Shafting arrangement and compressor

Abstract

This invention provides a shaft system structure and a compressor. The shaft system structure includes: a moving scroll and a moving disk bearing sleeved on the lower end of the moving scroll; a rotor assembly disposed below the moving scroll; a crankshaft including a large outer diameter shaft section and a small outer diameter shaft section connected sequentially from top to bottom, the upper end of the large outer diameter shaft section having an eccentric bearing hole for mounting the moving disk bearing, and the rotor assembly sleeved on the small outer diameter shaft section; an upper bracket through which the crankshaft passes, the upper bracket including a bracket body, the bracket body including a receiving cavity; and a main balance block sleeved on the crankshaft and located within the receiving cavity, the center of mass of the main balance block being spaced apart from the rotation axis of the crankshaft, to solve the problem in the prior art scroll compressors where the axial distance between the main balance block and the eccentric excitation source of the moving scroll is too large, resulting in poor balancing effect.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, and more specifically, to a shaft system structure and a compressor. Background Technology

[0002] A scroll compressor is a high-efficiency positive displacement compression device. Its core compression component consists of a stationary scroll plate and a moving scroll plate. During operation, the moving scroll plate, driven by a motor, makes a slight eccentric revolution around the center of the stationary scroll plate, forming a series of continuously changing crescent-shaped closed volumes, thereby realizing the intake, compression, and discharge of gas. The stability of its motion process directly depends on the precise matching of the shaft system and the support system.

[0003] The shaft system of current scroll compressors typically consists of a crankshaft, an upper support, a lower support, and a rotor assembly. The crankshaft drives the rotating scroll plate through an eccentric structure, and its motion is supported by bearings in the upper and lower supports. The upper support usually adopts a double bearing structure with two concentric arrangement and the same size to undertake the rotational support function of the rotating scroll plate side and the motor side, respectively.

[0004] However, in scroll compressors, the main balance block is located at the lower end of the upper support, and the axial distance between it and the eccentric excitation source of the moving scroll disk is too far. This causes the balancing force and the inertial force to be unable to be on the same plane, resulting in a significant unbalanced couple. This leads to poor balancing effect, causing shaft deflection, increased vibration, increased noise and decreased energy efficiency, which seriously restricts the further improvement of the overall performance of the scroll compressor. Summary of the Invention

[0005] The main objective of this invention is to provide a shaft system structure and compressor to solve the problem of poor balancing effect in existing scroll compressors due to the excessive axial distance between the main balance block and the eccentric excitation source of the moving scroll disk.

[0006] To achieve the above objectives, according to one aspect of the present invention, a shaft system structure is provided, at least applicable to a compressor. The shaft system structure includes: a moving scroll and a moving disc bearing sleeved on the lower end of the moving scroll; a rotor assembly disposed below the moving scroll; a crankshaft including a large outer diameter shaft section and a small outer diameter shaft section connected sequentially from top to bottom, the upper end of the large outer diameter shaft section having an eccentric bearing hole for mounting the moving disc bearing, and the rotor assembly sleeved outside the small outer diameter shaft section; an upper bracket through which the crankshaft passes, the upper bracket including a bracket body, the bracket body including a receiving cavity; and a main balance block sleeved on the crankshaft and located within the receiving cavity, the center of mass of the main balance block being spaced apart from the rotation axis of the crankshaft.

[0007] Furthermore, the upper support also includes a support cover plate and two support bearings. The support cover plate is set in the receiving cavity to divide the receiving cavity into an upper moving plate cavity and a lower balance cavity. The two support bearings are respectively sleeved on the outside of the crankshaft, and the main balance block is located in the lower balance cavity.

[0008] Furthermore, the main balancing block includes an annular connecting sleeve and an eccentric block disposed on one side of the outer circumferential surface of the annular connecting sleeve, with the annular connecting sleeve fitted onto the large outer diameter shaft section.

[0009] Furthermore, the two support bearings include a large bearing and a small bearing spaced apart from top to bottom. The large bearing and the small bearing are respectively installed inside the bracket cover plate and the bracket body, and the large bearing and the small bearing are respectively sleeved on the outside of the large outer diameter shaft section and the small outer diameter shaft section.

[0010] Furthermore, the upper bracket has a mounting through hole in the middle. The mounting through hole includes a large-diameter hole section and a small-diameter hole section located at the upper and lower ends of the lower balance cavity, respectively. The large-diameter hole section is located on the bracket cover plate and is corresponding to the large outer diameter shaft section. The large bearing is located between the large-diameter hole section and the large outer diameter shaft section. The small-diameter hole section is located on the bracket body and is corresponding to the small outer diameter shaft section. The small bearing is located between the small outer diameter shaft section and the large outer diameter shaft section.

[0011] Furthermore, the main body of the support is provided with an oil return hole, one end of which extends to the outer circumferential surface of the upper support, and the other end of which is connected to the lower balance cavity. The shaft system structure also includes an oil return pipe, one end of which is connected to the first end of the oil return hole, and the other end of which extends to the oil sump located at the bottom of the shaft system structure; and / or, the upper end face of the large bearing is lower than the upper end of the large diameter bore section; and / or, the lower end face of the small bearing is higher than the lower end of the small diameter bore section; and / or, the bottom surface of the large diameter bore section is in frictional contact with the lower end face of the large outer diameter shaft section to serve as the thrust surface of the crankshaft.

[0012] Furthermore, the upper end face of the large bearing is flush with the upper end face of the large outer diameter shaft section; and / or, the upper end face of the large bearing is flush with the upper end face of the moving disc bearing.

[0013] Furthermore, the crankshaft is also provided with an oil suction hole and an oil guide hole. The oil suction hole is located at the lower end of the small outer diameter shaft section, the lower end of the oil guide hole is connected to the oil suction hole, and the upper end of the oil guide hole is connected to the eccentric bearing hole. The shaft system structure also includes an oil suction pipe, the upper end of which is fixedly inserted into the oil suction hole, and the lower end of which extends to the oil sump located at the bottom of the shaft system structure.

[0014] Furthermore, an upper tangential outer oil groove for lubricating oil to flow into is provided on the outer circumferential surface of the large outer diameter shaft section, the upper tangential outer oil groove extending to the upper end face of the large outer diameter shaft section and corresponding to the large bearing; and / or, an upper tangential inner oil groove for lubricating oil to flow into is provided on the inner wall surface of the eccentric bearing hole, the upper tangential inner oil groove extending to the upper end face of the large outer diameter shaft section and corresponding to the moving disc bearing; and / or, a lower tangential outer oil groove for lubricating oil to flow into is provided on the outer circumferential surface of the small outer diameter shaft section, the lower tangential outer oil groove corresponding to the small bearing, and an oil passage hole is also provided on the small outer diameter shaft section, the two ends of the oil passage hole being connected to the oil guide hole and the lower tangential outer oil groove, respectively.

[0015] Furthermore, the oil suction pipe includes a pipe body and an oil guide plate disposed within the pipe body. The oil guide plate is a spiral plate, and the oil guide plate is interference-fitted with the inner wall of the pipe body so as to rotate synchronously with the crankshaft to draw the lubricating oil in the oil sump into the oil suction hole.

[0016] Furthermore, the shaft system structure also includes: a cross slip ring, a first slip ring groove for mounting a portion of the cross slip ring on the moving scroll plate, and a second slip ring groove for mounting another portion of the cross slip ring on the bracket cover plate; and / or, a sealing lubrication ring, the upper end face of which abuts against the moving scroll plate, and an annular inner flange on the bracket cover plate, the inner wall surface of which is already flush with the mounting support bearing, and an annular mounting groove for mounting a portion of the sealing lubrication ring on the upper end of the annular inner flange, thereby dividing the upper end of the annular inner flange into a first annular end face and a second annular end face arranged sequentially in a direction away from the support bearing, both of which are higher than the bottom surface of the annular mounting groove, for contacting the moving scroll plate to support it.

[0017] Furthermore, the rotor assembly includes a rotor and a secondary balancing block located at the end of the rotor away from the upper support. The center of mass of the secondary balancing block and the main balancing block are offset by 180 degrees around the center line of the rotor. A rotor flow hole is provided on the rotor and extends through the rotor along the rotor's axial direction. The rotor flow hole is located on the side of the secondary balancing block near the center line of the rotor.

[0018] According to another aspect of the present invention, a compressor is provided, including a housing and a stator assembly, a stationary scroll plate, and a shaft system structure located within the housing. The shaft system structure is the shaft system structure described above. The stator assembly is sleeved outside the rotor assembly of the shaft system structure and is fixedly connected to the housing. The stationary scroll plate and the moving scroll plate cooperate with each other and are fixedly connected to the housing.

[0019] Applying the technical solution of this invention, the shaft system structure of this invention is at least applicable to compressors. The shaft system structure includes: a moving scroll and a moving disc bearing sleeved on the lower end of the moving scroll; a rotor assembly disposed below the moving scroll; a crankshaft including a large outer diameter shaft section and a small outer diameter shaft section connected sequentially from top to bottom, the upper end of the large outer diameter shaft section having an eccentric bearing hole for installing the moving disc bearing, and the rotor assembly sleeved outside the small outer diameter shaft section; an upper bracket through which the crankshaft passes, the upper bracket including a bracket body, the bracket body including a receiving cavity; and a main balance block sleeved on the crankshaft and located within the receiving cavity, the center of mass of the main balance block being spaced apart from the rotation axis of the crankshaft. In this way, the shaft system structure of the present invention fundamentally reconstructs the dynamic balance system of the compressor by embedding the main balance block in the receiving cavity of the upper bracket and offsetting its center of mass from the crankshaft rotation axis. The main balance block is directly arranged below the moving scroll and inside the upper bracket, which significantly shortens the lever arm distance between the balancing mass and the excitation source. This makes the balancing torque and the gas torque more coplanar and synchronously opposite in space, greatly improving the dynamic balance accuracy of the shaft system structure. During operation, the vibration amplitude is reduced and the noise level is significantly reduced. This solves the problem of poor balancing effect in the existing scroll compressor due to the excessive axial distance between the main balance block and the eccentric excitation source of the moving scroll. The stability advantage is particularly prominent under high speed or high pressure ratio conditions. It avoids the phenomenon that the main balance block in the existing technology is usually set at both ends of the motor rotor, which is far away from the gas force excitation source of the moving scroll, resulting in the inertial force being unable to effectively counteract the high-frequency overturning torque of the moving scroll during the compression process, thus causing vibration and noise. Attached Figure Description

[0020] The accompanying drawings, which form part of this application, are used to provide a further understanding of the invention. The illustrative embodiments of the invention and their descriptions are used to explain the invention and do not constitute an undue limitation of the invention. In the drawings:

[0021] Figure 1 A cross-sectional view of an embodiment of the compressor according to the present invention is shown (dashed arrows indicate oil passages, and actual arrows indicate gas passages).

[0022] Figure 2 It shows Figure 1 A magnified view of part A of the compressor shown;

[0023] Figure 3 It shows Figure 1 A magnified view of part B of the compressor shown;

[0024] Figure 4 It shows Figure 1 A perspective view of the moving scroll of the compressor shown;

[0025] Figure 5 It shows Figure 1A cross-sectional view of the upper support of the compressor shown;

[0026] Figure 6 It shows Figure 5 A schematic diagram of the structure of the first embodiment of the bracket cover plate of the upper bracket shown;

[0027] Figure 7 It shows Figure 5 A schematic diagram of the structure of the second embodiment of the bracket cover plate of the upper bracket shown;

[0028] Figure 8 It shows Figure 1 A perspective view of the crankshaft of the compressor shown;

[0029] Figure 9 It shows Figure 1 The diagram shows the structure of the compressor rotor assembly.

[0030] The above figures include the following reference numerals:

[0031] 1. Shell; 2. Static vortex disk;

[0032] 3. Moving scroll plate; 31. First slip ring groove; 32. High-pressure oil groove of moving scroll plate; 33. Medium-pressure diversion groove of moving scroll plate;

[0033] 4. Sealing and lubrication ring; 5. Cross slip ring;

[0034] 6. Upper bracket; 60. Bracket body; 61. Large bearing; 62. Small bearing; 63. Large diameter bore section; 64. Small diameter bore section; 65. Oil return hole; 66. Receiving cavity; 661. Upper moving plate cavity; 662. Lower balance cavity; 67. First annular end face; 68. Second slip ring groove; 69. Annular inner flange; 610. Annular mounting groove; 611. Bracket cover plate; 612. Second annular end face;

[0035] 7. Moving disc bearing;

[0036] 8. Crankshaft; 81. Large outer diameter shaft section; 82. Small outer diameter shaft section; 83. Eccentric bearing bore; 84. Oil suction hole; 85. Oil guide hole; 86. Upper chamfered outer oil groove; 87. Upper chamfered inner oil groove; 88. Lower chamfered outer oil groove; 89. Oil passage hole;

[0037] 9. Rotor assembly; 91. Rotor; 93. Secondary balance block; 911. Rotor flow hole;

[0038] 10. Stator assembly; 11. Oil return pipe;

[0039] 12. Oil suction pipe; 121. Pipe body; 122. Oil guide plate;

[0040] 13. Oil tank;

[0041] 14. Main balance block; 141. Annular connecting sleeve; 142. Eccentric block. Detailed Implementation

[0042] It should be noted that, unless otherwise specified, the embodiments and features described in this application can be combined with each other. The present invention will now be described in detail with reference to the accompanying drawings and embodiments.

[0043] like Figures 1 to 9 As shown, the present invention provides a shaft system structure, at least applicable to compressors. The shaft system structure includes: a moving scroll 3 and a moving disk bearing 7 sleeved on the lower end of the moving scroll 3; a rotor assembly 9 disposed below the moving scroll 3; a crankshaft 8, including a large outer diameter shaft section 81 and a small outer diameter shaft section 82 connected sequentially from top to bottom, the upper end of the large outer diameter shaft section 81 having an eccentric bearing hole 83 for mounting the moving disk bearing 7, and the rotor assembly 9 sleeved outside the small outer diameter shaft section 82; an upper bracket 6, through which the crankshaft 8 passes, the upper bracket 6 including a bracket body 60, the bracket body 60 including a receiving cavity 66; and a main balance block 14, sleeved on the crankshaft 8 and located within the receiving cavity 66, the center of mass of the main balance block 14 being spaced apart from the rotation axis of the crankshaft 8.

[0044] Thus, the shaft system structure of the present invention fundamentally reconstructs the dynamic balance system of the compressor by embedding the main balance block 14 inside the receiving cavity 66 of the upper bracket 6 and offsetting its center of mass from the rotation axis of the crankshaft 8. The main balance block 14 is directly arranged below the moving scroll disk 3 and inside the upper bracket 6, which significantly shortens the lever arm distance between the balancing mass and the excitation source, making the balancing torque and the gas torque more coplanar and synchronously opposite in space. This greatly improves the dynamic balance accuracy of the shaft system structure, reduces the vibration amplitude and significantly reduces the noise level during operation. It solves the problem of poor balancing effect caused by the axial distance between the main balance block and the eccentric excitation source of the moving scroll disk in the prior art scroll compressor. The stability advantage is more prominent, especially under high speed or high pressure ratio conditions. It avoids the phenomenon that the main balance block in the prior art is usually set at both ends of the motor rotor, which is far away from the gas force excitation source of the moving scroll disk, resulting in the inertial force being unable to effectively counteract the high-frequency overturning torque of the moving scroll disk during the compression process, thus causing vibration and noise.

[0045] Furthermore, the shaft system structure of this invention integrates the main balance block 14 inside the upper bracket 6, which not only simplifies the shaft system assembly process but also reduces the risk of accumulated tolerances and loose parts caused by multi-point connections. Simultaneously, since the main balance block 14 no longer relies on the rotor assembly 9 for support, the rotor assembly 9 can adopt a lighter design, reducing rotational inertia and thus reducing starting torque and energy consumption. This provides a structural basis for subsequent optimization of the rotor assembly 9 and offers systematic support for achieving overall miniaturization, weight reduction, and energy efficiency improvement.

[0046] Specifically, both the large outer diameter shaft segment 81 and the small outer diameter shaft segment 82 are cylindrical shaft segments. The large outer diameter shaft segment 81 and the small outer diameter shaft segment 82 are relative concepts, indicating that the outer diameter of the large outer diameter shaft segment 81 is larger than the outer diameter of the small outer diameter shaft segment 82.

[0047] like Figure 5 As shown, the upper support 6 also includes a support cover plate 611 and two support bearings. The support cover plate 611 is disposed in the receiving cavity 66 to divide the receiving cavity 66 into an upper moving plate cavity 661 and a lower balance cavity 662. The two support bearings are respectively sleeved on the outside of the crankshaft 8, and the main balance block 14 is located in the lower balance cavity 662.

[0048] The shaft system structure of the present invention, by adding a bracket cover plate 611 inside the upper bracket, achieves for the first time physical isolation and functional partitioning between the support area of ​​the moving scroll plate 3 and the installation area of ​​the main balance block 14. This not only provides a stable and closed cavity space for the installation of the high-precision main balance block 14, but also avoids it from contacting contaminants such as lubricating oil and metal shavings of the moving scroll plate 3, thus extending the life of the balance block.

[0049] like Figure 9 As shown, the main balancing block 14 includes an annular connecting sleeve 141 and an eccentric block 142 disposed on one side of the outer circumferential surface of the annular connecting sleeve 141. The annular connecting sleeve 141 is sleeved on the large outer diameter shaft section 81.

[0050] The shaft system structure of the present invention achieves a dual improvement in the precise control of balance quality and the ease of assembly by designing the main balance block 14 as a combination of an annular connecting sleeve 141 and a single-sided eccentric block 142. The annular connecting sleeve 141 is used as the base, and its inner hole is interference-fitted with the large outer diameter shaft section 81 of the crankshaft 8. The eccentric block 142 is fixed to the outer wall of the annular connecting sleeve 141 by integral casting or welding. This ensures the dynamic balance accuracy during rotation and realizes the modular setting of eccentric quality. It allows for rapid balancing by replacing the main balance block 14 of different weights during the whole machine debugging stage, which significantly reduces the production line debugging time and rework rate.

[0051] like Figures 1 to 3 as well as Figure 5 As shown, the two support bearings include a large bearing 61 and a small bearing 62 arranged at intervals from top to bottom. The large bearing 61 and the small bearing 62 are respectively installed in the bracket cover plate 611 and the bracket body 60, and the large bearing 61 and the small bearing 62 are respectively sleeved on the outer side of the large outer diameter shaft section 81 and the small outer diameter shaft section 82.

[0052] The shaft system structure of this invention achieves synergistic optimization of load and stiffness by setting the crankshaft 8 as a double-segment structure with a large outer diameter shaft segment 81 and a small outer diameter shaft segment 82, respectively, and corresponding to the large bearing 61 and the small bearing 62 of different sizes coaxially within the upper support 6. The large outer diameter shaft segment 81 bears the high load of the moving scroll disk 3, and its diameter matches the inner diameter of the large bearing 61, enhancing bending stiffness; while the small outer diameter shaft segment 82 only needs to bear the self-weight of the rotor assembly 9 and the low-amplitude rotational inertial force, and the reduction of its diameter significantly reduces the load on the small bearing 61. The sliding friction area and circumferential speed between bearings 62 reduce mechanical power consumption from the source, achieving a precise match between large diameter for heavy loads and small diameter for light loads. This solves the problem that the arrangement of the upper support bearings in existing scroll compressors cannot achieve a compact, lightweight, and low-power shaft structure while ensuring the stability of the moving scroll. It also avoids the phenomenon of large deflection and poor stability caused by the high-pressure gas force on the moving scroll being transmitted to the middle bearing through the crankshaft eccentricity in the shaft structure of existing compressors.

[0053] The shaft system structure of this invention eliminates the existing lower bracket and bottom thrust bearing, and concentrates the axial support function on the upper bracket 6, so that the entire shaft system forms a compact cantilever structure with upper support and lower suspension, which greatly reduces the axial height of the scroll compressor and has significant structural advantages for space-sensitive compressors such as household / commercial inverter air conditioners and heat pumps.

[0054] Meanwhile, since the moving scroll bearing 7 is directly installed in the eccentric bearing hole 83 of the large outer diameter shaft section 81 of the crankshaft 8, the point of application of gas force is axially close to the support center of the large bearing 61, which effectively shortens the torque arm, significantly suppresses the bending deformation of the crankshaft 8, makes the motion trajectory of the moving scroll 3 more ideal, reduces the fluctuation of the sealing gap, and greatly improves the compression efficiency and long-term reliability, laying the foundation for the realization of a high-efficiency, low-noise compressor.

[0055] like Figures 1 to 3 as well as Figure 5 As shown, the upper bracket 6 has a mounting through hole in the middle. The mounting through hole includes a large-diameter hole section 63 and a small-diameter hole section 64 located at the upper and lower ends of the lower balance cavity 662, respectively. The large-diameter hole section 63 is located on the bracket cover plate 611 and is corresponding to the large outer diameter shaft section 81. The large bearing 61 is located between the large-diameter hole section 63 and the large outer diameter shaft section 81. The small-diameter hole section 64 is located on the bracket body 60 and is corresponding to the small outer diameter shaft section 82. The small bearing 62 is located between the small outer diameter shaft section 82 and the large outer diameter shaft section 81.

[0056] Specifically, the large bearing 61 and the small bearing 62 are relative concepts, indicating that the outer diameter of the large bearing 61 is larger than the outer diameter of the small bearing 62, and the inner diameter of the large bearing 61 is larger than the inner diameter of the small bearing 62; the large-diameter bore section 63 and the small-diameter bore section 64 are both cylindrical bore sections, and the large-diameter bore section 63 and the small-diameter bore section 64 are also relative concepts, indicating that the inner diameter of the large-diameter bore section 63 is larger than the inner diameter of the small-diameter bore section 64.

[0057] The shaft system structure of the present invention provides a stepped mounting through hole in the upper support body 60, so that the large bearing 61 and the small bearing 62 form a coaxial support system in the axial direction, avoiding the problems of shaft system eccentricity and vibration superposition caused by axial misalignment in the existing multi-support series structure.

[0058] Among them, the large-diameter bore section 63 provides sufficient radial constraint space for the high-load area on the side of the moving scroll disk 3, while the small-diameter bore section 64 provides precise guidance for the light-load area on the side of the rotor assembly 9. The two have a smooth axial transition, ensuring that the crankshaft 8 does not experience step-like jumps under high-speed rotation. This makes the upper bracket 6 an integrated component that combines radial support, axial positioning, and bearing installation. This not only simplifies the assembly process and reduces the number of parts, but also greatly improves the concentricity and dynamic balance accuracy of the shaft system structure, effectively reducing the noise of the entire machine.

[0059] The aforementioned stepped mounting through-hole design also enables axial positioning and preload control of the large bearing 61 and the small bearing 62. The large bearing 61 is installed in the large-diameter bore section 63, and its axial position is jointly defined by the moving scroll plate 3 and the lower end face of the large-diameter bore section 63. The small bearing 62 is located in the small-diameter bore section 64, and its axial position can be precisely controlled by the transition step between the large outer diameter shaft section 81 and the small outer diameter shaft section 82 of the crankshaft 8.

[0060] like Figures 1 to 3 as well as Figure 5 As shown, the support body 60 is provided with an oil return hole 65. One end of the oil return hole 65 extends to the outer peripheral surface of the upper support 6, and the other end of the oil return hole 65 is connected to the lower balance cavity 662. The shaft system structure also includes an oil return pipe 11. One end of the oil return pipe 11 is connected to the first end of the oil return hole 65, and the other end of the oil return pipe 11 extends to the oil sump 13 located at the bottom of the shaft system structure; and / or, the upper end face of the large bearing 61 is lower than the upper end of the large diameter bore section 63; and / or, the lower end face of the small bearing 62 is higher than the lower end of the small diameter bore section 64; and / or, the bottom surface of the large diameter bore section 63 is in frictional contact with the lower end face of the large outer diameter shaft section 81 to serve as the thrust surface of the crankshaft 8.

[0061] The shaft system structure of this invention constructs a highly efficient self-circulating oil circuit by setting an oil return hole 65 on the outer periphery of the upper bracket 6 and connecting it to an oil return pipe 11 that leads directly to the oil sump 13. During the operation of the compressor, some lubricating oil leaks into the mounting through hole through the gap between the driven scroll plate 3 and the upper bracket 6. Without the oil return hole 65, this oil is prone to accumulate or be thrown into the rotor assembly 9, causing lubrication failure or insulation risk. However, the shaft system structure of this invention actively recovers this leaked oil through the oil return hole 65 and the oil return pipe 11, and achieves pump-free self-returning oil by combining gravity and centrifugal force, ensuring stable lubrication and controllable oil quantity, significantly improving the reliability of the compressor, and is particularly suitable for environmentally friendly air conditioning systems with low filling volume and high safety requirements.

[0062] This design provides axial thermal expansion space and assembly clearance for the large bearing 61 and the small bearing 62, preventing bearing jamming or deformation due to temperature rise or press stress. More importantly, the bottom surface of the large-diameter bore section 63 makes frictional contact with the lower end face of the large-outer-diameter shaft section 81, directly using the bottom surface of the large-diameter bore section 63 as the thrust surface of the crankshaft 8. The bottom surface of the large-diameter bore section 63 is precision ground to form a high-gloss friction pair. Combined with the trace oil film between the crankshaft 8 and the upper support 6, a rolling element-free thrust structure is achieved. While ensuring axial load-bearing capacity, the existing combination of the lower thrust bearing and lower support is completely eliminated, reducing production costs and weight, eliminating the risk of rolling element fatigue failure, and significantly improving the compressor's lifespan.

[0063] like Figures 1 to 3 As shown, the upper end face of the large bearing 61 is flush with the upper end face of the large outer diameter shaft section 81; and / or, the upper end face of the large bearing 61 is flush with the upper end face of the moving disc bearing 7.

[0064] The flush arrangement of the upper end face of the large bearing 61 with the upper end face of the large outer diameter shaft section 81 eliminates the axial step clearance between the upper end of the large bearing 61 and the upper end of the crankshaft 8, enabling the moving disc bearing 7 and the large bearing 61 to form a continuous and smooth support transition in the axial direction. This effectively suppresses the vibration excitation source caused by the axial step clearance, reduces fretting wear under high-speed rotation, reduces the coaxiality error between the rotation center of the moving scroll 3 and the center line of the crankshaft 8, significantly improves the meshing accuracy of the moving scroll 3 and the stationary scroll 2, reduces compression leakage, and improves volumetric efficiency.

[0065] When the upper surface of the large bearing 61 is flush with the upper surface of the moving disc bearing 7, the two together form an integrated radial bearing platform. This allows the gas force and centrifugal force on the moving scroll 3 to be directly transmitted to the upper support 6 through the two coaxial bearings, the large bearing 61 and the moving disc bearing 7, instead of being indirectly transmitted through the crankshaft journal 8. This upgrades the original indirect support mode to direct synchronous support, greatly reducing the sway amplitude and angular velocity fluctuation of the moving scroll 3, making the compression process more stable, significantly attenuating the high-frequency components in the noise spectrum, and making the overall noise characteristics closer to the silent level, which can meet the stringent requirements of high-end household air conditioners for quiet operation.

[0066] like Figures 1 to 3 as well as Figure 8 As shown, the crankshaft 8 is also provided with an oil suction hole 84 and an oil guide hole 85. The oil suction hole 84 is located at the lower end of the small outer diameter shaft section 82, the lower end of the oil guide hole 85 is connected to the oil suction hole 84, and the upper end of the oil guide hole 85 is connected to the eccentric bearing hole 83. The shaft system structure also includes an oil suction pipe 12, the upper end of which is fixedly inserted into the oil suction hole 84, and the lower end of which extends to the oil sump 13 located at the bottom of the shaft system structure.

[0067] like Figure 4 As shown, the moving scroll plate 3 also includes a high-pressure oil groove 32 and a medium-pressure drainage groove 33. One end of the high-pressure oil groove 32 extends to the eccentric bearing hole 83 to allow lubricating oil to enter.

[0068] The shaft system structure of this invention forms a self-priming oil supply path from oil sump 13 → oil suction pipe 12 → oil suction hole 84 → oil guide hole 85 → eccentric bearing hole 83 → moving scroll plate 3, etc. Utilizing the centrifugal negative pressure generated by the rotation of crankshaft 8, the lubricating oil in the bottom oil sump is actively drawn in through the oil suction pipe 12 and precisely delivered to the friction interface between the moving scroll bearing 7 and the eccentric bearing hole 83 through the oil guide hole 85, realizing an instant lubrication response of oil supply upon rotation. Especially during low-temperature start-up or low-frequency operation, it significantly shortens the oil film establishment time, avoids dry friction, and extends the service life of the shaft system structure. It solves the problems of delayed oil supply and slow oil film establishment in the prior art that rely on the upper support oil circuit or external oil pump.

[0069] like Figures 1 to 3 as well as Figure 8As shown, an upper tangential outer oil groove 86 for lubricating oil to flow into is provided on the outer circumferential surface of the large outer diameter shaft section 81. The upper tangential outer oil groove 86 extends to the upper end face of the large outer diameter shaft section 81 and is correspondingly provided with the large bearing 61; and / or, an upper tangential inner oil groove 87 for lubricating oil to flow into is provided on the inner wall surface of the eccentric bearing hole 83. The upper tangential inner oil groove 87 extends to the upper end face of the large outer diameter shaft section 81 and is correspondingly provided with the moving disc bearing 7; and / or, a lower tangential outer oil groove 88 for lubricating oil to flow into is provided on the outer circumferential surface of the small outer diameter shaft section 82. The lower tangential outer oil groove 88 is correspondingly provided with the small bearing 62. An oil passage hole 89 is also provided on the small outer diameter shaft section 82. The two ends of the oil passage hole 89 are connected to the oil guide hole 85 and the lower tangential outer oil groove 88, respectively.

[0070] The upper tangent outer oil groove 86 and upper tangent inner oil groove 87 form a multi-point oil supply network when the crankshaft rotates. The upper tangent outer oil groove 86 supplies oil to the large bearing 61, while the upper tangent inner oil groove 87 supplies oil to the moving disc bearing 7. This ensures that all friction pairs are supplied with oil synchronously without blind spots, abandoning the existing single-point oil injection mode and realizing surface contact lubrication. The oil film thickness is controllable and the distribution is uniform, which greatly reduces the bearing temperature rise, effectively avoids the carbonization failure of the lubricating oil, and extends the compressor maintenance cycle.

[0071] The coordinated design of the lower cut edge outer oil groove 88 and the oil passage hole 89 realizes a multi-purpose oil circuit reuse mechanism: the lubricating oil delivered by the oil guide hole 85 can not only supply multiple structures at its upper end, but also be diverted to the small bearing 62 through the oil passage hole 89, realizing one-time oil supply and double lubrication. Without adding an extra oil circuit, the problem of insufficient lubrication of the small bearing 62 is solved, which improves the lubrication efficiency of the entire shaft system, while reducing the total amount of lubricating oil used, reducing production costs and environmental burden.

[0072] Furthermore, the oil suction pipe 12 includes a pipe body 121 and an oil guide plate 122 disposed inside the pipe body 121. The oil guide plate 122 is a spiral plate and is interference-fitted with the inner wall surface of the pipe body 121 so as to rotate synchronously with the crankshaft 8 to draw the lubricating oil in the oil sump 13 into the oil suction hole 84.

[0073] Specifically, the distance R between the centerline of the crankshaft 8 and the centerline of the eccentric bearing hole 83 is greater than zero. The oil suction hole 84 is collinear with the centerline of the crankshaft 8, ensuring that the oil suction process is not affected by eccentric rotation and avoiding torsion, deformation, or breakage of the oil suction pipe due to eccentric force, thus ensuring reliable oil supply. The centerline of the oil guide hole 85 is offset to the side closer to the eccentric bearing hole 83 and located on the side of the centerline of the eccentric bearing hole 83 away from the centerline of the crankshaft 8. This ensures that the oil guide hole 85 is always in the high-pressure zone in the direction of centrifugal force when the crankshaft 8 rotates. The centrifugal effect enhances the oil delivery efficiency to the eccentric area, allowing the oil to automatically flow to the high-load friction area, achieving self-guided oil supply and significantly improving lubrication efficiency and response speed.

[0074] The structure of the oil suction pipe 12 with built-in oil guide plate 122 upgrades the existing passive oil suction to an active pumping mode. The oil guide plate 122 rotates synchronously with the crankshaft, forming a micro spiral pump effect. Even at low speeds or during cold starts, it can continuously deliver oil from the oil sump 13 upwards, solving the problem of delayed oil supply from the oil holes inside the crankshaft 8 at low speeds. This significantly improves the compressor's low-temperature start-up performance and meets the stringent requirements for the reliability of heat pump operation in cold regions during winter.

[0075] like Figure 1 As shown, the oil guide plate 122 is a spiral plate, and the oil guide plate 122 is interference-fitted with the inner wall of the pipe body 121 so as to rotate synchronously with the crankshaft 8 to draw the lubricating oil in the oil sump 13 into the oil suction hole 84.

[0076] The spiral-shaped oil guide plate 122 structure enables the oil suction pipe 12 to function as both an oil passage and a miniature rotary pump. Its interference fit ensures synchronous operation with the crankshaft without slippage. With each revolution, it can push a fixed volume of oil upward, overcoming the shortcomings of existing gravity or negative pressure oil suction methods that are highly dependent on speed. It can maintain stable oil supply across the entire speed range, completely eliminating lubrication gaps, providing core protection for compressors operating at full frequency and wide bandwidth, and achieving seamless lubrication from standby to full load.

[0077] Specifically, the spiral oil guide plate 122 can be made of engineering plastic or surface-hardened steel, which is shear-resistant and oil corrosion-resistant. After interference fit with the pipe body, it forms an integrated leak-free structure, avoiding the problems of easy aging and falling off of welding or bonding seals. It can improve the oil suction reliability to a lifetime maintenance-free level, significantly reducing the maintenance costs of end users and enhancing the product's market competitiveness. It is especially suitable for high-end application scenarios that are sensitive to operation and maintenance costs, such as high-end commercial multi-split air conditioners and data center cooling systems.

[0078] like Figure 1 , Figure 2 , Figure 6 and Figure 7As shown, the shaft system structure also includes: a cross slip ring 5, a first slip ring groove 31 for mounting a part of the cross slip ring 5 on the moving scroll plate 3, a second slip ring groove 68 for mounting another part of the cross slip ring 5 on the bracket cover plate 611; and / or, a sealing lubrication ring 4, the upper end face of the sealing lubrication ring 4 abutting against the moving scroll plate 3, and an annular inner flange 69 on the bracket cover plate 611, the inner wall surface of the annular inner flange 69 being flush with the mounting support bearing, an annular mounting groove 610 for mounting part of the sealing lubrication ring 4 being provided at the upper end of the annular inner flange 69, to separate the upper end of the annular inner flange 69 into a first annular end face 67 and a second annular end face 612 arranged sequentially in a direction away from the support bearing, the first annular end face 67 and the second annular end face 612 being flush with each other and both higher than the bottom surface of the annular mounting groove 610, for contacting the moving scroll plate 3 to support the moving scroll plate 3.

[0079] The shaft system structure of the present invention, by introducing structures such as an annular inner flange 69 and an annular mounting groove 610, realizes for the first time the integration of support, sealing and lubrication functions of the moving scroll plate. The first annular end face 67 and the second annular end face 612 of the bracket cover plate 611 directly contact the bottom of the moving scroll plate 3 as the main support surface, forming a "center-lifting" micro-tilting support structure, so that the moving scroll plate 3 automatically fits towards the center when subjected to gas force, realizing the "self-centering" effect.

[0080] Meanwhile, the sealing lubrication ring 4 is embedded in the annular mounting groove 610, with its upper end face abutting against the moving scroll disk 3, and its lower end face forming a sealing cavity based on the annular inner flange 69. This serves as both a barrier separating the high-pressure and low-pressure areas and a lubricating medium, allowing a small amount of lubricating oil to form a dynamic oil film between the moving scroll disk and the sealing ring. This provides a triple function of sealing, friction reduction, and heat dissipation, with more stable sealing performance. During long-term operation, even after the lubrication ring wears down, it can still be compensated for by the oil film, achieving a self-repairing seal, significantly reducing compressor leakage rate and improving volumetric efficiency and energy efficiency.

[0081] Specifically, the height difference between the upper end face of the annular inner flange 69 and the bottom surface of the annular mounting groove 610 is 0.1 mm to 2 mm.

[0082] Optionally, the height difference between the upper end face of the annular inner flange 69 and the bottom surface of the annular mounting groove 610 can be any one of 0.1mm, 0.3mm, 0.5mm, 0.8mm, 1mm, 1.3mm, 1.5mm, 1.8mm and 2mm.

[0083] like Figure 9As shown, the rotor assembly 9 includes a rotor 91 and a secondary balancing block 93 located at the end of the rotor 91 away from the upper support 6. The center of mass of the secondary balancing block 93 and the main balancing block 14 are offset by 180 degrees around the center line of the rotor 91. A rotor flow hole 911 is provided on the rotor 91 and extends through the rotor 91 along the axial direction of the rotor 91. The rotor flow hole 911 is located on the side of the secondary balancing block 93 near the center line of the rotor 91.

[0084] The shaft system structure of this invention arranges the main balance block 14 near the upper support 6, making its center of mass as close as possible to the eccentric excitation source of the moving scroll plate. This improves the axial alignment between the point of application of the balancing force and the point of application of the gas force, fundamentally eliminating the couple vibration caused by the lower balance block. The main balance block 14 and the secondary balance block 93 are arranged in a 180° opposite layout, ensuring symmetrical distribution of dynamic balance mass, reducing the vibration acceleration of the whole machine, and effectively suppressing the sharp noise peaks in the noise spectrum, thereby meeting the requirements of quiet home appliances. Among them, the main balance block 14 is located inside the upper support 6, mainly to counteract the overturning of the gas force of the moving scroll plate 3, while the secondary balance block 93 is located at the lower end of the rotor 91, specifically to counteract the centrifugal inertial force of the rotor 91 rotation. The centers of mass of the two are arranged symmetrically at 180°, forming a complete reverse compensation in space, which reduces the vibration amplitude of the whole machine, significantly better than the single balance block structure.

[0085] The rotor flow hole 911 penetrates the rotor 91 and is located inside the main balance block 14 and the auxiliary balance block 93, forming an axially continuous cooling channel for the refrigerant gas. This allows the refrigerant to flow through the interior of the rotor 91, significantly enhancing the heat dissipation efficiency of the rotor 91, preventing heat accumulation inside and causing insulation aging, reducing the temperature rise of the rotor 91, and increasing the power density of the rotor 91. It is particularly suitable for high-load scenarios such as variable frequency multi-split air conditioners and data center heat pumps.

[0086] like Figure 1 As shown, the present invention provides a compressor, including a housing 1 and a stator assembly 10, a stationary scroll 2 and a shaft system structure located inside the housing 1. The shaft system structure is the shaft system structure described above. The stator assembly 10 is sleeved on the outside of the rotor assembly 9 of the shaft system structure and is fixedly connected to the housing 1. The stationary scroll 2 and the moving scroll 3 cooperate with each other and are fixedly connected to the housing 1.

[0087] Thus, the compressor of this invention integrates all the aforementioned innovative structures into a single compressor platform for the first time, creating a "revolutionary high-efficiency, high-reliability, compact scroll compressor." Traditional compressors, due to independent optimization of each component, often suffer from the problem of "local advancement but overall lag." However, this solution achieves a synergistic improvement across the entire chain, from lubrication and support to balancing and sealing, through a systematic reconstruction of the shaft system: the main balance block is moved inward to shorten the lever arm, the bearing diameter is changed to reduce friction, the oil guide hole directly supplies the moving disc, the oil suction pipe is spiral pumped, the sealing and lubrication rings are integrated, and the rotor is balanced in two stages—each of which brings an exponential improvement to the overall performance of the machine.

[0088] The compressor of this invention reduces overall power consumption, noise level, height, and number of parts while maintaining the same displacement, thus improving assembly efficiency. It can also operate stably under extreme conditions such as low temperature, high temperature, and high frequency inverter, extending its service life. Its compact structure and excellent performance make it suitable for applications with stringent reliability and energy efficiency requirements, such as high-end commercial air conditioning, cold chain systems, and heat pumps for new energy vehicles.

[0089] As can be seen from the above description, the embodiments of the present invention achieve the following technical effects:

[0090] The shaft system structure of the present invention is applicable at least to compressors. The shaft system structure includes: a moving scroll 3 and a moving disk bearing 7 sleeved on the lower end of the moving scroll 3; a rotor assembly 9 disposed below the moving scroll 3; a crankshaft 8, including a large outer diameter shaft section 81 and a small outer diameter shaft section 82 connected sequentially from top to bottom, wherein the upper end of the large outer diameter shaft section 81 has an eccentric bearing hole 83 for mounting the moving disk bearing 7, and the rotor assembly 9 is sleeved outside the small outer diameter shaft section 82; an upper bracket 6, through which the crankshaft 8 passes, the upper bracket 6 including a bracket body 60, the bracket body 60 including a receiving cavity 66; and a main balance block 14, which is sleeved on the crankshaft 8 and located within the receiving cavity 66, wherein the center of mass of the main balance block 14 is spaced apart from the rotation axis of the crankshaft 8. Thus, the shaft system structure of the present invention fundamentally reconstructs the dynamic balance system of the compressor by embedding the main balance block 14 inside the receiving cavity 66 of the upper bracket 6 and offsetting its center of mass from the rotation axis of the crankshaft 8. The main balance block 14 is directly arranged below the moving scroll disk 3 and inside the upper bracket 6, which significantly shortens the lever arm distance between the balancing mass and the excitation source, making the balancing torque and the gas torque more coplanar and synchronously opposite in space. This greatly improves the dynamic balance accuracy of the shaft system structure, reduces the vibration amplitude and significantly reduces the noise level during operation. It solves the problem of poor balancing effect caused by the axial distance between the main balance block and the eccentric excitation source of the moving scroll disk in the prior art scroll compressor. The stability advantage is more prominent, especially under high speed or high pressure ratio conditions. It avoids the phenomenon that the main balance block in the prior art is usually set at both ends of the motor rotor, which is far away from the gas force excitation source of the moving scroll disk, resulting in the inertial force being unable to effectively counteract the high-frequency overturning torque of the moving scroll disk during the compression process, thus causing vibration and noise.

[0091] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the exemplary embodiments according to this application. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0092] Unless otherwise specifically stated, the relative arrangement, numerical expressions, and values ​​of the components and steps described in these embodiments do not limit the scope of this application. It should also be understood that, for ease of description, the dimensions of the various parts shown in the drawings are not drawn to actual scale. Techniques, methods, and devices known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and devices should be considered part of the specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not as limitations. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters in the following drawings denote similar items; therefore, once an item is defined in one drawing, it need not be further discussed in subsequent drawings.

[0093] In the description of this application, it should be understood that the orientation or positional relationship indicated by directional terms such as "front, back, up, down, left, right", "horizontal, vertical, horizontal" and "top, bottom" is usually based on the orientation or positional relationship shown in the accompanying drawings, and is only for the convenience of describing this application and simplifying the description. Unless otherwise stated, these directional terms do not indicate or imply that the device or element referred to must have a specific orientation or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation on the scope of protection of this application; the directional terms "inner" and "outer" refer to the inner and outer contours relative to the outline of each component itself.

[0094] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.

[0095] Furthermore, it should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore cannot be construed as limiting the scope of protection of this application.

[0096] The above description is merely a preferred embodiment of the present invention and is not intended to limit the invention. Various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A shafting arrangement characterised in that, At least applicable to compressors, the shaft system structure includes: The moving scroll (3) and the moving disk bearing (7) sleeved at the lower end of the moving scroll (3). The rotor assembly (9) is disposed below the moving scroll plate (3); The crankshaft (8) includes a large outer diameter shaft section (81) and a small outer diameter shaft section (82) connected sequentially from top to bottom. The upper end of the large outer diameter shaft section (81) is provided with an eccentric bearing hole (83) for installing the moving disc bearing (7). The rotor assembly (9) is sleeved on the small outer diameter shaft section (82). Upper bracket (6), the crankshaft (8) passes through the upper bracket (6), the upper bracket (6) includes a bracket body (60), the bracket body (60) includes a receiving cavity (66); The main balance block (14) is sleeved on the crankshaft (8) and located in the receiving cavity (66). The center of mass of the main balance block (14) is spaced apart from the rotation axis of the crankshaft (8).

2. The shaft system structure according to claim 1, characterized in that, The upper support (6) also includes a support cover plate (611) and two support bearings. The support cover plate (611) is disposed in the receiving cavity (66) to divide the receiving cavity (66) into an upper moving plate cavity (661) and a lower balance cavity (662). The two support bearings are respectively sleeved on the crankshaft (8). The main balance block (14) is located in the lower balance cavity (662).

3. The shafting arrangement of claim 1 wherein, The main balance block (14) includes an annular connecting sleeve (141) and an eccentric block (142) disposed on one side of the outer circumferential surface of the annular connecting sleeve (141). The annular connecting sleeve (141) is sleeved on the large outer diameter shaft section (81).

4. The shafting arrangement of claim 2 wherein, The two supporting bearings include a large bearing (61) and a small bearing (62) spaced apart from top to bottom. The large bearing (61) and the small bearing (62) are respectively installed inside the bracket cover plate (611) and the bracket body (60), and the large bearing (61) and the small bearing (62) are respectively sleeved on the outside of the large outer diameter shaft section (81) and the small outer diameter shaft section (82).

5. The shaft system structure according to claim 4, characterized in that, The upper bracket (6) has a mounting through hole in the middle. The mounting through hole includes a large-diameter hole section (63) and a small-diameter hole section (64) located at the upper and lower ends of the lower balance cavity (662). The large-diameter hole section (63) is located on the bracket cover plate (611) and is correspondingly arranged with the large outer diameter shaft section (81). The large bearing (61) is located between the large-diameter hole section (63) and the large outer diameter shaft section (81). The small-diameter hole section (64) is located on the bracket body (60) and is correspondingly arranged with the small outer diameter shaft section (82). The small bearing (62) is located between the small outer diameter shaft section (82) and the small outer diameter shaft section (82).

6. The shaft system structure according to claim 5, characterized in that, The support body (60) is provided with an oil return hole (65), one end of which extends to the outer circumferential surface of the upper support (6), and the other end of which communicates with the lower balance chamber (662). The shaft system structure also includes an oil return pipe (11), one end of which is connected to the first end of the oil return hole (65), and the other end of which extends to an oil sump (13) located at the bottom of the shaft system structure; and / or, The upper end face of the large bearing (61) is lower than the upper end of the large-diameter bore section (63); and / or, The lower end face of the small bearing (62) is higher than the lower end of the small diameter bore section (64); and / or, The bottom surface of the large-diameter bore section (63) is in frictional contact with the lower end surface of the large outer diameter shaft section (81) to serve as the thrust surface of the crankshaft (8).

7. The shaft system structure according to claim 4, characterized in that, The upper end face of the large bearing (61) is flush with the upper end face of the large outer diameter shaft section (81); and / or, the upper end face of the large bearing (61) is flush with the upper end face of the moving disc bearing (7).

8. The shaft system structure according to claim 4, characterized in that, The crankshaft (8) is also provided with an oil suction hole (84) and an oil guide hole (85). The oil suction hole (84) is located at the lower end of the small outer diameter shaft section (82). The lower end of the oil guide hole (85) is connected to the oil suction hole (84), and the upper end of the oil guide hole (85) is connected to the eccentric bearing hole (83). The shaft system structure also includes an oil suction pipe (12). The upper end of the oil suction pipe (12) is fixedly inserted into the oil suction hole (84), and the lower end of the oil suction pipe (12) extends to the oil sump (13) located at the bottom of the shaft system structure.

9. The shaft system structure according to claim 8, characterized in that, The outer circumferential surface of the large outer diameter shaft section (81) is provided with an upper tangential outer oil groove (86) for lubricating oil to flow in. The upper tangential outer oil groove (86) extends to the upper end face of the large outer diameter shaft section (81) and is correspondingly provided with the large bearing (61); and / or, The inner wall surface of the eccentric bearing hole (83) is provided with an upper tangential inner oil groove (87) for lubricating oil to flow in. The upper tangential inner oil groove (87) extends to the upper end face of the large outer diameter shaft section (81) and is correspondingly provided with the moving disc bearing (7); and / or, The outer circumferential surface of the small outer diameter shaft section (82) is provided with a lower cut edge outer oil groove (88) for lubricating oil to flow in. The lower cut edge outer oil groove (88) is provided corresponding to the small bearing (62). The small outer diameter shaft section (82) is also provided with an oil passage hole (89). The two ends of the oil passage hole (89) are respectively connected to the oil guide hole (85) and the lower cut edge outer oil groove (88).

10. The shaft system structure according to claim 8, characterized in that, The oil suction pipe (12) includes a pipe body (121) and an oil guide plate (122) disposed inside the pipe body (121). The oil guide plate (122) is a spiral plate. The oil guide plate (122) is interference-fitted to the inner wall of the pipe body (121) so that it rotates synchronously with the crankshaft (8) to draw the lubricating oil in the oil sump (13) into the oil suction hole (84).

11. The shaft system structure according to claim 2, characterized in that, The shaft system structure also includes: A cross slip ring (5), wherein the moving scroll plate (3) is provided with a first slip ring groove (31) for mounting a portion of the cross slip ring (5), and the bracket cover plate (611) is provided with a second slip ring groove (68) for mounting the other portion of the cross slip ring (5); and / or, A sealing lubrication ring (4) is provided, the upper end face of which abuts against the moving scroll plate (3). An annular inner flange (69) is also provided on the bracket cover plate (611). The inner wall surface of the annular inner flange (69) is already connected to the support bearing. An annular mounting groove (610) for installing part of the sealing lubrication ring (4) is provided at the upper end of the annular inner flange (69) to separate the upper end of the annular inner flange (69) into a first annular end face (67) and a second annular end face (612) arranged sequentially in a direction away from the support bearing. The first annular end face (67) and the second annular end face (612) are flush and both higher than the bottom surface of the annular mounting groove (610) to contact the moving scroll plate (3) to support the moving scroll plate (3).

12. The shaft system structure according to any one of claims 1 to 11, characterized in that, The rotor assembly (9) includes a rotor (91) and a secondary balancing block (93) located at one end of the rotor (91) away from the upper support (6). The secondary balancing block (93) and the main balancing block (14) are offset by 180 degrees around the center line of the rotor (91). The rotor (91) has a rotor flow hole (911) that extends through the rotor (91) along the axial direction of the rotor (91) and is located on the side of the auxiliary balance block (93) near the center line of the rotor (91).

13. A compressor, characterized in that, The device includes a housing (1) and a stator assembly (10), a stationary scroll plate (2) and a shaft system structure located within the housing (1). The shaft system structure is the shaft system structure according to any one of claims 1 to 12. The stator assembly (10) is sleeved outside the rotor assembly (9) of the shaft system structure and is fixedly connected to the housing (1). The stationary scroll plate (2) cooperates with the moving scroll plate (3) and is fixedly connected to the housing (1).

Images