compressor

Abstract

This application provides a compressor, including a housing and a crankshaft, a moving scroll, and a stationary scroll respectively disposed therein. The moving scroll meshes with the stationary scroll. An eccentric receiving groove is provided at the end of the crankshaft, parallel to the centerline of the crankshaft. At least a portion of the moving scroll is inserted into the eccentric receiving groove, and a first bearing is disposed between the moving scroll and the eccentric receiving groove. The compressor also includes a support frame located below the moving scroll, with an installation channel provided within the support frame. At least a portion of the crankshaft passes through the installation channel, and a second bearing is sleeved on the crankshaft, fitting against the wall of the installation channel. A lubrication return portion is provided within the installation channel, opposite to the outer peripheral wall of at least a portion of the crankshaft. Along the radial direction of the crankshaft, the orthographic projection plane of the first bearing coincides with the orthographic projection plane of the second bearing. This solves the technical problems of redundant shaft structure, dispersed lubrication paths, and poor motion stability in related scroll compressors.

Description

Technical Field

[0001] This application relates to the field of compressor technology, and more specifically, to a compressor. Background Technology

[0002] Traditional scroll compressors generally use a coaxial, equal-diameter double bearing structure as the upper support to simultaneously bear the radial load of the moving scroll and the rotational support of the crankshaft. The eccentric part of the crankshaft and the center line of the moving scroll bearing often have axial misalignment, and the lubrication system relies on an independent oil return pipe to guide the lubricating oil from the compression chamber back to the oil sump. Axial thrust is achieved by a separate thrust bearing or lower support.

[0003] However, this dual-bearing structure results in an excessively large motor side shaft diameter and an increased overall height, which not only increases material costs and rotational inertia but also raises frictional power consumption. At the same time, the independent oil return pipe structure is prone to lubrication interruption due to oil clogging or seal failure, reducing system reliability. In addition, the lack of horizontal alignment between the moving scroll bearing and the crankshaft eccentricity causes asymmetrical force on the shaft system and increased deflection, leading to wobbling and vibration of the moving scroll, which affects compression efficiency and durability. Summary of the Invention

[0004] The main objective of this application is to provide a compressor that solves the technical problems of redundant shaft structure, dispersed lubrication paths, and poor motion stability of scroll compressors in the related art.

[0005] To achieve the above objectives, according to one aspect of this application, a compressor is provided, including a housing and a crankshaft, a moving scroll, and a stationary scroll respectively disposed therein, the moving scroll meshing with the stationary scroll, an eccentric receiving groove provided at the end of the crankshaft, the center line of the eccentric receiving groove being parallel to the center line of the crankshaft, at least a portion of the moving scroll being inserted into the eccentric receiving groove, and a first bearing being disposed between the moving scroll and the eccentric receiving groove;

[0006] The compressor also includes a support frame located below the moving scroll plate. An installation channel is provided inside the support frame, and at least a portion of the crankshaft passes through the installation channel. A second bearing is sleeved on the crankshaft, and the second bearing is in contact with the wall of the installation channel. A lubrication return section is provided inside the installation channel, located below the second bearing. At least a portion of the outer peripheral wall of the crankshaft is opposite to the lubrication return section. In the radial direction of the crankshaft, the orthographic projection of the first bearing on the inner wall of the installation channel coincides with the orthographic projection of the second bearing on the inner wall of the installation channel.

[0007] Furthermore, an oil supply channel is provided inside the crankshaft, one end of which is connected to an oil sump inside the housing, and the other end of which is connected to an eccentric receiving groove; a first lubrication part is provided on the crankshaft, which is located on the groove wall of the eccentric receiving groove to lubricate the first bearing.

[0008] Furthermore, the first lubrication part includes: a first oil passage groove disposed on the groove wall of the eccentric receiving groove; the first oil passage groove extends along the axial direction of the crankshaft, and the outer peripheral surface of the first bearing is disposed opposite to the first oil passage groove, so that a portion of the lubricating oil flows into the first oil passage groove through the eccentric receiving groove.

[0009] Furthermore, the first oil passage groove extends from the bottom surface of the eccentric receiving groove to the top end face of the crankshaft.

[0010] Furthermore, a second lubrication part is provided on the outer circumferential surface of the crankshaft, which is connected to the first lubrication part so as to lubricate the second bearing through the second lubrication part.

[0011] Furthermore, the second lubrication part includes: a second oil passage groove disposed on the outer peripheral surface of the crankshaft; extending along the axial direction of the crankshaft, the inner peripheral surface of the second bearing is opposite to the second oil passage groove, so that after a portion of the lubricating oil flows through the first lubrication part, it flows into the second oil passage groove through the top end face of the crankshaft.

[0012] Furthermore, the installation channel includes a first channel segment and a second channel segment that are connected to each other. The first channel segment is located above the second channel segment. The crankshaft includes a first shaft segment and a second shaft segment that are connected to each other. The diameter of the first shaft segment is larger than the diameter of the second shaft segment. The first shaft segment is disposed within the first channel segment. The eccentric receiving groove is located on the first shaft segment. The lubrication return oil part and the second shaft segment are disposed within the second channel segment.

[0013] Furthermore, an oil guide groove extending circumferentially is provided on the outer peripheral wall of the second shaft section, and an oil passage hole extending radially is provided inside the second shaft section. The oil guide groove is connected to the oil supply channel through the oil passage hole.

[0014] The lubrication return section includes: at least two third oil passage grooves, which are spaced apart on the inner wall of the second channel section along the circumference of the installation channel. One end of each third oil passage groove is connected to the second oil passage groove and the oil passage guide groove, respectively, and the other end of each third oil passage groove extends out of the second channel section and is connected to the oil sump.

[0015] The third oil passage grooves are arranged in a spiral pattern, or the third oil passage grooves extend axially along the second channel section.

[0016] Furthermore, the lubrication return section also includes: at least two fourth oil passage grooves, which are disposed within the second channel section and are disposed in a one-to-one correspondence with at least two third oil passage grooves. One end of each third oil passage groove is connected to the corresponding fourth oil passage groove. At least two fourth oil passage grooves are disposed opposite to and connected to the oil passage guide groove. Each fourth oil passage groove is connected to the second oil passage groove.

[0017] Furthermore, the number of the third oil passage grooves is N; along the radial direction of the second channel segment, the third oil passage groove has a first cross-sectional area S1, the second oil passage groove has a second cross-sectional area S2, and along the axial direction of the second channel segment, the oil passage hole has a third cross-sectional area S3, wherein NS1>S2+S3, and N≥2;

[0018] And / or, the third oil passage groove has a maximum tangential distance L; the second channel segment has a preset inner diameter D; wherein, 5NL<πD, N≥2.

[0019] Furthermore, the bottom of the first shaft segment has a first thrust surface, and a stop block is provided in the mounting channel. The stop block extends from at least a portion of the channel wall of the mounting channel toward the center line of the mounting channel. The stop block surrounds the second channel segment, and the top of the stop block has a second thrust surface. At least a portion of the first thrust surface and the second thrust surface are in contact.

[0020] Furthermore, the compressor also includes: a stator and a rotor assembly, disposed within the housing, the rotor assembly being sleeved on the crankshaft, and the stator being sleeved on the rotor assembly; wherein, a first balance block and a second balance block are respectively disposed at both ends of the rotor assembly along the axial direction, the first balance block being disposed on the first end face of the rotor assembly, and the second balance block being disposed on the second end face of the rotor assembly, and the first balance block and the second balance block being staggered along the axial direction of the rotor assembly.

[0021] The present application provides a compressor, including a housing and a crankshaft, a moving scroll, and a stationary scroll respectively disposed therein. The moving scroll meshes with the stationary scroll. An eccentric receiving groove is provided at the end of the crankshaft. The center line of the eccentric receiving groove is parallel to the center line of the crankshaft. At least a portion of the moving scroll is inserted into the eccentric receiving groove. A first bearing is provided between the moving scroll and the eccentric receiving groove.

[0022] The compressor also includes a support frame located below the moving scroll plate. An installation channel is provided within the support frame, through which at least a portion of the crankshaft passes. A second bearing is fitted onto the crankshaft, and the second bearing is in contact with the wall of the installation channel. A lubrication return section is provided within the installation channel, located below the second bearing. At least a portion of the outer peripheral wall of the crankshaft is positioned opposite the lubrication return section. Furthermore, along the radial direction of the crankshaft, the orthographic projection of the first bearing onto the inner wall of the installation channel coincides with the orthographic projection of the second bearing onto the inner wall of the installation channel.

[0023] By aligning the orthographic projections of the first and second bearings on the inner wall of the mounting channel, their coaxial arrangement in the radial direction is achieved, completely eliminating the traditional double-layer concentric bearing structure. This significantly reduces the axial dimension of the support frame and the motor side shaft diameter, improving the overall miniaturization and reducing material costs and rotational inertia. Furthermore, the second bearing directly conforms to the wall of the mounting channel to form a sliding pair, achieving self-circulating lubrication in conjunction with the lower lubrication return section. This avoids the additional frictional losses caused by traditional rolling bearings or double bearing stacking, effectively reducing shaft rotational power consumption, improving overall energy efficiency, and solving the technical problems of redundant shaft structure, dispersed lubrication paths, and poor motion stability in scroll compressors in related technologies. Attached Figure Description

[0024] The accompanying drawings, which form part of this application, are used to provide a further understanding of this application. The illustrative embodiments and descriptions of this application are used to explain this application and do not constitute an undue limitation of this application. In the drawings:

[0025] Figure 1 A cross-sectional view is shown, illustrating an embodiment of the compressor according to this application;

[0026] Figure 2 A schematic diagram of the crankshaft provided according to an embodiment of the compressor of this application is shown;

[0027] Figure 3 It shows Figure 2 A schematic diagram of the structure from a Z-axis perspective;

[0028] Figure 4 It shows Figure 3 Enlarged view of section C;

[0029] Figure 5 A cross-sectional view of a first embodiment of a support frame provided according to an embodiment of the compressor of this application is shown;

[0030] Figure 6 It shows Figure 5 A cross-sectional view from the perspective of the AA (American Academy of Sciences).

[0031] Figure 7 It shows Figure 6 Enlarged view of section B;

[0032] Figure 8 A cross-sectional view of a second embodiment of the support frame provided according to an embodiment of the compressor of this application is shown;

[0033] Figure 9 A schematic diagram of the rotor assembly provided in an embodiment of the compressor according to this application is shown;

[0034] Figure 10A schematic diagram of the structure of the moving scroll plate provided in an embodiment of the compressor according to this application is shown.

[0035] The above figures include the following reference numerals:

[0036] 10. Shell;

[0037] 11. Inhalation tube;

[0038] 12. First sealing part;

[0039] 13. Cross slip ring;

[0040] 14. Exhaust pipe;

[0041] 15. Oil suction pipe;

[0042] 16. Oil tank;

[0043] 20. Crankshaft;

[0044] 21. Eccentric receiving tank;

[0045] 22. Oil supply channel;

[0046] 23. First lubrication section; 231. First oil passage groove;

[0047] 24. Second lubrication section; 241. Second oil passage groove;

[0048] 25. Lubrication return section; 251. Third oil passage groove; 252. Fourth oil passage groove;

[0049] 26. First shaft segment; 261. First thrust surface;

[0050] 27. Second axle segment;

[0051] 28. Oil guide groove;

[0052] 29. Oil passage hole;

[0053] 30. Moving vortex disk;

[0054] 31. High-pressure oil tank;

[0055] 32. Medium-pressure diversion channel;

[0056] 33. Scroll disk cross-shaped slip ring groove;

[0057] 40. Static vortex disk;

[0058] 50. First bearing;

[0059] 60. Support frame; 61. Installation channel; 610. First channel section; 611. Second channel section;

[0060] 62. Support end face;

[0061] 63. Support cross-shaped slip ring groove;

[0062] 64. Second sealing part;

[0063] 65. Stop block; 651. Second thrust surface;

[0064] 70. Second bearing;

[0065] 80. Stator;

[0066] 90. Rotor assembly;

[0067] 91. Rotor flow hole;

[0068] 92. First balancing block;

[0069] 93. The second balancing block. Detailed Implementation

[0070] It should be noted that, unless otherwise specified, the embodiments and features described in this application can be combined with each other. This application will now be described in detail with reference to the accompanying drawings and embodiments.

[0071] Please refer to Figures 1 to 10 As shown, the technical solution of this application provides a compressor, including a housing 10 and a crankshaft 20, a moving scroll 30, and a stationary scroll 40 respectively disposed therein. The moving scroll 30 meshes with the stationary scroll 40. An eccentric receiving groove 21 is provided at the end of the crankshaft 20, and the center line of the eccentric receiving groove 21 is parallel to the center line of the crankshaft 20. At least a portion of the moving scroll 30 is inserted into the eccentric receiving groove 21, and a first bearing 50 is disposed between the moving scroll 30 and the eccentric receiving groove 21. The compressor also includes a support frame 60, which is located below the moving scroll 30. An installation channel 61 is provided inside the crankshaft 20, at least a portion of which passes through the installation channel 61. A second bearing 70 is fitted onto the crankshaft 20, and the second bearing 70 is in contact with the channel wall of the installation channel 61. A lubrication return oil part 25 is provided inside the installation channel 61, and the lubrication return oil part 25 is located below the second bearing 70. At least a portion of the outer peripheral wall of the crankshaft 20 is opposite to the lubrication return oil part 25. In the radial direction of the crankshaft 20, the orthographic projection plane of the first bearing 50 on the inner wall of the installation channel 61 coincides with the orthographic projection plane of the second bearing 70 on the inner wall of the installation channel 61.

[0072] By aligning the orthographic projections of the first bearing 50 and the second bearing 70 on the inner wall of the mounting channel 61, they are arranged coaxially in the radial direction, completely eliminating the traditional double-layer concentric bearing structure. This significantly reduces the axial dimension of the support frame 60 and the motor side shaft diameter, improving the overall miniaturization and reducing material costs and rotational inertia. Furthermore, the second bearing 70 directly conforms to the wall of the mounting channel 61 to form a sliding pair, achieving self-circulating lubrication in conjunction with the lower lubrication return section 25. This avoids the additional frictional losses caused by traditional rolling bearings or double bearing stacking, effectively reducing shaft rotational power consumption, improving overall energy efficiency, and solving the technical problems of redundant shaft structure, dispersed lubrication paths, and poor motion stability in scroll compressors in related technologies.

[0073] Furthermore, by eliminating the lower support ring structure, costs are reduced while the compressor height can be significantly lowered. Additionally, the upper bracket sliding bearing (second bearing 70) + spiral oil groove structure (lubrication return section 25) further reduces bearing friction power consumption, shrinks the motor side shaft diameter, and lowers energy efficiency and cost. The upper bracket thrust groove and multi-oil groove structure allow all return oil to pass through the main bearing, while eliminating the return oil pipe structure, further reducing energy efficiency and cost and improving reliability.

[0074] In this embodiment, an oil supply channel 22 is provided inside the crankshaft 20. One end of the oil supply channel 22 is connected to the oil sump 16 inside the housing 10, and the other end of the oil supply channel 22 is connected to the eccentric receiving groove 21. A first lubrication part 23 is provided on the crankshaft 20. The first lubrication part 23 is located on the groove wall surface of the eccentric receiving groove 21 to lubricate the first bearing 50.

[0075] The lubricating oil is directly delivered from the oil sump 16 to the eccentric receiving groove 21 area where the moving scroll plate 30 bearing is located through the internal oil supply channel 22 of the crankshaft 20. This avoids the problems of long, high-resistance, and easy-to-clogging oil supply paths associated with traditional external oil circuits or indirect seepage, ensuring precise, stable, and timely supply of lubricant to the friction pairs, significantly improving the lubrication reliability and lifespan of the first bearing 50. Furthermore, the lubricating oil acts directly on the contact surface of the high-speed rotating first bearing 50, forming a stable oil film, effectively reducing the coefficient of friction and temperature rise, suppressing the risk of material wear or burning caused by local overheating, and improving the operating stability of the compressor under high-load conditions.

[0076] In this embodiment, the first lubrication part 23 includes a first oil passage groove 231, which is disposed on the groove wall of the eccentric receiving groove 21. The first oil passage groove 231 extends along the axial direction of the crankshaft 20, and the outer peripheral surface of the first bearing 50 is disposed opposite to the first oil passage groove 231 so that a portion of the lubricating oil flows into the first oil passage groove 231 through the eccentric receiving groove 21 to lubricate the first bearing 50.

[0077] The first oil passage groove 231 extending axially forms a continuous lubricating oil channel, which makes the lubricating oil evenly distributed along the entire axial length of the bearing. This avoids the problems of uneven lubrication and local dry friction caused by traditional point or local oil supply, significantly reduces the bearing wear rate, and extends the service life.

[0078] The first oil passage groove 231 structure utilizes the centrifugal force generated when the crankshaft 20 rotates and the oil pressure in the eccentric receiving groove 21 to actively guide the lubricating oil to the bearing friction area. No additional pressure supply device is required. The structure has a passive response and a rapid response, making it especially suitable for the operating environment of compressors with high speed and large dynamic load changes, and the lubrication response is more timely.

[0079] In this embodiment, the first oil-passing groove 231 extends from the bottom surface of the eccentric receiving groove 21 to the top end face of the crankshaft 20.

[0080] This allows the lubricating oil to evenly cover the upper and lower end faces and the entire outer peripheral friction zone of the first bearing 50 along the entire axial direction, preventing localized dry friction at the upper / lower ends of the first bearing 50 due to insufficient lubrication. Especially during compressor start-up, shutdown, or vertical installation, a stable oil film can be maintained, significantly improving the bearing's anti-wear performance and operational reliability. After escaping from the upper end of the first oil passage groove 231, the lubricating oil can directly enter the compression chamber between the moving scroll plate 30 and the stationary scroll plate 40, forming a thin oil film to assist in sealing and reduce high-pressure gas leakage. Simultaneously, oil mist enters the system with the exhaust gas, participating in motor cooling and internal component lubrication, achieving multiple uses for one oil and improving the overall lubrication efficiency of the system.

[0081] In this embodiment, a second lubrication part 24 is provided on the outer peripheral surface of the crankshaft 20. The second lubrication part 24 is connected to the first lubrication part 23 so as to lubricate the second bearing 70 through the second lubrication part 24.

[0082] The above configuration allows the same stream of lubricating oil supplied from the oil sump 16 through the internal oil supply channel 22 of the crankshaft 20 to simultaneously flow to two key friction pairs: the first bearing 50 (the bearing of the moving scroll 30) and the second bearing 70 (the radial support bearing of the crankshaft 20). The second bearing 70, as the main radial support point of the crankshaft 20 within the mounting channel 61 of the support frame 60, bears the rotational inertia force and the lateral load transmitted by the moving scroll 30 for extended periods. The lubricating oil is guided from the first lubrication section 23 to the surface of the second bearing 70 via the second lubrication section 24, continuously forming a stable oil film. This effectively reduces frictional power consumption, suppresses temperature rise, reduces journal wear and vibration, improves shaft rotational accuracy, further suppresses shaft deflection, and ensures high stability of the moving scroll 30's movement.

[0083] In this embodiment, the second lubrication part 24 includes a second oil passage groove 241, which is disposed on the outer peripheral surface of the crankshaft 20. Extending along the axial direction of the crankshaft 20, the inner peripheral surface of the second bearing 70 is opposite to the second oil passage groove 241, so that after a portion of the lubricating oil flows through the first lubrication part 23, it flows into the second oil passage groove 241 through the top end face of the crankshaft 20.

[0084] After the lubricating oil completes the lubrication of the first bearing 50, it naturally flows along the top end face of the crankshaft 20 to the second oil groove 241 due to gravity and the centrifugal force generated by the high-speed rotation of the crankshaft 20. There is no need for an oil pump, throttle valve or independent channel control, which effectively avoids the problem of uneven oil supply or insufficient oil quantity caused by oil pressure fluctuations in traditional pressure-driven oil supply.

[0085] Furthermore, the second oil groove 241 extends axially, covering the entire contact length of the second bearing 70, so that the lubricating oil forms a continuous oil film along the inner circumferential surface of the bearing, effectively reducing the friction coefficient and temperature rise between the journal and the bearing hole, suppressing the risk of pitting, scratching or seizing caused by local dry friction, significantly reducing shaft deflection, and ensuring high precision and low vibration of the eccentric motion of the moving scroll 30.

[0086] Lubricating oil path: Oil sump 16 → Oil supply channel 22 inside crankshaft 20 → First oil passage groove 231 (lubricating the moving disc bearing) → Overflow from the top surface of crankshaft 20 → Second oil passage groove 241 (lubricating the support bearing of crankshaft 20) → Lower lubrication return section 25 → Oil sump 16. In this way, two critical bearings are lubricated through a single main oil path, completely eliminating the need for traditional independent oil supply holes, branch oil pipes, and oil needles. This simplifies the system, reduces leakage points, improves assembly efficiency, and significantly reduces manufacturing costs.

[0087] In this embodiment, the mounting channel 61 includes a first channel segment 610 and a second channel segment 611 that are connected to each other. The first channel segment 610 is located above the second channel segment 611. The crankshaft 20 includes a first shaft segment 26 and a second shaft segment 27 that are connected to each other. The diameter of the first shaft segment 26 is larger than the diameter of the second shaft segment 27. The first shaft segment 26 is disposed in the first channel segment 610. The eccentric receiving groove 21 is located on the first shaft segment 26. The lubrication return oil part 25 and the second shaft segment 27 are disposed in the second channel segment 611.

[0088] The first channel section 610, in conjunction with the large-diameter first shaft section 26, provides high-rigidity radial support to withstand the high gas force and centrifugal force (the main load) generated when the moving scroll plate 30 rotates. The second channel section 611, in conjunction with the small-diameter second shaft section 27, only needs to bear the rotational inertia force and axial thrust of the crankshaft 20, requiring lower radial stiffness and allowing for a more compact design. This avoids increased frictional power consumption or assembly stress concentration, significantly improving the smoothness of shaft system operation and its resistance to deflection.

[0089] In traditional scroll compressors, to ensure consistent support, the upper and lower bearings are often designed with the same diameter, resulting in an excessively large radial dimension of the upper support and a bulky structure. This application's solution utilizes a design with a larger upper diameter shaft section and a smaller lower diameter shaft section, along with a stepped channel. This allows the larger diameter shaft section to cover only the 30mm load area of ​​the moving scroll plate, without extending to the full shaft length. Meanwhile, the smaller diameter shaft section can be significantly reduced in diameter to directly fit the rotor's inner bore, allowing the motor rotor to be closer to the upper support, shortening the cantilever length, and improving the overall shaft space utilization.

[0090] like Figure 5 and Figure 8 As shown, in this embodiment, an oil guide groove 28 extending circumferentially is provided on the outer peripheral wall of the second shaft section 27, and an oil passage hole 29 extending radially is provided inside the second shaft section 27. The oil guide groove 28 is connected to the oil supply channel 22 through the oil passage hole 29. The lubrication return oil section 25 includes at least two third oil passage grooves 251. At least two third oil passage grooves 251 are spaced apart on the inner wall of the second channel section 611 along the circumferential direction of the mounting channel 61. One end of each third oil passage groove 251 is connected to the second oil passage groove 241 and the oil guide groove 28, respectively, and the other end of each third oil passage groove 251 extends out of the second channel section 611 and is connected to the oil sump 16. The third oil passage grooves 251 are arranged in a spiral, or the third oil passage grooves 251 extend axially along the second channel section 611.

[0091] Lubricating oil path: oil supply channel 22 (inside crankshaft 20) → radial oil passage hole 29 (connecting to the second shaft section 27) → circumferential oil guide groove 28 (arranged along the circumference of the shaft section) → third oil passage groove 251 → return oil to oil sump 16. This forms a complete lubrication closed loop of "axial oil supply → circumferential uniform distribution → radial guidance → gravity return oil". This breaks through the traditional single-point oil supply and local lubrication mode, achieving uniform lubrication of the second bearing 70 along its entire length and circumference, significantly reducing the risk of local dry friction.

[0092] When the third oil passage groove 251 adopts a spiral structure (consistent with the rotation direction of the crankshaft 20, conforming to the right-hand rule):

[0093] The rotation generates an oil pumping effect: the third oil passage groove 251 acts like a miniature spiral pump, using centrifugal force to actively draw lubricating oil from the bearing friction area axially downwards to the oil sump 16.

[0094] Prevent oil stagnation or accumulation: Avoid the accumulation of lubricating oil at the bottom of the bearing, which can lead to excessive oil mist, oil churning loss, or motor insulation risks;

[0095] Improved oil return speed and thoroughness: Especially under conditions of frequent compressor start-stop, tilted installation, or high speed operation, the spiral structure ensures rapid and residue-free oil discharge, significantly improving system reliability.

[0096] If an axial straight groove arrangement is adopted (extending axially along the second channel segment 611):

[0097] The process is simpler and the cost is lower; it is suitable for commercial compressors that operate at low speeds, high loads, and for long periods of time; and it enhances flexibility.

[0098] At least two third oil passage grooves 251 (preferably 3-4) are symmetrically distributed circumferentially; the lubricating oil return path is evenly distributed to avoid uneven shaft stress and eccentric vibration caused by unilateral oil return; in coordination with the rotor balance block arrangement, the overall dynamic balance performance is further optimized, noise and bearing wear are reduced, the overall machine life is extended, and the traditional oil return pipe is completely eliminated.

[0099] In this embodiment, the lubrication return section 25 further includes at least two fourth oil passage grooves 252. The at least two fourth oil passage grooves 252 are disposed in the second channel section 611 and are disposed in a one-to-one correspondence with at least two third oil passage grooves 251. One end of each third oil passage groove 251 is connected to the corresponding fourth oil passage groove 252. The at least two fourth oil passage grooves 252 are disposed opposite to the oil passage guide groove 28 and are connected to the oil passage guide groove 28. Each fourth oil passage groove 252 is connected to the second oil passage groove 241.

[0100] In this way, the fourth oil passage groove 252 is directly connected to the oil passage guide groove 28, allowing some of the lubricating oil to flow directly into the fourth oil passage groove 252 after friction on the surface of the second bearing 70, and then flow back to the oil sump 16 from the corresponding third oil passage groove 251. This path eliminates the traditional oil return pipe structure, shortens the oil flow path, and reduces oil return resistance, which is especially advantageous under low speed and high viscosity oil conditions. Furthermore, the oil flowing through the oil hole 29 flows into at least two third oil passage grooves 251 through the oil passage guide groove 28, which can simultaneously lubricate the crankshaft 20, and the lubricated oil flows back to the oil sump 16 under gravity. At the same time, the oil flowing down from the bearing friction area → fourth oil passage groove 252 → third oil passage groove 251 → oil sump 16 forms a local oil circulation feedback mechanism, which helps to maintain the bearing temperature stability and suppress local overheating.

[0101] like Figure 4 and Figure 7 As shown, in this embodiment, the number of third oil passage grooves 251 is N; along the radial direction of the second channel segment 611, the third oil passage groove 251 has a first cross-sectional area S1, the second oil passage groove 241 has a second cross-sectional area S2, and along the axial direction of the second channel segment 611, the oil passage hole 29 has a third cross-sectional area S3, wherein NS1>S2+S3, and N≥2.

[0102] The above configuration requires that the total flow capacity of the system's oil return channels be strictly greater than the total amount of oil supplied by the lubrication system to the bearing. This ensures that all lubricating oil entering the friction zone of the second bearing 70 from the oil supply paths (S2, S3) can be discharged promptly and completely; preventing lubricating oil from accumulating, stagnating, forming an excessively thick oil film, or spraying oil mist in the bearing area; and avoiding fatal risks such as "oil pressure increase → seal failure → oil leakage into the motor cavity" caused by poor oil return.

[0103] like Figure 6 and Figure 7 As shown, in this embodiment, the number of third oil-passing grooves 251 is N; the third oil-passing groove 251 has a maximum tangential distance L; the second channel segment 611 has a preset inner diameter D; wherein, 5NL < πD, N ≥ 2.

[0104] To ensure lubrication of the spiral oil grooves on the support frame 60, the spiral grooves cannot be too large or too numerous. Sufficient support surface must be ensured to improve oil return efficiency. Blindly increasing the number or depth of grooves will lead to insufficient strength in the bearing support area. Thus, the solution in this application precisely sets the limit number and size of grooves by 5NL<πD to achieve sufficient oil return channels and sufficient structural strength.

[0105] In this embodiment, the bottom of the first shaft segment 26 has a first thrust surface 261, and a stop block 65 is provided in the mounting channel 61. The stop block 65 extends from at least a portion of the channel wall of the mounting channel 61 toward the center line of the mounting channel 61. The stop block 65 forms a second channel segment 611, and the top of the stop block 65 has a second thrust surface 651. The first thrust surface 261 and at least a portion of the second thrust surface 651 are in contact.

[0106] In traditional structures, axial thrust is transmitted through multiple stages via bearing raceways, cages, outer rings, and lower supports, resulting in elastic deformation, clearance accumulation, and frictional losses. In this application, the first thrust surface 261 and the second thrust surface 651 are in direct metal-to-metal contact with a controllable contact area. The axial load is directly transmitted to the support structure via a rigid force transmission path, effectively suppressing axial movement and micro-vibration of the moving scroll 30, significantly improving compression efficiency and operational stability.

[0107] Furthermore, the second thrust surface 651 of the stop block is not only a pressure-bearing surface, but also the starting point of the oil return channel. In this application, the second thrust surface 651 is provided with a thrust oil discharge groove (fourth oil passage groove 252), which is connected to the third oil passage groove 251. After the lubricating oil flows out from the friction pair between the first thrust surface 261 and the second thrust surface 651, it directly enters the oil discharge groove (fourth oil passage groove 252) → spiral oil groove (third oil passage groove 251) → oil pool 16. This achieves coordinated management of "friction heat + lubricating oil + axial load" in the same area, avoiding excessive temperature rise, oil film rupture, and scratch wear caused by oil accumulation on the thrust surface.

[0108] In this embodiment, the compressor further includes a stator 80 and a rotor assembly 90, which are disposed within the housing 10. The rotor assembly 90 is sleeved on the crankshaft 20, and the stator 80 is sleeved on the rotor assembly 90. A first balance block 92 and a second balance block 93 are respectively disposed at both ends of the rotor assembly 90 along the axial direction. The first balance block 92 is disposed on the first end face of the rotor assembly 90, and the second balance block 93 is disposed on the second end face of the rotor assembly 90. The first balance block 92 and the second balance block 93 are staggered along the axial direction of the rotor assembly 90.

[0109] The rotor assembly 90 is coaxially fitted to the outer periphery of the second shaft section 27 of the crankshaft 20 by interference fit or heat fitting, so as to realize the efficient transmission of motor torque to the crankshaft 20; the stator 80 is fixed to the inner wall of the housing 10, forming a uniform air gap with the rotor assembly 90 to ensure stable output of electromagnetic force.

[0110] To balance the inertial centrifugal force generated by the eccentric structure (eccentricity R) during high-speed rotation of the crankshaft 20, a first balance block 92 and a second balance block 93 are respectively provided on the two axial end faces of the rotor assembly 90, forming a balance system with double-ended axial opposition and spatially staggered arrangement. Specifically, the first balance block 92 is arranged around the multiple rotor flow holes 91 on the rotor assembly 90.

[0111] In this application, the workflow is as follows:

[0112] The lubricating oil pumped from the oil tank 16 reaches the eccentric receiving groove 21 through the oil supply channel 22, which is the bottom of the first bearing 50. Part of the lubricating oil enters the compression chamber inside the pump body through the gap of the PTFE sealing ring in the high-pressure oil groove 31 of the moving scroll 30 and the first sealing part 12 at the bottom of the moving scroll 30 for lubrication. The oil-gas mixture in the compression chamber is discharged through the exhaust hole in the middle of the stationary scroll 40 and enters the compressor cavity. Then, the lubricating oil is separated by the oil-gas separation structure inside the compressor and flows to the bottom of the oil tank 16 through the gap inside the motor. Another part of the lubricating oil lubricates the gap of the second bearing 70 through the first oil passage groove 231 and the second oil passage groove 241. After flowing downward through the second oil passage groove 241, it flows to the bottom of the oil tank 16 in sequence through the fourth oil passage groove 252 and the third oil passage groove 251.

[0113] Figure 1In the compressor structure of this application, the high-pressure lubricating oil of the compressor is located in the oil sump 16 at the bottom of the compressor. The compressor motor drives the crankshaft 20 to rotate, and at the same time drives the oil suction pipe 15 located at the bottom of the crankshaft 20 to rotate. The oil suction pipe 15 draws the lubricating oil located at the bottom of the compressor into the bottom of the moving scroll 30 through the oil supply channel 22 of the crankshaft 20. The lubricating oil enters the end face of the moving and stationary scrolls 40 through the central oil hole of the moving scroll 30 for lubrication, and enters the support frame 60 through the PTFE gap (first sealing part 12) for lubrication. Excess lubricating oil returns to the bottom of the oil sump 16 through the return oil pipe. The top of the housing is provided with an air suction pipe 11 and the side is provided with an exhaust pipe 14. Unlike conventional structures, the crankshaft 20 has cut edges on both the inner and outer sides of its top, allowing the high-pressure lubricating oil at the bottom of the moving scroll 30 to pass through the outer side of the moving scroll 30 bearing (first bearing 50) and the support frame 60 bearing (second bearing 70). This allows the lubricating oil to reach the PTFE, and excess lubricating oil to reach the return oil pipe and the top of the support frame 60 bearing (second bearing 70).

[0114] Figure 2 The crankshaft 20 structure of this application consists of a first shaft segment 26 and a second shaft segment 27. The first shaft segment 26 and the second shaft segment 27 are coaxially distributed but have different shaft diameters. An eccentric receiving groove 21 is formed at the center of the end with the larger shaft diameter (first shaft segment 26), and the distance between the center of the eccentric receiving groove 21 and the center of the first shaft segment 26 is the eccentricity R. A first bearing 50 is fitted into the eccentric receiving groove 21. A second bearing 70 is fitted into the first shaft segment 26, and the end with the smaller shaft diameter (second shaft segment 27)... 27) The rotor assembly 90 is interference-fitted with the second shaft section 27 of the crankshaft 20 by heat fitting or cold pressing. The bottom oil suction pipe 15 is interference-fitted into the bottom of the crankshaft 20. An oil guide plate (not shown) is provided inside the oil suction pipe 15. The oil guide plate is a spiral thin plate. It is interference-fitted inside the oil suction pipe 15. The spiral rotation brings the bottom lubricating oil into the inner hole of the crankshaft 20 and supplies oil upward. The bottom surface of the large end of the shaft diameter serves as the thrust surface of the crankshaft 20 and makes frictional contact with the support frame 60.

[0115] Figure 5 and Figure 8 The support frame 60 structure of this application includes a support end face 62, with the bottom of the moving scroll disk 30 substrate contacting the support end face 62 to support the axial movement of the moving scroll disk 30; a cross slip ring 13 is installed in a groove to restrict radial movement; a PTFE sealing ring is installed in the second sealing part 64 of the support frame 60, dividing the bottom of the moving scroll disk 30 into two areas, an inner and an outer ring, where the inner ring is high pressure and the outer ring is low pressure. High-pressure oil leaks from the PTFE into the low-pressure area to lubricate the internal parts of the upper support; the second bearing 70 in the support frame 60 is responsible for bearing the gas force and centrifugal force generated by the rotation of the moving scroll disk 30. Figure 5 It is a spiral oil groove. Figure 8Both straight oil grooves can achieve the same effect. The second thrust surface 651 on the support frame 60 is responsible for bearing the shaft support of the shaft system (abutting against the first thrust surface 261 of the first shaft section 26). At least two fourth oil passage grooves 252 are provided on the second thrust surface 651, which are responsible for connecting the second oil passage groove 241 and the third oil passage groove 251, allowing lubricating oil to flow from the pump body to the third oil passage groove 251, and finally to the oil sump 16.

[0116] Figure 9 The rotor assembly 90 structure of this application includes a first balance block 92, a rotor assembly 90, and a second balance block 93. The rotor assembly 90 has a rotor flow hole 91 through which a top line passes, responsible for connecting the airflow between the upper and lower chambers of the motor to form an upper and lower circulation, reducing the oil circulation rate. The rotor flow hole 91 is located on the outer side of the crankshaft 20 and the inner side of the balance block. The first balance block 92 and the second balance block 93 are installed, and the positions of the main balance block and the auxiliary balance block can also be interchanged to meet the balance check requirements.

[0117] Figure 10 The moving scroll 30 structure of this application is an interference fit on the bottom shaft of the moving scroll 30. The moving scroll 30 has two oil grooves inside: a high-pressure oil groove 31, which is responsible for transporting the high-pressure lubricating oil from the center of the crankshaft 20 to the contact pair of the base plates of the moving scroll 30 and the stationary scroll 40, and is the main lubricating oil channel of the moving scroll 30; and a medium-pressure drainage groove 32, which is responsible for introducing the intermediate pressure of the pump body compression chamber into the bottom of the moving scroll 30 to form a medium-pressure back pressure, which is responsible for lifting the moving scroll 30 during operation, so that the moving scroll 30 and the stationary scroll 40 fit together and seal, thereby improving performance; and a scroll cross slip ring groove 33 for the support cross slip ring groove 63 for mounting the cross slip ring 13.

[0118] As can be seen from the above description, the embodiments of this application achieve the following technical effects:

[0119] By aligning the projected planes of the first bearing 50 and the second bearing 70 on the inner wall of the mounting channel 61, they are arranged coaxially in the radial direction, completely eliminating the traditional double-layer concentric bearing structure. This significantly reduces the axial dimension of the support frame 60 and the motor side shaft diameter, improving the overall miniaturization and reducing material costs and rotational inertia. Furthermore, the second bearing 70 directly conforms to the wall of the mounting channel 61 to form a sliding pair, achieving self-circulating lubrication in conjunction with the lower lubrication return section 25. This avoids the additional friction losses caused by traditional rolling bearings or double bearing stacking, effectively reducing shaft rotational power consumption and improving overall energy efficiency. This solves the technical problems of redundant shaft structure, dispersed lubrication paths, and poor motion stability in scroll compressors in related technologies. Moreover, by eliminating the lower support ring structure, costs are reduced while the compressor height can be significantly lowered. Furthermore, by using the upper bracket sliding bearing (second bearing 70) + spiral oil groove structure (lubrication return oil part 25), the bearing friction power consumption can be further reduced, the motor side shaft diameter can be reduced, and energy efficiency and cost can be reduced. By using the upper bracket thrust groove and multi-oil groove structure, all return oil can pass through the main bearing, while eliminating the return oil pipe structure, reducing energy efficiency and cost and improving reliability.

[0120] 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.

[0121] 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.

[0122] 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.

[0123] 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.

[0124] 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.

[0125] The above description is merely a preferred embodiment of this application and is not intended to limit this application. Various modifications and variations can be made to this application by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this application should be included within the protection scope of this application.

Claims

1. A compressor comprising a housing (10) and a crankshaft (20), a moving scroll (30), and a stationary scroll (40) respectively disposed therein, wherein the moving scroll (30) meshes with the stationary scroll (40), characterized in that, The crankshaft (20) has an eccentric receiving groove (21) at its end, the center line of the eccentric receiving groove (21) being parallel to the center line of the crankshaft (20), at least a portion of the moving scroll plate (30) being inserted into the eccentric receiving groove (21), and a first bearing (50) being provided between the moving scroll plate (30) and the eccentric receiving groove (21); the compressor further includes: A support frame (60) is located below the moving scroll plate (30). An installation channel (61) is provided inside the support frame (60). At least a portion of the crankshaft (20) passes through the installation channel (61). A second bearing (70) is sleeved on the crankshaft (20). The second bearing (70) is in contact with the channel wall of the installation channel (61). A lubrication return oil part (25) is provided inside the installation channel (61). The lubrication return oil part (25) is located below the second bearing (70). At least a portion of the outer peripheral wall of the crankshaft (20) is opposite to the lubrication return oil part (25). Along the radial direction of the crankshaft (20), the orthographic projection of the first bearing (50) on the inner wall of the mounting channel (61) coincides with the orthographic projection of the second bearing (70) on the inner wall of the mounting channel (61).

2. The compressor according to claim 1, characterized in that, The crankshaft (20) is provided with an oil supply channel (22), one end of which is connected to the oil sump (16) inside the housing (10), and the other end of which is connected to the eccentric receiving groove (21). The crankshaft (20) is provided with a first lubrication part (23), which is located on the groove wall of the eccentric receiving groove (21) to lubricate the first bearing (50).

3. The compressor according to claim 2, characterized in that, The first lubrication part (23) includes: The first oil passage groove (231) is disposed on the groove wall of the eccentric receiving groove (21); the first oil passage groove (231) extends along the axial direction of the crankshaft (20), and the outer peripheral surface of the first bearing (50) is disposed opposite to the first oil passage groove (231) so that a portion of the lubricating oil flows into the first oil passage groove (231) through the eccentric receiving groove (21).

4. The compressor according to claim 3, characterized in that, The first oil groove (231) extends from the bottom surface of the eccentric receiving groove (21) to the top end face of the crankshaft (20).

5. The compressor according to claim 2, characterized in that, A second lubrication part (24) is provided on the outer peripheral surface of the crankshaft (20). The second lubrication part (24) is connected to the first lubrication part (23) so as to lubricate the second bearing (70) through the second lubrication part (24).

6. The compressor according to claim 5, characterized in that, The second lubrication part (24) includes: The second oil passage groove (241) is provided on the outer peripheral surface of the crankshaft (20); extending along the axial direction of the crankshaft (20), the inner peripheral surface of the second bearing (70) is opposite to the second oil passage groove (241), so that after a portion of the lubricating oil flows through the first lubrication part (23), it flows into the second oil passage groove (241) through the top end face of the crankshaft (20).

7. The compressor according to claim 6, characterized in that, The installation channel (61) includes a first channel segment (610) and a second channel segment (611) that are connected. The first channel segment (610) is located above the second channel segment (611). The crankshaft (20) includes a first shaft segment (26) and a second shaft segment (27) that are connected. The diameter of the first shaft segment (26) is larger than the diameter of the second shaft segment (27). The first shaft segment (26) is disposed in the first channel segment (610). The eccentric receiving groove (21) is located on the first shaft segment (26). The lubrication return oil part (25) and the second shaft segment (27) are disposed in the second channel segment (611).

8. The compressor according to claim 7, characterized in that, The second shaft section (27) has an oil guide groove (28) extending circumferentially on its outer peripheral wall, and an oil passage hole (29) extending radially inside the second shaft section (27). The oil guide groove (28) communicates with the oil supply channel (22) through the oil passage hole (29); the lubrication return oil section (25) includes: At least two third oil passage grooves (251) are arranged at intervals along the circumference of the installation channel (61) on the inner wall of the second channel section (611). One end of each third oil passage groove (251) is connected to the second oil passage groove (241) and the oil passage guide groove (28), respectively. The other end of each third oil passage groove (251) extends out of the second channel section (611) and is connected to the oil pool (16). The third oil passage grooves (251) are arranged in a spiral, or the third oil passage grooves (251) extend axially along the second channel segment (611).

9. The compressor according to claim 8, characterized in that, The lubrication return section (25) also includes: At least two fourth oil passage grooves (252) are disposed in the second channel section (611) and are disposed in a one-to-one correspondence with the at least two third oil passage grooves (251). One end of each third oil passage groove (251) is connected to the corresponding fourth oil passage groove (252). The at least two fourth oil passage grooves (252) are disposed opposite to the oil passage guide groove (28) and are connected to the oil passage guide groove (28). Each fourth oil passage groove (252) is connected to the second oil passage groove (241).

10. The compressor according to claim 8, characterized in that, The number of the third oil-passing grooves (251) is N; Along the radial direction of the second channel segment (611), the third oil passage groove (251) has a first cross-sectional area S1, the second oil passage groove (241) has a second cross-sectional area S2, and along the axial direction of the second channel segment (611), the oil passage hole (29) has a third cross-sectional area S3, wherein NS1>S2+S3, N≥2; and / or, The third oil-passing groove (251) has a maximum cutting edge distance L; the second channel segment (611) has a preset inner diameter D; wherein, 5NL<πD, N≥2.

11. The compressor according to claim 7, characterized in that, The bottom of the first shaft segment (26) has a first thrust surface (261), and a stop block (65) is provided in the mounting channel (61). The stop block (65) extends from at least a portion of the channel wall of the mounting channel (61) toward the center line of the mounting channel (61). The stop block (65) surrounds the second channel segment (611). The top of the stop block (65) has a second thrust surface (651). The first thrust surface (261) is in contact with at least a portion of the second thrust surface (651).

12. The compressor according to claim 1, characterized in that, The compressor also includes: A stator (80) and a rotor assembly (90) are disposed within the housing (10), the rotor assembly (90) is sleeved on the crankshaft (20), and the stator (80) is sleeved on the rotor assembly (90); The rotor assembly (90) is provided with a first balance block (92) and a second balance block (93) at both ends along the axial direction. The first balance block (92) is provided on the first end face of the rotor assembly (90), and the second balance block (93) is provided on the second end face of the rotor assembly (90). The first balance block (92) and the second balance block (93) are staggered along the axial direction of the rotor assembly (90).

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