compressor

Abstract

The utility model provides a compressor, include: a crankshaft, a static scroll and a dynamic scroll of intermeshing, an eccentric swing cover, the dynamic scroll bearing of transmission dynamic scroll, the top of the sleeve joint part of eccentric swing cover is sleeve jointed the crankshaft, the outer periphery of sleeve joint part is equipped with a retraction annular shoulder platform, and a stop ring is arranged on the annular shoulder platform, when the back of dynamic scroll, the top of the crankshaft compresses the stop ring, and the stop ring provides the biasing force to the crankshaft to limit the back angle of dynamic scroll, the utility model can rely on the cooperation of crankshaft and eccentric swing cover and play the back stop effect of dynamic scroll, and the stop ring is installed between eccentric swing cover and crankshaft and plays the buffering effect.

Description

Technical Field

[0001] This utility model relates to the field of refrigeration equipment, and more specifically, to compressors. Background Technology

[0002] Scroll compressors, as efficient, low-noise, and compact fluid machinery, are widely used in air conditioning, refrigeration, heat pumps, and thermal management systems for new energy vehicles. Their core working components consist of a stationary scroll and a moving scroll, which mesh to form a continuously changing compression chamber, achieving gas compression. In actual operation, due to system control or environmental changes, the compressor may draw in liquid refrigerant or refrigeration oil, a phenomenon known as "liquid-bearing operation." Liquid is difficult to compress within the compression chamber; if it cannot be discharged in time, it will cause a sudden increase in pressure within the chamber, potentially leading to mechanical failures such as scroll tooth breakage and crankshaft seizure.

[0003] To prevent such malfunctions, existing technologies typically employ a "retracting mechanism" to temporarily disengage the moving scroll when liquid enters, creating a pressure relief channel. Among these, an eccentric swing sleeve structure is a common method for achieving this retraction. The moving scroll is mounted on the crankshaft's crankpin via an eccentric swing sleeve. When the pressure inside the compression chamber abnormally increases, the moving scroll drives the eccentric swing sleeve to rotate around the crankpin at a certain angle, temporarily separating the teeth of the moving and stationary scrolls, allowing the liquid to be discharged.

[0004] However, the retraction angle must be precisely controlled within a reasonable range. If the retraction angle is too small, the liquid cannot be effectively discharged; if the retraction angle is too large, the moving scroll cannot re-engage under centrifugal force, leading to compressor failure. Therefore, a stop structure must be installed to limit the maximum retraction angle of the eccentric swing sleeve.

[0005] Currently, the main stop solutions available in the industry are as follows: (1) Stop pin scheme A stop pin hole is made at the top of the crankshaft, a stop pin is pressed in, and a buffer ring is fitted onto the pin. The eccentric swing sleeve has protrusions or grooves; when the swing sleeve rotates to a certain angle, its protrusions contact the buffer ring on the stop pin, achieving a stop. The disadvantage of this solution is: The stop pins need to be designed, processed, and assembled separately, increasing the number of parts. The crankshaft requires additional machining of pin holes, which is a complex and costly process. The buffer ring only makes local contact, causing stress concentration, which can easily lead to fatigue damage with long-term use.

[0006] (2) Slotted crankshaft design

[0007] An annular groove is machined on the top of the crankshaft, and a stop ring is installed. When the eccentric swing sleeve rotates, its protruding part contacts the stop ring to achieve limiting. The disadvantage of this solution is: The crankshaft requires machining an annular groove, which weakens the structural strength of the crankshaft; The high precision required for groove machining increases manufacturing costs. The stop ring is not easily installed and is prone to falling off or shifting.

[0008] In summary, existing stop structures generally suffer from problems such as a large number of parts, complex manufacturing, high cost, and insufficient reliability. Therefore, there is an urgent need for a swing sleeve stop solution that is simple in structure, low in cost, highly reliable, and has good cushioning performance.

[0009] In view of this, the present invention provides a compressor. Utility Model Content

[0010] In view of the problems in the prior art, the purpose of this utility model is to provide a compressor that overcomes the difficulties of the prior art. It can play the role of stopping the retraction of the moving scroll by relying on the cooperation of the crankshaft and the eccentric swing sleeve. The stop ring installed between the eccentric swing sleeve and the crankshaft plays a buffering role, thereby improving reliability.

[0011] An embodiment of this utility model provides a compressor, comprising: One crankshaft; A stationary volute and a moving volute mesh with each other; An eccentric swing sleeve drives the moving scroll bearing of the moving scroll. The sleeve part of the eccentric swing sleeve is sleeved on the top of the crankshaft. The outer periphery of the sleeve part is provided with an inwardly recessed circumferential shoulder. A stop ring, disposed on the circumferential shoulder, compresses the stop ring at the top of the crankshaft during the retraction of the moving scroll, and the stop ring provides a biasing force to the crankshaft to limit the retraction angle of the moving scroll; and A main bearing is sleeved on the crankshaft, and the crankshaft, eccentric swing sleeve and main bearing together form an annular limiting space that clamps the stop ring.

[0012] Preferably, the outer periphery of the stop ring fits against the inner wall of the circumferential shoulder, and a gap is formed between the stop ring and the main bearing.

[0013] Preferably, the circumferential shoulder has a ring width of L2, and the distance between the sleeve and the crankshaft is L1, with 10%≤L1 / (L1+L2)≤40%.

[0014] Preferably, the diameter of the stop ring is F, where 1.25L2≤F≤2L2.

[0015] Preferably, the height of the circumferential shoulder is L3, the height of the sleeve is L4, and L4 / (L3+L4)≥30%.

[0016] Preferably, the stop ring is an elastic O-ring.

[0017] Preferably, the compression ratio of the stop ring is in the range of 20% to 50%.

[0018] Preferably, the top of the crankshaft is provided with a pin hole, and the eccentric swing sleeve further includes a balancing part and a bushing. The bushing is provided with a through hole, and the through hole is pinned to the pin hole by an eccentric pin.

[0019] The compressor of this invention can stop the retraction of the moving scroll by the cooperation of the crankshaft and the eccentric swing sleeve. The stop ring installed between the eccentric swing sleeve and the crankshaft plays a buffering role, thereby improving reliability. Attached Figure Description

[0020] Other features, objects, and advantages of this invention will become more apparent from the following detailed description of non-limiting embodiments with reference to the accompanying drawings.

[0021] Figure 1 This is a schematic diagram of a partial component in the compressor of this utility model.

[0022] Figure 2 for Figure 1 Cross-sectional view along the AA direction.

[0023] Figure 3 for Figure 2 Cross-sectional view along the BB direction.

[0024] Figure 4 for Figure 2 A magnified view of region C in the middle.

[0025] Figure 5 This is a schematic diagram of the eccentric swing sleeve in the compressor of this utility model.

[0026] Figure 6 This is a schematic diagram of the cooperation between the eccentric swing sleeve and the stop ring in the compressor of this utility model.

[0027] Figure 7 This is a perspective view of the eccentric swing sleeve and crankshaft fitting together in the compressor of this utility model.

[0028] Figure 8 This is a top view of the eccentric swing sleeve and crankshaft cooperation in the compressor of this utility model.

[0029] Figure 9 for Figure 8 Cross-sectional view along the DD direction.

[0030] Figure 10 This is a perspective view of the eccentric swing sleeve retracting in the compressor of this utility model.

[0031] Figure 11 This is a top view of the eccentric swing sleeve retracting in the compressor of this utility model.

[0032] Figure 12 for Figure 11 Cross-sectional view along the EE direction.

[0033] Figure Labels Detailed Implementation

[0034] The following specific examples illustrate the implementation methods of this application. Those skilled in the art can easily understand the other advantages and effects of this application from the content disclosed herein. This application can also be implemented or applied through other different specific embodiments, and various details in this application can be modified or changed according to different viewpoints and application systems without departing from the spirit of this application. It should be noted that, unless otherwise specified, the embodiments and features in the embodiments of this application can be combined with each other.

[0035] The embodiments of this application will now be described in detail with reference to the accompanying drawings, so that those skilled in the art can easily implement the application. This application may be embodied in many different forms and is not limited to the embodiments described herein.

[0036] In this application, the terms "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., refer to specific features, structures, materials, or characteristics represented in connection with that embodiment or example, which are included in at least one embodiment or example of this application. Furthermore, the specific features, structures, materials, or characteristics represented may be combined in any suitable manner in one or more embodiments or examples. Moreover, without contradiction, those skilled in the art can combine and integrate different embodiments or examples represented in this application, as well as features of different embodiments or examples.

[0037] Furthermore, the terms "first" and "second" are used for illustrative purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the representation of this application, "multiple" means two or more, unless otherwise explicitly specified.

[0038] For the purpose of clearly describing this application, devices that are not relevant to the description are omitted, and the same or similar components throughout the specification are given the same reference numerals.

[0039] Throughout this specification, when it is said that a device is "connected" to another device, this includes not only "direct connection" but also "indirect connection" by placing other components in between. Furthermore, when it is said that a device "comprises" a certain constituent element, unless otherwise stated otherwise, this does not exclude other constituent elements, but rather implies that other constituent elements may be included.

[0040] When we say that a device is "above" another device, this can mean that it is directly above the other device, or it can mean that other devices are present in between. Conversely, when we say that a device is "directly" "above" another device, there are no other devices present in between.

[0041] Although the terms first, second, etc., are used in some instances herein to refer to various elements, these elements should not be limited by these terms. These terms are used only to distinguish one element from another. For example, first interface and second interface, etc., are used. Furthermore, as used herein, the singular forms “a,” “an,” and “the” are intended to also include the plural forms unless the context indicates otherwise. It should be further understood that the terms “comprising,” “including,” indicate the presence of features, steps, operations, elements, components, items, kinds, and / or groups, but do not exclude the presence, occurrence, or addition of one or more other features, steps, operations, elements, components, items, kinds, and / or groups. The terms “or” and “and / or” as used herein are interpreted as inclusive, or mean any one or any combination thereof. Thus, “A, B, or C” or “A, B, and / or C” means “any one of: A; B; C; A and B; A and C; B and C; A, B, and C.” Exceptions to this definition will only occur if the combination of elements, functions, steps, or operations is inherently mutually exclusive in some way.

[0042] The technical terms used herein are for reference only to specific embodiments and are not intended to limit the scope of this application. The singular form used herein includes the plural form unless the statement explicitly indicates otherwise. The word "comprising" as used in the specification means to specify a particular characteristic, region, integer, step, operation, element, and / or component, and does not exclude the presence or addition of other characteristics, regions, integers, steps, operations, elements, and / or components.

[0043] Although not explicitly defined, all terms, including technical and scientific terms used herein, shall have the same meaning as commonly understood by one of ordinary skill in the art to which this application pertains. Terms defined in commonly used dictionaries shall be further interpreted as having a meaning consistent with the relevant technical literature and the content of this present application, and shall not be over-interpreted as having an ideal or overly formulaic meaning unless otherwise defined.

[0044] Figure 1This is a schematic diagram of a partial component in the compressor of this utility model. Figure 2 for Figure 1 Cross-sectional view along the AA direction. Figure 3 for Figure 2 Cross-sectional view along the BB direction. Figure 4 for Figure 2 A magnified view of region C in the middle. Figure 5 This is a schematic diagram of the eccentric swing sleeve in the compressor of this utility model. Figure 6 This is a schematic diagram of the cooperation between the eccentric swing sleeve and the stop ring in the compressor of this utility model. Figure 7 This is a perspective view of the eccentric swing sleeve and crankshaft fitting together in the compressor of this utility model. Figure 8 This is a top view of the eccentric swing sleeve and crankshaft cooperation in the compressor of this utility model. Figure 9 for Figure 8 Cross-sectional view along the DD direction. Figure 10 This is a perspective view of the eccentric swing sleeve retracting in the compressor of this utility model. Figure 11 This is a top view of the eccentric swing sleeve retracting in the compressor of this utility model. Figure 12 for Figure 11 A cross-sectional view along the EE direction. (See attached image.) Figures 1 to 12 As shown, the compressor of this utility model includes: a crankshaft 1, a stationary scroll 8 and a moving scroll 7 meshing with each other, an eccentric swing sleeve 5, and a stop ring 4. The eccentric swing sleeve 5 drives the moving scroll bearing 6 of the moving scroll 7. The sleeve portion 52 of the eccentric swing sleeve 5 is fitted onto the top of the crankshaft 1, and the outer periphery of the sleeve portion 52 is provided with an inwardly recessed circumferential shoulder 53. The stop ring 4 is disposed on the circumferential shoulder 53. When the moving scroll 7 retracts, the top of the crankshaft 1 compresses the stop ring 4, and the stop ring 4 provides a biasing force to the crankshaft 1 to limit the retraction angle of the moving scroll 7. A main bearing 3 is fitted onto the crankshaft 1. The crankshaft 1, the eccentric swing sleeve 5, and the main bearing 3 together form an annular limiting space that clamps the stop ring 4. The purpose of this invention is to provide a scroll compressor swing sleeve stop and buffer structure with an extremely simple structure, few parts, and low manufacturing cost. This structure can precisely and stably control the maximum retraction angle of the moving scroll, ensuring consistent stop structure throughout the product's entire lifespan and effectively avoiding performance degradation and failure risks caused by wear. Furthermore, it eliminates the need for any additional drilling or grooving in critical stress areas of the crankshaft, thus completely preserving the original structural integrity and mechanical strength of the crankshaft. This results in a highly efficient and smooth buffer, significantly reducing impact noise and vibration, and comprehensively improving the compressor's NVH performance.

[0045] In a preferred embodiment, the outer periphery of the stop ring 4 fits against the inner wall of the circumferential shoulder 53, and a gap is formed between the stop ring 4 and the main bearing 3, but this is not a limitation.

[0046] In a preferred embodiment, the circumferential shoulder 53 has a circumferential width of L2, and the distance between the sleeve portion 52 and the crankshaft is L1, 10%≤L1 / (L1+L2)≤40%, but is not limited thereto.

[0047] In a preferred embodiment, the diameter of the stop ring 4 is F, where 1.25L2≤F≤2L2, but is not limited thereto.

[0048] In a preferred embodiment, the height of the circumferential shoulder 53 is L3, the height of the sleeve portion 52 is L4, and L4 / (L3+L4)≥30%, but is not limited thereto.

[0049] In a preferred embodiment, the stop ring 4 is an elastic O-ring, but is not limited thereto.

[0050] In a preferred embodiment, the compression rate of the stop ring 4 ranges from 20% to 50%, but is not limited thereto.

[0051] In a preferred embodiment, the top of the crankshaft 1 is provided with a pin hole, and the eccentric swing sleeve 5 also includes a balancing part 51 and a bushing 54. The bushing 54 is provided with a through hole 55, and the through hole 55 is pinned to the pin hole by an eccentric pin 2, but is not limited thereto.

[0052] In a preferred embodiment, the balancing part 51, the sleeve part 52, the circumferential shoulder 53, the bushing 54, and the through hole 55 of the eccentric swing sleeve 5 are all integrally formed, but this is not a limitation.

[0053] The compressor of this invention includes the following basic elements: crankshaft 1, stationary scroll 8, moving scroll 7, eccentric swing sleeve 5, and stop ring 4. The crankshaft 1 serves as the power input shaft and is driven to rotate by a motor. The stationary scroll 8 and moving scroll 7 mesh with each other to form a compression chamber. The eccentric swing sleeve 5 is a key transmission component connecting the crankshaft 1 and the moving scroll 7. It is connected to the moving scroll 7 via a moving scroll bearing 6 (such as a needle roller bearing). The eccentric swing sleeve 5 has a crucial "sleeving part 52," which directly sleeves onto the top of the crankshaft 1 through its inner hole. A recessed "circumferential shoulder 53" is machined into the outer periphery of the sleeve part 52. This shoulder is not a separate part but is part of the eccentric swing sleeve 5 body. The stop ring 4, as an independent elastic element, is directly placed and positioned on the circumferential shoulder 53.

[0054] The working principle and inventiveness of this utility model are embodied in the following dynamic process: When abnormal high pressure is generated in the compression chamber due to the entry of liquid, the moving scroll 7 is forced to retract under the action of liquid pressure. This retraction motion is transmitted to the eccentric swing sleeve 5 through the moving scroll bearing 6, forcing the eccentric swing sleeve 5 to rotate relative to the crankshaft 1 around the axis of the "eccentric pin 2" connecting it to the crankshaft 1 (i.e., "retraction" motion). As the retraction angle increases, the stop ring 4 installed on the circumferential shoulder 53 of the eccentric swing sleeve 5 also rotates around the center of the crankshaft 1. When the retraction reaches the preset maximum angle, the top outer edge of the crankshaft 1 begins to contact the stop ring 4. After contact occurs, the top of the crankshaft 1 continues to move, beginning to radially compress the stop ring 4. The stop ring 4 undergoes significant and controllable elastic deformation (such as compression and shear combined deformation). The compressed stop ring 4 applies a gradually increasing normal reaction force (i.e., bias force) to the crankshaft 1, pointing towards the center of the crankshaft 1. This reaction force generates a torque opposite to the direction of the eccentric pendulum sleeve 5's retraction. This torque constitutes a strong resistance to the further rotation of the eccentric pendulum sleeve 5, thus ultimately limiting the retraction angle of the moving volute 7 within the preset safe maximum value θmax. During this process, liquid leaks out through the increased gap between the volute teeth due to the retraction, causing a pressure drop. When the pressure inside the cavity returns to normal, the retraction force disappears, and the moving volute 7 and the eccentric pendulum sleeve 5 automatically reset under the action of centrifugal force and other restoring forces. The stop ring 4 also returns to its original shape due to its own elasticity.

[0055] The compressor also includes a main bearing 3, which is fitted onto the crankshaft 1 and provides radial support for the crankshaft 1. In a highly preferred embodiment, the top outer cylindrical surface of the crankshaft 1, the circumferential shoulder 53 of the eccentric swing sleeve 5, and the end face of the main bearing 3 near the top of the crankshaft 1 together naturally form an "annular limiting space" for accommodating and radially and axially restricting the stop ring 4. This design is a distinguishing feature between this invention and the prior art. It cleverly utilizes the geometric features of the inherent and essential components in the compressor core assembly to form a functional "mounting groove," thereby completely eliminating the need to machine a dedicated annular groove or stop pin hole on the crankshaft 1, achieving extreme structural simplification.

[0056] The outer peripheral wall of the stop ring 4 and the inner sidewall of the circumferential shoulder 53 are preferably in close contact or have a very small gap. This design ensures that the stop ring 4 is well positioned radially, preventing it from wobbling or shifting within the circumferential shoulder 53, and ensuring the accuracy and consistency of the contact position when the stop action occurs. Simultaneously, in the axial direction (parallel to the crankshaft 1 axis), a small "initial gap" or a "slight pre-contact" state can be designed between the stop ring 4 and the end face of the main bearing 3 in the non-stop state. This ensures that the triggering and limiting of the stop function are mainly accomplished by the radial contact-compression mechanism between the top of the crankshaft 1 and the stop ring 4, avoiding the uncertainty caused by the premature participation of the end face of the main bearing 3 in force transmission. The specific connection method between crankshaft 1 and eccentric swing sleeve 5 is as follows: a pin hole is provided on the top of crankshaft 1, a through hole 55 is provided on bushing 54 of eccentric swing sleeve 5, an eccentric pin 2 passes through the through hole 55 and is firmly pinned (such as interference fit) into the pin hole of crankshaft 1, thereby forming a hinged connection.

[0057] To optimize the buffering and limiting performance of this invention, based on in-depth mechanical analysis, simulation calculations, and experimental verification, the following preferred ranges for key dimensions were determined. These ranges are crucial for achieving the superior technical effects of this invention: (1) The radial clearance ratio is L1 / (L1+L2). Wherein, L1 is the radial distance (i.e., assembly clearance) between the inner wall of the sleeve 52 and the outer wall of the top of the crankshaft 1. L2 is the ring width (radial dimension) of the circumferential shoulder 53. The preferred range of the radial clearance ratio is: 10%≤L1 / (L1+L2)≤40%. This ratio determines the depth and manner in which the top of the crankshaft 1 "cuts" into the stop ring 4 when the stop is effective, directly affecting the deformation mode (compression or shear), effective force-bearing area, and shape of the force-displacement curve of the stop ring 4. If the ratio is too small, the buffer stiffness may be too large, resulting in a large impact force; if the ratio is too large, the limit may be inaccurate, and the stop ring 4 may easily undergo excessive and uncontrollable deformation. This range ensures that the buffering process is smooth and controllable, and can accurately limit the angle.

[0058] (2) The diameter ratio of the stop ring 4 is D1 / L2. Wherein, D1 is the diameter of the stop ring 4 in its free state (for an O-ring with a circular cross-section, it refers to its wire diameter). The preferred range for the diameter of the stop ring 4 is: 1.25≤D1 / L2≤2.0. This range ensures that the stop ring 4 has sufficient volume and material to provide the necessary elastic restoring force and energy absorption capacity. If D1 / L2 is too small (the stop ring 4 is too thin), the buffering force provided is insufficient, and it is prone to premature damage due to excessive stress. If D1 / L2 is too large (the stop ring 4 is too thick), it may lead to installation difficulties or unnecessary interference with the crankshaft 1 or main bearing 3 in the non-stop state, increasing frictional losses.

[0059] (3) The height ratio of the sleeve portion 52 is L4 / (L3+L4). Wherein, L3 is the axial height of the circumferential shoulder 53. L4 is the total axial height of the sleeve portion 52. The preferred range of the height ratio of the sleeve portion 52 is: L4 / (L3+L4)≥30%. This ratio ensures that the sleeve portion 52 has a sufficiently long axial guide surface to fit with the top of the crankshaft 1. This is crucial for ensuring the stability of the eccentric swing sleeve 5 during operation, reducing swaying, and ensuring the trajectory accuracy of the revolution and translation of the moving scroll 7, thereby indirectly improving the reliability and efficiency of the compressor.

[0060] (4) Material and Compression Ratio of the Stop Ring 4. The stop ring 4 is preferably a standard elastic O-ring. Its material should be an elastomer resistant to refrigerants, lubricating oils, and high temperatures, and possessing excellent fatigue resistance, such as hydrogenated nitrile rubber (HNBR), fluororubber (FKM), or ethylene propylene diene monomer (EPDM). The compression ratio of the stop ring 4 under operating conditions is the percentage of the deformation of its cross-section in the compression direction (free cross-section diameter - compressed cross-section diameter) to the free cross-section diameter when the moving scroll 7 retracts to its maximum design angle and is compressed by the crankshaft 1. The compression ratio range of the stop ring 4 is 20% ≤ compression ratio ≤ 50%. This compression ratio range has been carefully selected. A compression ratio below 20% may not provide sufficient buffering force, and the sealing and positioning effect between the stop ring 4 and the mating surface may be poor. A compression ratio above 50% will result in excessive stress on the stop ring 4, potentially leading to permanent deformation (plastic deformation) or accelerated stress relaxation and aging, affecting its service life and performance consistency. Compression ratios of 20% to 50% provide stable and reliable cushioning and angle limitation throughout the entire product lifespan.

[0061] The specific embodiments of this utility model include: See Figure 1 As shown, this diagram illustrates the core transmission and stop components of a scroll compressor utilizing this invention. The crankshaft 1 is driven by an electric motor (not shown) and rotates along its axis. The main bearing 3 is press-fitted or fixed within the compressor housing (not shown), providing radial support for the crankshaft 1. The stationary scroll 8 is also fixed to the housing. The moving scroll 7 and the stationary scroll 8 mesh with each other via their involute profiles, forming a series of crescent-shaped compression chambers.

[0062] The eccentric swing sleeve 5 is a key component for realizing the revolution and translation of the moving scroll 7. It connects to the pin hole at the top of the crankshaft 1 via a through hole 55 on the bushing 54 and an eccentric pin 2 passing through this hole, thus achieving a hinged connection. A moving scroll bearing 6 (e.g., a needle roller bearing) is mounted on the balancing part 51 of the eccentric swing sleeve 5, and the moving scroll 7 rests on the eccentric swing sleeve 5 via this bearing. When the crankshaft 1 rotates, the eccentric pin 2 drives the eccentric swing sleeve 5, which in turn drives the moving scroll 7 to revolve and translate around the center of the stationary scroll 8, completing the gas compression process.

[0063] The core improvement of this utility model is concentrated in the sleeve portion 52 of the eccentric swing sleeve 5. For example... Figure 1 , Figure 2 , Figure 4 , Figure 5 , Figure 6 , Figure 9 , Figure 12 As shown, an inwardly recessed circumferential shoulder 53 is machined on the inner cylindrical surface of the sleeve portion 52 by turning or grinding. This shoulder 53 has a defined circumferential width L2 and a circumferential shoulder height L3 (axial height).

[0064] A standard O-ring made of hydrogenated nitrile butadiene rubber (HNBR) serves as the stop ring 4 and is placed directly on this circumferential shoulder 53. For example... Figure 1 and Figure 5 As shown, after the crankshaft 1, main bearing 3, and eccentric swing sleeve 5 with stop ring 4 are assembled, the three naturally work together: The outer cylindrical surface at the top of crankshaft 1 forms the "inner wall" of the annular limiting space. The bottom surface and inner wall of the circumferential shoulder 53 of the eccentric swing sleeve 5 form the "bottom" and "outer wall" of the annular limiting space. The upper end face of the main bearing 3 forms the "top cover" or "axial limiting surface" of the annular limiting space. Thus, a complete and functional annular limiting space is formed, and the stop ring 4 is stably accommodated and confined within this space. In this embodiment, the outer peripheral wall of the stop ring 4 and the inner wall of the circumferential shoulder 53 are in close contact (transition fit) to achieve radial positioning. A small initial gap S is designed between the top surface of the stop ring 4 and the end face of the main bearing 3 to ensure that the stopping function is dominated by the radial contact between the crankshaft 1 and the stop ring 4.

[0065] The compressor of this invention is in normal compression state ( Figure 7 , 8 9): During normal operation of the compressor, the moving scroll 7 maintains a set meshing state with the stationary scroll 8 under the constraints of gas force, centrifugal force, and mechanical structure. At this time, there is a radial clearance between the outer cylindrical surface of the crankshaft 1 and the stop ring 4, and the stop ring 4 is in a free state and does not participate in force transmission.

[0066] The compressor of this utility model is in a retracted and stopped state ( Figure 10 , 11 12): When a large amount of liquid refrigerant or oil enters the compression chamber, the pressure P_abnormal inside the chamber rises sharply. This pressure acts on the moving scroll 7, generating a retraction torque M_retreat that causes it to detach from the stationary scroll 8. This torque is transmitted to the eccentric swing sleeve 5 through the moving scroll bearing 6, forcing the eccentric swing sleeve 5 to rotate around the axis of the eccentric pin 2 along... Figure 3As indicated by the middle arrow, the crankshaft 1 rotates (retracts). With the increase of the retraction angle θ, the stop ring 4, fixed to the eccentric swing sleeve 5, also moves closer to the crankshaft 1. When the retraction angle reaches its design maximum value θmax, the top outer edge of the crankshaft 1 begins to contact the stop ring 4. Retraction continues, and the crankshaft 1 continuously radially compresses the stop ring 4. The stop ring 4 undergoes elastic deformation, its cross-section changing from a circle to an approximately elliptical shape, with material pushed to both sides and axially. During this process, the stop ring 4 applies a gradually increasing normal reaction force F_elastic to the crankshaft 1. This force generates a resisting torque M_resist, opposite in direction to the retraction torque M_retreat. When the resisting torque M_resist balances the retraction torque M_retreat, the eccentric swing sleeve 5 and the moving scroll 7 stop retracting, and the retraction angle is precisely limited to θmax. At this point, the compressed liquid rapidly leaks out through the increased gap between the scroll teeth, and the internal pressure decreases. Once the internal pressure returns to normal (reset state), the abnormal retraction torque acting on the moving scroll 7 disappears. At this time, the moving scroll 7 and the eccentric swing sleeve 5 are thrown back to their initial positions under the centrifugal force generated by rotating around the main shaft. The stop ring 4 loses compression and quickly returns to its original state relying on its own elastic restoring force. The compressor resumes normal compression operation.

[0067] Furthermore, the key dimension design embodiments of this utility model (see reference) Figure 9 , 12Based on the compressor model and design requirements, the target maximum retraction angle θmax is set. Using geometric relationships, the theoretical contact point position between the crankshaft and the swing sleeve required to achieve θmax is calculated, thus determining the required radial spacing L1 (considering tolerances) to be approximately 0.5mm. The design circumferential shoulder width L2 is approximately 2.0mm. Therefore, L1 / (L1+L2)=0.5 / (0.5+2.0)=20%, falling within the preferred range of 10%~40%. The free-state wire diameter F (diameter) of the stop ring 4 is selected. According to 1.25L2≤D1≤2L2, i.e. 2.5mm≤D1≤4.0mm, a standard O-ring with D1=3.0mm is selected in this example. Therefore, D1 / L2=3.0 / 2.0=1.5, falling within the preferred range. The design circumferential shoulder height L3 is 1.0mm, and the total height of the sleeve part L4 is 3.0mm. Therefore, L4 / (L3+L4) = 3.0 / (1.0+3.0) = 75%, which is greater than the preferred lower limit of 30%, ensuring the stability of the sleeve guide. Through dynamic simulation and tolerance analysis, it is confirmed that under extreme boundary conditions, the compression ratio of the stop ring 4 in the working state can be controlled at about 30%, which is within the optimal range of 20% to 50%, providing sufficient buffering force while ensuring a long service life. In summary, this utility model, through an extremely ingenious "integrated" design, seamlessly embeds the stop buffering function into the existing core transmission components of the compressor, utilizing its own geometric features to form a functional structure. Thus, with the lowest cost and the simplest structure, it achieves performance, reliability, and NVH performance superior to existing technologies. It represents a significant technological advancement in the field of scroll compressor stop technology.

[0068] In summary, the purpose of this utility model is to provide a compressor that can stop the retraction of the moving scroll by relying on the cooperation of the crankshaft and the eccentric swing sleeve, and to improve reliability by installing a stop ring between the eccentric swing sleeve and the crankshaft.

[0069] The above description, in conjunction with specific preferred embodiments, provides a further detailed explanation of the present invention. It should not be construed that the specific implementation of the present invention is limited to these descriptions. For those skilled in the art, various simple deductions or substitutions can be made without departing from the concept of the present invention, and all such modifications and substitutions should be considered within the protection scope of the present invention.

Claims

1. A compressor, characterized in that, include: A crankshaft (1); A stationary volute (8) and a moving volute (7) mesh with each other; An eccentric swing sleeve (5) drives the moving scroll bearing (6) of the moving scroll (7). The sleeve part (52) of the eccentric swing sleeve (5) is sleeved on the top of the crankshaft (1). The outer periphery of the sleeve part (52) is provided with an inwardly recessed circumferential shoulder (53). A stop ring (4) is disposed on the circumferential shoulder (53). During the retraction of the moving scroll (7), the top of the crankshaft (1) compresses the stop ring (4), and the stop ring (4) provides a biasing force to the crankshaft (1) to limit the retraction angle of the moving scroll (7); and A main bearing (3) is sleeved on the crankshaft (1), and the crankshaft (1), the eccentric swing sleeve (5) and the main bearing (3) together form an annular limiting space that clamps the stop ring (4).

2. The compressor as described in claim 1, characterized in that, The outer periphery of the stop ring (4) fits against the inner wall of the circumferential shoulder (53), and a gap is formed between the stop ring (4) and the main bearing (3).

3. The compressor as described in claim 1, characterized in that, The circumferential shoulder (53) has a circumferential width of L2, and the distance between the sleeve (52) and the crankshaft is L1, with 10% ≤ L1 / (L1+L2) ≤ 40%.

4. The compressor as described in claim 3, characterized in that, The diameter of the stop ring (4) is F, where 1.25L2≤F≤2L2.

5. The compressor as described in claim 1, characterized in that, The height of the circumferential shoulder (53) is L3, the height of the sleeve (52) is L4, and L4 / (L3+L4)≥30%.

6. The compressor as claimed in claim 1, characterized in that, The stop ring (4) is an elastic O-ring.

7. The compressor as claimed in claim 1, characterized in that, The compression rate of the stop ring (4) ranges from 20% to 50%.

8. The compressor as claimed in claim 1, characterized in that, The crankshaft (1) has a pin hole at its top. The eccentric swing sleeve (5) also includes a balance part (51) and a bushing (54). The bushing (54) has a through hole (55), and the through hole (55) is pinned to the pin hole by an eccentric pin (2).

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