less complex, more compact, and less expensive, thus preventing the swing bushing from swinging excessively and causing the compressor to malfunction.

[0056] See back Figure 4 The first bushing 7 may further include a retaining ring 73, which is disposed in the section of the first cylindrical portion 71 near the second cylindrical portion 72 and extends radially from the outer peripheral wall 712 of the first cylindrical portion 71. When engaged with the moving scroll 3, the retaining ring 73 can, to a certain extent, limit the axial displacement of the first bushing 7. An oil guide groove 731 is provided on the lower shaft end face of the retaining ring 73 to facilitate the guidance of lubricant to the upper end face of the bearing housing 5. When using the retaining ring 73, it is preferable that the first cylindrical portion 71, the second cylindrical portion 72, and the retaining ring 73 are integrally formed.

[0057] Figures 8 to 10 A schematic diagram of a second embodiment of the scroll compressor 100 according to the present invention is shown. In the second embodiment, the remaining components of the scroll compressor 100 are substantially the same as those of the first embodiment, except that the first bushing 7 described above is replaced with a second bushing 8, which will be described in detail below.

[0058] The second bushing 8 (also referred to as a sliding bushing) is constructed to include a main body 81 and a through hole 82 extending through the main body 81 along the axial direction L. The cross-section of the through hole is substantially D-shaped, and therefore it is also referred to herein as a D-shaped through hole 82. The D-shaped through hole 82 has a planar section.

[0059] When the second bushing 8 is assembled to the scroll compressor 100, the eccentric journal 41 of the drive shaft 4 will pass through the D-shaped through hole 82 of the second bushing 8. In order to cooperate with the second bushing 8, a drive plane section 411 needs to be provided on the eccentric journal 41, which will cooperate with the plane section of the D-shaped through hole 82.

[0060] See especially Figure 10 After the eccentric journal 41 is inserted into the D-shaped through hole 82, the driving plane section 411 of the eccentric journal 41 will face the plane section of the D-shaped through hole 82. The radial dimension of the D-shaped through hole 82 is designed to allow the driving plane section 411 to move a certain distance radially R relative to the plane section of the D-shaped through hole 82 after the eccentric journal 41 is inserted into the D-shaped through hole 82. This allows the main body 81 to slide radially R relative to the eccentric journal 41, so that the scroll compressor can autonomously adjust the eccentricity of the moving scroll.

[0061] By providing bushings 7 and 8 in the through-shaft scroll compressor, radial flexibility is introduced, thereby ensuring that the eccentricity of the moving scroll is no longer solely determined by the fixed eccentricity of the eccentric journal 41, but rather by both the eccentric journal 41 and the bushings 7 and 8. When using the first bushing 7, the first cylindrical portion 71 with varying wall thickness can rotate circumferentially around the eccentric journal 41, allowing the center of the moving scroll 3 to be flexibly and autonomously adjusted according to the machining tolerances of the relevant components, thus achieving a variable eccentricity for the moving scroll 3. Similarly, when using the second bushing 8, the main body 81 can slide radially R relative to the eccentric journal 41, also enabling the moving scroll 3 to have a variable eccentricity.

[0062] Taking the first bushing 7 as an example, when the eccentricity of the eccentric journal 41 is less than the eccentricity of the scroll due to machining tolerances or assembly issues, the first bushing 7 can be rotated to a position with a larger wall thickness to change the eccentricity of the scroll, thereby allowing the scroll profiles to contact each other and achieving radial sealing to avoid leakage. When the eccentricity of the eccentric journal 41 is greater than the eccentricity of the scroll due to machining tolerances or assembly issues, the first bushing 7 can be rotated to a position with a smaller wall thickness to change the eccentricity of the scroll, thereby avoiding radial interference between the scroll profiles.

[0063] By providing the first bushing 7 and the second bushing 8, the requirements for the machining accuracy of the parts are reduced, as are the requirements for the assembly accuracy of the compressor. This reduces the manufacturing cost of the through-shaft scroll compressor and further improves its reliability.

[0064] It should be noted that although this document illustrates an example of the motor 1, compression mechanism CM, and bearing housing 5 arranged axially from top to bottom within the interior space of the housing 9, and of the moving scroll 3 being arranged below the fixed scroll 2, those skilled in the art will understand that the relative positions of the above components are not limited thereto. For example, provided that the drive shaft 4 passes axially through the fixed scroll 2 and the moving scroll 3, the motor 1 can be arranged below the bearing housing 5, in which case the lower shaft end 43 of the drive shaft 4 is connected to the motor 1. Alternatively, for example, the bearing housing 5, the moving scroll 3, and the fixed scroll 2 can be arranged axially from top to bottom along the L, in which case the second cylindrical portion 72 can also be located axially above the first cylindrical portion 71. Furthermore, a portion of the motor and drive shaft may also be arranged outside the housing.

[0065] The preferred embodiments of the present invention have been described above with reference to specific examples. It is understood that the above description is exemplary and not restrictive, and various modifications and variations can be conceived by those skilled in the art without departing from the scope of the present invention. These modifications and variations are also included within the scope of protection of this application.

Claims

1. A scroll compressor characterized by, include: A motor, which is designed to power the scroll compressor; A compression mechanism, comprising a fixed scroll and a moving scroll, wherein the moving scroll meshes with the fixed scroll to define a compression cavity between the moving scroll and the fixed scroll; A drive shaft having a first central axis and extending along the first central axis through the fixed vortex and the moving vortex, one end of the drive shaft being connected to the motor such that the drive shaft can rotate about the first central axis under the drive of the motor, the drive shaft having an eccentric journal having a second central axis radially offset about the first central axis, the eccentric journal engaging with the moving vortex to drive the moving vortex to move; as well as A bushing is designed to move relative to the eccentric journal to give the moving scroll a variable eccentricity. One axial section of the bushing is arranged between the moving scroll and the eccentric journal so that the power of the drive shaft can be transmitted to the moving scroll via the axial section of the bushing. Another axial section of the bushing is designed to limit the range of motion of the bushing relative to the eccentric journal to further limit the range of variation of the variable eccentricity of the moving scroll.

2. The scroll compressor of claim 1, wherein The bushing is designed to rotate circumferentially relative to the eccentric journal, and another axial section of the bushing is designed to limit the range of circumferential rotation angle of the bushing relative to the eccentric journal.

3. The scroll compressor of claim 1, wherein The scroll compressor includes a single compression mechanism.

4. The scroll compressor of claim 1, wherein The compression mechanism is arranged axially below the motor, the moving scroll meshes with the stationary scroll axially below the stationary scroll, the upper end of the drive shaft is connected to the motor, the scroll compressor also includes a bearing housing arranged axially below the compression mechanism, the drive shaft passes through the bearing housing, the scroll compressor also includes an oil sump arranged axially below the bearing housing, and the lower end of the drive shaft extends into the oil sump.

5. The scroll compressor according to any one of claims 2 to 4, wherein The bushing is configured to include a first cylindrical portion and a second cylindrical portion arranged axially adjacent to the first cylindrical portion, the first cylindrical portion being sleeved on the outer periphery of the eccentric journal, wherein the first cylindrical portion serves as one axial segment of the bushing and the second cylindrical portion serves as another axial segment of the bushing.

6. The scroll compressor according to claim 5, characterized in that, The second cylindrical portion is arranged axially below the first cylindrical portion.

7. The scroll compressor of claim 6, wherein The inner peripheral wall of the first cylindrical portion defines a first circular through hole, the eccentric journal passes coaxially through the first circular through hole about the first circular through hole, and the outer peripheral wall of the first cylindrical portion extends about a third central axis that is radially offset about the second central axis.

8. The scroll compressor of claim 6 or 7, wherein The inner peripheral wall of the second cylindrical portion defines a second circular through hole, and the section of the drive shaft located axially below the eccentric journal passes through the second circular through hole coaxially with respect to the second circular through hole, and the outer peripheral wall of the second cylindrical portion extends around the first central axis.

9. The scroll compressor according to claim 6, characterized in that, The upper end face of the bearing seat of the scroll compressor, which is located axially below the compression mechanism, has an upwardly open receiving recess so that the second cylindrical part can be conformally seated in the receiving recess.

10. The scroll compressor according to claim 8, characterized in that, The radial clearance between the first cylindrical portion and the eccentric journal is R1, and the radial clearance between the second cylindrical portion and the corresponding section of the drive shaft is R2, wherein R2 > 0, and R2 is designed to allow the first cylindrical portion to rotate less than 180° relative to the eccentric journal.

11. The scroll compressor of claim 10, wherein, R2 > 10R1.

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