Reverse rotation preventing structure and compressor

Abstract

The anti-reverse-rotation structure is used for preventing a crankshaft from rotating reversely, the crankshaft is inserted into a center hole of a lower support, a through hole is formed in the crankshaft in the radial direction, a groove is formed in the side wall of the center hole, and a limiting face is arranged on the side wall of the groove; the reverse rotation preventing structure comprises a limiting piece and an elastic piece, one end of the elastic piece abuts against the interior of the through hole, the other end of the elastic piece is matched with one end of the limiting piece, and the other end of the limiting piece can make sliding contact with the side wall of the groove when the crankshaft rotates forwards and can be blocked by the limiting face when the groove rotates reversely. Through cooperation of the limiting piece and the limiting face, the crankshaft is forcibly locked at the beginning of reverse rotation, the reverse rotation delay phenomenon caused by gas backflow is eliminated, and immediate stop is achieved. Aiming at the reliability problem of the one-way valve, rigid combination of the limiting piece and the elastic piece is adopted. The limiting piece flexibly slides in the groove to avoid abrasion during forward rotation, impact force is directly borne by the limiting face during reverse rotation, collision energy is absorbed by the elastic piece, and the risk of breakage of the valve plate is fundamentally solved.

Description

Technical Field

[0001] The present invention belongs to the field of compressors, and in particular relates to an anti-reversal structure and a compressor. Background Art

[0002] Scroll compressors are a common and widely used type of compressor. They utilize a unique scroll design, where two intersecting spiral scrolls mesh together to compress gas. This design not only simplifies the internal structure and reduces friction between moving parts, but also significantly improves compression efficiency and operational stability.

[0003] When the scroll compressor is shut down, the high-pressure refrigerant on the exhaust side will flow back to the suction side, causing the compressor to reverse. The existing technology usually uses a one-way check valve structure to achieve the anti-reversal function, but this type of structure has two key defects: First, under high-speed and large-displacement conditions, when the compressor operates in a high-pressure differential environment, the check valve plate will repeatedly impact the stator and valve seat at an extremely high speed, causing the valve plate to tilt, wear, or even break; Second, due to insufficient structural clearance and sealing, high-pressure gas will still flow back through the valve clearance, which cannot completely prevent the compressor from reversing, and can only delay the reversal process. This not only causes excessive shutdown noise, but also causes abnormal wear of moving parts, seriously affecting the reliability of the compressor. In particular, with the development trend of scroll compressors towards high speed, the existing anti-reversal structure can no longer meet the demand in terms of reliability and timeliness. Summary of the Invention

[0004] In view of this, the present invention provides an anti-reversal structure and a compressor, which solve the technical problems of the traditional anti-reversal structure being easily worn and affecting the performance of the compressor.

[0005] In order to solve the above problems, according to one aspect of the present application, an embodiment of the present invention provides an anti-reversal structure, which is used to prevent the crankshaft from reversing. The crankshaft is inserted into the center hole of the lower bracket, and the crankshaft is radially provided with a through hole. The side wall of the center hole has a groove, and the side wall of the groove has a limiting surface; the anti-reversal structure includes a limiting member and an elastic member, one end of the elastic member abuts against the through hole, and the other end of the elastic member cooperates with one end of the limiting member, and the other end of the limiting member can slide in contact with the side wall of the groove when the crankshaft rotates forward, and can be blocked by the limiting surface when the groove reverses.

[0006] In some embodiments, the other end of the limit member is a first curved surface, the side wall of the groove is a second curved surface, and the first curved surface cooperates with the second curved surface; when the crankshaft rotates forward, the first curved surface slides along the second curved surface.

[0007] In some embodiments, the limiting surface is a vertically arranged plane, and the plane is adjacent to the second curved surface; when the crankshaft is reversed, the first curved surface and the plane form an obstruction.

[0008] In some embodiments, one end of the limiting member has a matching hole, and the other end of the elastic member is located in the matching hole.

[0009] In some embodiments, the crankshaft has a central oil hole, and the through hole is connected to the central oil hole to form an oil supply channel; when the crankshaft rotates, the lubricating oil enters the through hole through the oil supply channel to lubricate the contact surface between the limit member and the inner wall of the through hole.

[0010] In some embodiments, the first curved surface is a spherical surface, the second curved surface is an arc curved surface, and the curvature radius of the spherical surface is smaller than the curvature radius of the arc curved surface to form a line contact sliding fit.

[0011] In some embodiments, there are four through holes, which are evenly distributed along the circumference of the crankshaft, and each through hole is provided with a corresponding limiting member and elastic member; two limiting surfaces are provided, and the two limiting surfaces are relatively arranged on the side walls of the groove.

[0012] In some embodiments, two limiting surfaces are provided, and the two limiting surfaces are symmetrically distributed at 180° with the crankshaft axis as the center, and when any of the limiting members contacts the limiting surface, the maximum reversal angle of the crankshaft is no more than 90°.

[0013] In some embodiments, the elastic member is a spring.

[0014] According to another aspect of the present application, an embodiment of the present invention provides a compressor, which includes a crankshaft, a lower bracket, a shell, a compression assembly, a drive assembly and the above-mentioned anti-reversal structure, wherein the crankshaft, the lower bracket, the compression assembly and the drive assembly are all arranged in the shell, and the anti-reversal structure is arranged between the through hole and the groove.

[0015] Compared with the prior art, the anti-reversal structure of the present invention has at least the following beneficial effects: The anti-reversal structure provided by the present invention is used to prevent the crankshaft from reversing. The crankshaft is inserted into the center hole of the lower bracket, and the crankshaft is provided with a through hole in the radial direction. The side wall of the center hole is provided with a groove, and the side wall of the groove is provided with a limiting surface; the anti-reversal structure includes a limiting part and an elastic part, one end of the elastic part abuts against the through hole, and the other end of the elastic part cooperates with one end of the limiting part, and the other end of the limiting part can slide in contact with the side wall of the groove when the crankshaft rotates forward, and can be blocked by the limiting surface when the groove reverses.

[0016] The present invention forcibly locks the crankshaft at the start of reversal through the rigid mechanical blocking of the limiter and the limit surface, completely eliminating the reversal delay phenomenon caused by gas backflow and achieving instant stop with zero reversal turns. In order to solve the reliability problem of the one-way valve, this embodiment eliminates the fragile valve plate structure and adopts a rigid combination of a limiter and an elastic member. During forward rotation, the limiter slides flexibly in the groove to avoid wear. During reversal, the impact force is directly borne by the limit surface, and the elastic member absorbs the collision energy, fundamentally solving the risk of valve plate breakage. The entire structure transforms the passive anti-reversal relying on gas sealing into a purely mechanical active locking, completely avoiding the defects of high-pressure gas leakage and reversal delay caused by sealing gaps in traditional structures.

[0017] The compressor provided by the present invention is designed based on the above-mentioned anti-reversal structure. Its beneficial effects can be found in the beneficial effects of the above-mentioned anti-reversal structure, which will not be described in detail here.

[0018] The above description is only an overview of the technical solution of the present invention. In order to more clearly understand the technical means of the present invention and implement it according to the contents of the specification, the following is a detailed description of the preferred embodiments of the present invention with reference to the accompanying drawings. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the following briefly introduces the drawings required for use in the description of the embodiments. Obviously, the drawings described below are some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.

[0020] Figure 1 1 is a schematic structural diagram of an anti-reversal structure provided by an embodiment of the present invention; Figure 2 is a cross-sectional view of an anti-reversal structure provided by an embodiment of the present invention; Figure 3 yes Figure 2 A partial enlarged view of point A in the middle; Figure 4 1 is a schematic structural diagram of a bracket in an anti-reversal structure provided by an embodiment of the present invention; Figure 5 is a top view of a bracket in an anti-reversal structure provided by an embodiment of the present invention; Figure 6 This is a cross-sectional view of the engagement between the limiting member and the groove when the crankshaft rotates forward in an anti-reverse rotation structure provided by an embodiment of the present invention; Figure 7 yes Figure 6 A partial enlarged view of point B in the middle; Figure 8This is a cross-sectional view of the cooperation between the limiting member and the limiting surface when the crankshaft reverses in an anti-reversal structure provided by an embodiment of the present invention; Figure 9 yes Figure 8 A partial enlarged view of point C in the middle; Figure 10 is a cross-sectional view of a compressor provided by an embodiment of the present invention; Figure 11 yes Figure 10 A partial enlarged view of point D in the middle; in: 1. Crankshaft; 11. Through hole; 12. Center oil hole; 2. Lower bracket; 21. Center hole; 22. Groove; 23. Limiting surface; 3. Anti-reverse structure; 31. Limiting member; 32. Elastic member; 311. Matching hole; 4. Housing; 41. Upper cover; 42. Main body; 43. Lower cover; 5. Compression assembly; 51. Stationary scroll; 52. Orbital scroll; 53. Cross ring; 6. Drive assembly; 61. Motor rotor; 62. Motor stator. DETAILED DESCRIPTION

[0021] To further illustrate the technical means and effects employed by the present invention to achieve its intended objectives, the following detailed description of the specific implementation methods, structures, features, and effects of the present invention is provided in conjunction with the accompanying drawings and preferred embodiments. In the following description, different references to "one embodiment" or "embodiment" do not necessarily refer to the same embodiment. Furthermore, specific features, structures, or characteristics of one or more embodiments may be combined in any suitable manner.

[0022] In the description of the present invention, it should be clarified that the terms "first", "second", etc. in the specification and claims of the present invention and the above-mentioned drawings are used to distinguish similar objects, and are not necessarily used to describe a specific order or sequence; the terms "vertical", "transverse", "longitudinal", "front", "back", "left", "right", "up", "down", "horizontal", etc. indicating directions or positional relationships are based on the directions or positional relationships shown in the drawings, and are only for the convenience of describing the present invention, and do not mean that the devices or elements referred to must have a specific direction or position, and therefore cannot be understood as limiting the present invention.

[0023] In the description of the present invention, it should be noted that, unless otherwise expressly specified or limited, the terms "mounted," "connected," and "connected" should be understood broadly. For example, they may refer to fixed, detachable, or integral connections; mechanical or electrical connections; and direct or indirect connections through an intermediary. Those skilled in the art will understand the specific meanings of the above terms in the present invention based on the specific circumstances.

[0024] Example 1: This embodiment provides an anti-reversal structure, such as Figures 1-8 As shown, the anti-reversal structure is used to prevent the crankshaft 1 from reversing. The crankshaft 1 is inserted into the center hole 21 of the lower bracket 2. The crankshaft 1 is radially provided with a through hole 11. The side wall of the center hole 21 has a groove 22, and the side wall of the groove 22 has a limiting surface 23; the anti-reversal structure includes a limiting member 31 and an elastic member 32, one end of the elastic member 32 abuts against the through hole 11, and the other end of the elastic member 32 cooperates with one end of the limiting member 31, and the other end of the limiting member 31 can slide in contact with the side wall of the groove 22 when the crankshaft 1 rotates forward, and can be blocked by the limiting surface 23 when the groove 22 reverses.

[0025] In this embodiment, the crankshaft 1 serves as the core transmission component to drive the compressor and carry the anti-reverse structure. The lower bracket 2 fixes and supports the crankshaft 1 and provides a mounting base. The center hole 21 constrains the rotation trajectory of the crankshaft 1. The groove 22 provides a sliding track and a limiting space for the limiter 31. The limiting surface 23 directly blocks the limiter 31 during reversal to achieve mechanical locking. The limiter 31 slides along the side wall of the groove 22 during forward rotation, and engages with the limiting surface 23 to prevent rotation during reversal. The elastic member 32 continuously applies radial thrust to the limiter 31, so that it always clings to the side wall of the groove 22, while absorbing collision energy during reversal impact.

[0026] The crankshaft 1 is inserted into the center hole 21 of the lower bracket 2 for rotational support. The crankshaft 1 has a through hole 11 radially provided to accommodate a limit member 31 and an elastic member 32. The limit member 31 is located near the outside of the through hole 11, and the elastic member 32 is installed on the inside of the through hole 11, with one end thereof abutting against the inner wall of the through hole 11, and the other end pushing the limit member 31 so that it has a tendency to extend radially outward. A groove 22 is provided on the side wall of the center hole 21 of the lower bracket 2, and the groove 22 includes a specially designed limit surface 23. When the crankshaft 1 is installed in place, the end of the limit member 31 maintains a spatial correspondence with the side wall of the groove 22. When the crankshaft 1 rotates forward, the limit member 31 slides in contact with the smooth side wall of the groove 22. When the crankshaft 1 rotates reversely, the limit member 31 forms a blocking fit with the limit surface 23.

[0027] When the crankshaft 1 drives the limiting member 31 to rotate forward, the limiting member 31 slides against the smooth side wall of the groove 22 under the push of the elastic member 32. Figure 6 and Figure 7 As shown. The curved surface profile of the groove 22 causes the limiter 31 to undergo radial expansion and contraction during the sliding process. At this time, the anti-reverse structure does not affect the normal rotation of the crankshaft 1. When the compressor stops and reverses, the crankshaft 1 rotates in the opposite direction. The limiter 31 remains in the extended state under the action of the elastic member 32 and is immediately blocked by the limit surface 23 of the groove 22. Figure 8 and Figure 9This rigid blockage forcibly interrupts the reverse motion of the crankshaft 1, achieving instantaneous locking. During the entire process, the elastic member 32 ensures flexible contact during forward rotation and buffers the rigid collision during reverse rotation.

[0028] This embodiment uses the rigid mechanical blocking of the limit member 31 and the limit surface 23 to forcibly lock the crankshaft 1 at the start of reversal, completely eliminating the reversal delay phenomenon caused by gas backflow and achieving instant stop with zero reversal turns. In order to solve the reliability problem of the one-way valve, this embodiment eliminates the fragile valve plate structure and adopts a rigid combination of the limit member 31 and the elastic member 32. During forward rotation, the limit member 31 slides flexibly in the groove 22 to avoid wear. During reversal, the impact force is directly borne by the limit surface 23, and the elastic member 32 absorbs the collision energy, fundamentally solving the risk of valve plate breakage. The entire structure transforms the passive anti-reversal relying on gas sealing into a purely mechanical active locking, completely avoiding the defects of high-pressure gas leakage and reversal delay caused by sealing gaps in traditional structures.

[0029] In a specific embodiment, the other end of the limiter 31 is a first curved surface, the side wall of the groove 22 is a second curved surface, and the first curved surface cooperates with the second curved surface; when the crankshaft 1 rotates forward, the first curved surface slides along the second curved surface.

[0030] The end of the stopper 31 is designed as a first curved surface, and the sidewall of the groove 22 is correspondingly designed as a second curved surface, forming a curved surface-matching structure. This design ensures that the first curved surface of the stopper 31 and the second curved surface of the groove 22 always maintain point or line contact during contact, rather than a hard collision between two planes. Its core benefits are: the curved surface matching significantly reduces local stress on the contact surface, preventing scraping or jamming between the stopper 31 and the sidewall of the groove 22; and the curved surface profile guides the stopper 31 to slide smoothly along a predetermined trajectory, reducing motion resistance and ensuring interference-free operation of the anti-reverse mechanism during forward rotation of the crankshaft 1.

[0031] During forward rotation of the crankshaft 1, the first curved surface of the stopper 31 continuously slides along the second curved surface of the groove 22. This sliding contact is maintained by the radial elastic force of the elastic member 32, allowing the stopper 31 to adaptively expand and contract within the groove 22. This embodiment employs a sliding contact mode to replace the impact and collision of traditional valve discs, completely eliminating the risk of wear or breakage caused by high-frequency impact. Furthermore, the sliding contact of the curved surfaces allows the stopper 31 to adjust its radial position in real time according to the curvature of the groove 22, ensuring smooth operation.

[0032] In a specific embodiment, the limiting surface 23 is a vertically arranged plane, which is adjacent to the second curved surface; when the crankshaft 1 is reversed, the first curved surface and the plane form a block. Of course, the limiting surface 23 is not necessarily absolutely vertical.

[0033] Limiting surface 23 is a vertical plane perpendicular to the direction of rotation. This plane directly adjoins the second curved surface of groove 22, forming a continuous transition structure. This vertical plane provides a rigid, full-circumference barrier for limiting member 31, ensuring instantaneous surface contact between the first curved surface and limiting surface 23 during reversal, rather than point contact. This enhances impact resistance. Furthermore, this adjacent design ensures that limiting member 31 slides seamlessly from the second curved surface to the limiting surface 23, avoiding delayed locking due to lost motion and significantly improving anti-reversal response speed.

[0034] At the moment of crankshaft 1's reverse rotation, the first curved surface of stopper 31 forms a rigid surface contact barrier with the vertical plane of stopper surface 23. This surface barrier completely eliminates the slip component that could otherwise be generated by the curved surface structure, converting the impact force completely into an axial restraining force, thus instantly locking the reverse motion of crankshaft 1. Simultaneously, the surface contact pattern evenly distributes the impact load across the entire end of stopper 31, preventing deformation or fracture caused by localized stress concentration. This fundamentally addresses the reliability issue of valve disc fracture due to single-point impact in prior art.

[0035] In a specific embodiment, one end of the limiting member 31 has a matching hole 311 , and the other end of the elastic member 32 is located in the matching hole 311 .

[0036] A cylindrical mating hole 311 is provided at the end of the limiter 31, and the front end of the elastic member 32 is nested inside the mating hole 311 to form an embedded connection. After adopting this structure, firstly, the mating hole 311 forms a radial circumferential wrapping constraint on the end of the elastic member 32, completely preventing the elastic member 32 from slipping or deflecting laterally when the crankshaft 1 rotates at high speed or reverses, and ensuring that the elastic force transmission is always carried out along the axial centerline of the limiter 31. Secondly, the embedded connection significantly increases the contact area between the elastic member 32 and the limiter 31, so that the two are combined into a whole. During reversal, the buffering force of the elastic member 32 can be evenly spread to the entire end bearing surface of the limiter 31, avoiding deformation caused by local stress concentration. Finally, the depth design of the mating hole 311 allows the compression stroke of the elastic member 32 to be precisely limited within the hole, preventing the elastic member 32 from bending due to excessive compression, ensuring that it only undergoes axial elastic deformation, thereby maintaining the reliability of the anti-reversal mechanism in long-term high-frequency telescopic movement. This structure fundamentally optimizes the defects of traditional spring and pin stacking assembly that are prone to loosening and failure, providing stable response capabilities for high-speed scroll compressors.

[0037] In a specific embodiment, the crankshaft 1 has a central oil hole 12, and the through hole 11 is connected to the central oil hole 12 to form an oil supply channel; when the crankshaft 1 rotates, the lubricating oil enters the through hole 11 through the oil supply channel to lubricate the contact surface between the limit member 31 and the inner wall of the through hole 11.

[0038] A central oil hole 12 running axially is provided inside the crankshaft 1, and the central oil hole 12 is directly connected to the radial through hole 11 to form an internal oil supply channel. First, the oil supply path is highly integrated by integrating the internal oil circuit of the crankshaft 1, without the need for additional external oil pipes or lubrication structures, which significantly simplifies the overall assembly complexity of the compressor. Secondly, as part of the original oil supply system of the compressor, the central oil hole 12 can directly utilize the centrifugal pump effect generated when the crankshaft 1 rotates to actively transport lubricating oil, ensuring that the lubricating medium is continuously and stably injected into the through hole 11. Finally, the integrated oil circuit design completely avoids the risks of oil leakage, pipeline vibration fatigue or loose interfaces that may occur in traditional external oil pipes under high-speed operation, providing an inherently reliable lubrication guarantee basis for the anti-reversal mechanism.

[0039] During the rotation of the crankshaft 1, lubricating oil continuously flows from the center oil hole 12 into the interior of the through hole 11, forming an oil film on the sliding contact surface between the stopper 31 and the inner wall of the through hole 11. The oil film significantly reduces the friction coefficient of the stopper 31 during radial expansion and contraction, effectively suppressing micro-wear caused by dry friction and preventing the stopper 31 from getting stuck or wearing unevenly within the through hole 11. Furthermore, the lubricating oil continuously washes away metal debris and heat generated on the contact surface, preventing abrasive accumulation from causing damage to the kinematic pair. It also suppresses lubricating oil degradation caused by high temperatures, significantly extending the service life of the stopper 31 and the through hole 11.

[0040] In a specific embodiment, the first curved surface is a spherical surface, the second curved surface is an arc curved surface, and the curvature radius of the spherical surface is smaller than the curvature radius of the arc curved surface to form a line contact sliding fit.

[0041] The first curved surface of the stopper 31 adopts a spherical structure, and the second curved surface of the groove 22 is designed as an arc surface, and the curvature radius of the spherical surface is precisely smaller than the curvature radius of the arc surface. This geometric matching ensures that the spherical surface of the stopper 31 and the arc surface of the groove 22 form a stable line contact rather than point contact or surface contact when in contact. The line contact mode implemented in this embodiment significantly increases the effective bearing area and avoids the edge stress concentration phenomenon caused by slight alignment deviation between the spherical surface and the arc surface; when the crankshaft 1 rotates, the lubricating oil is actively brought into the contact line area and an oil film is established. The friction coefficient is significantly reduced compared to traditional surface contact, reducing the risk of adhesive wear between the stopper 31 and the groove 22. In addition, the line contact has an adaptive centering feature. Even if the crankshaft 1 has radial runout or assembly tolerance, the spherical surface of the stopper 31 can still automatically adjust the contact line position along the arc surface, ensuring that the anti-reversal mechanism maintains stable and low-noise operation during long-term high-frequency telescopic movement, completely solving the fatal defect of the valve plate breaking due to non-uniform impact in the background technology.

[0042] In a specific embodiment, there are four through holes 11, and the four through holes 11 are evenly distributed along the circumference of the crankshaft 1. Each through hole 11 is provided with a corresponding limiting member 31 and an elastic member 32; two limiting surfaces 23 are provided, and the two limiting surfaces are relatively arranged on the side walls of the groove 22.

[0043] Four through-holes 11 are symmetrically arranged in the radial cross-section of the crankshaft 1, spaced evenly along the circumference at 90° intervals. Each through-hole 11 houses an independent anti-reverse unit consisting of a stopper 31 and an elastic member 32. This layout ensures that the four sets of stoppers 31 create a circumferential force balance during crankshaft 1 rotation, eliminating vibrations caused by unbalanced loading. Furthermore, the multi-redundant design ensures that even if any three stoppers 31 fail, the remaining units can still independently perform the anti-reverse function, significantly improving the system's fault tolerance. Two stopper surfaces 23 are symmetrically arranged on the sidewalls of the groove 22, with a phase difference of 180°. Each stopper surface 23 is a vertical plane that smoothly merges with the circular curved surface of the groove 22. The core function of the dual stopper surfaces 23 is to exponentially increase the density of blocking points: when the crankshaft 1 reverses, regardless of the initial stopping angle, the stopper 31 will always reach the nearest stopper surface 23 within a smaller reversal angle. For example, if only a single limit surface is provided, a maximum reversal of 90° is required to be blocked, while a double limit surface reduces the maximum reversal stroke by 50%.

[0044] The four groups of limit members 31 and the double limit surfaces 23 work together to form a high-density anti-reversal structure. At the moment of crankshaft 1 reversal, at least two limit members 31 can synchronously contact the corresponding limit surfaces 23 within a 45° range: for example, when reversing counterclockwise, the limit member 31 at the 0° phase will contact the 0° limit surface 23, while the limit member 31 at the 180° phase will contact the 180° limit surface 23, thus achieving dual-point synchronous blocking. This arrangement shortens the blocking stroke and improves the anti-reversal response speed; moreover, the double limit members 31 share the impact load, completely avoiding the risk of overload fracture; in addition, the circumferential uniform distribution of the four limit members 31 and the symmetrical layout of the double limit surfaces 23 constitute a torque self-balancing system, and the reversal impact force is decomposed into two pairs of opposite force couples, eliminating the hidden dangers of deflection friction of the crankshaft 1 and unilateral wear of the bearing of the lower bracket 2, significantly extending the life of the compressor.

[0045] In a specific embodiment, two limiting surfaces 23 are provided, and the two limiting surfaces 23 are symmetrically distributed at 180° with the crankshaft axis as the center, and when any of the limiting members 31 contacts the limiting surface 23, the maximum reversal angle of the crankshaft 1 is no more than 90°.

[0046] The two limit surfaces 23 are symmetrically arranged with the axis of the crankshaft 1 as the center, and cooperate with the four evenly distributed through holes 11 to lock the crankshaft 1 within a very short stroke when it is reversed. In any stop position, there is always a limit member 31 that is no more than 45° away from the nearest limit surface 23. When the crankshaft 1 reverses, the limit member 31 is blocked after sliding 45°. At this time, the maximum reversal angle of the crankshaft 1 is constrained within 90° (for example: if the initial position of the limit member 31 is 45° away from the limit surface 23, the reversal of 45° will be blocked; if it is initially close to the limit surface 23, the reversal of nearly 0° will be blocked). This embodiment achieves a faster response speed and completely solves the reversal delay problem; in addition, the double limit surfaces 23 allow the impact force to be shared by the two limit members 31, avoiding overload and breakage of a single component.

[0047] In a specific embodiment, the elastic member 32 is a spring. The elastic member 32 adopts a spring structure. The linear elastic characteristics of the spring enable the limit member 31 to accurately expand and contract along the curved surface contour of the groove 22 when the crankshaft 1 rotates forward, and always maintain a flexible contact pressure with the side wall of the groove 22, thereby avoiding jamming or detachment caused by processing tolerances. When the limit member 31 hits the limit surface 23 when the crankshaft 1 reverses, the spring absorbs the impact kinetic energy through its own compression deformation, significantly reducing the rigid collision stress between the limit member 31 and the limit surface 23, and fundamentally solving the problem of traditional valve plate breakage. In addition, the spring's fatigue life characteristics of millions of times ensure that the anti-reversal mechanism can operate reliably for a long time under the high-frequency start-stop conditions of the compressor, and its automatic reset function enables the limit member 31 to quickly return to the ready state after each obstruction, which reduces the maintenance cost compared to hydraulic or pneumatic buffer solutions.

[0048] When the scroll compressor is operating normally, the crankshaft 1 rotates forward under the drive of the motor, and the crankshaft 1 inserted into the center hole 21 of the lower bracket 2 drives the limiter 31 in the radial through hole 11 to rotate synchronously. At this time, the spring of the elastic member 32 continuously applies radial thrust through the matching hole 311 of the limiter 31, pushing the spherical end of the limiter 31 to slide close to the arc surface of the groove 22. The curved surface profile of the groove 22 guides the limiter 31 to perform adaptive telescopic movement during sliding, and the elastic deformation of the spring compensates for the manufacturing tolerance to ensure that there is no jamming during the sliding process. At the same time, the center oil hole 12 of the crankshaft 1 continuously supplies lubricating oil to the through hole 11, forming an oil film between the limiter 31 and the inner wall of the through hole 11, significantly reducing friction and wear. The circumferential uniform distribution of the four groups of through holes 11 balances the centrifugal force and avoids vibration of the crankshaft 1.

[0049] At the moment the compressor stops, the high-pressure gas on the exhaust side flows back to push the crankshaft 1 to reverse. At this time, the limiter 31 remains in a radially extended state under the action of the spring, and the two limiter surfaces 23 symmetrically arranged in the groove 22 immediately take effect: no matter what the initial stop angle of the crankshaft 1 is, the closest limiter 31 must contact the corresponding limiter surface 23 within a 45° reversal range. For example, when the 0° phase limiter 31 touches the 0° limiter surface 23, the 180° phase limiter 31 simultaneously touches the 180° limiter surface 23, forming a two-point rigid blockage. The spherical surface of the limiter 31 forms a surface contact with the vertical limiter surface 23, most of the impact force is absorbed by the spring, and the remaining load is evenly shared by the two limiters 31. This process constrains the maximum reversal angle of the crankshaft 1 to within 90°, which is significantly shorter than the reversal stroke of the traditional solution. After the blocking is completed, the spring automatically resets and the limiter 31 returns to the ready state. During the entire process, the lubricating oil continuously flushes the contact surface, removes the wear debris and cools the moving pair, ensuring long-term and reliable operation of the mechanism.

[0050] Example 2: This embodiment provides a compressor, such as Figure 9 and Figure 10 As shown, the compressor includes a crankshaft 1, a lower bracket 2, a shell 4, a compression assembly 5, a drive assembly 6 and the anti-reversal structure 3 described in Example 1. The crankshaft 1, the lower bracket 2, the compression assembly 5 and the drive assembly 6 are all arranged in the shell 4, and the anti-reversal structure 3 is arranged between the through hole 11 and the groove 22.

[0051] The compression assembly 5 includes a fixed scroll 51, an orbiting scroll 52, and an Oldham ring 53. The drive assembly 6 includes a motor rotor 61 and a motor stator 62. The housing 4 includes an upper cover 41, a body 42, and a lower cover 43.

[0052] In this embodiment, the housing 4 comprises an upper cover 41, a main body 42, and a lower cover 43, which are sealed together to form a sealed container. The lower bracket 2 and motor stator 62 are fixedly mounted within the main body 42. The upper end of the crankshaft 1 passes through the center hole 21 of the lower bracket 2 and connects to the orbiting scroll 52 of the compression assembly 5. The lower end connects to the motor rotor 61 of the drive assembly 6. The central portion of the crankshaft 1 is rotatably supported by the center hole 21 of the lower bracket 2. The fixed scroll 51 of the compression assembly 5 is fixed to the upper portion of the main body 42 and meshes with the orbiting scroll 52 via a cross ring 53. The stopper 31 and elastic member 32 of the anti-reverse mechanism 3 are embedded in the four radial through-holes 11 of the crankshaft 1. The spherical end of the stopper 31 spatially corresponds to the arc-shaped curved surface of the groove 22 of the lower bracket 2 and the two 180° symmetrical stopper surfaces 23. The motor rotor 61 is sleeved over the lower end of the crankshaft 1. The motor stator 62 is press-fitted onto the inner wall of the main body 42 and forms an electromagnetic coupling with the motor rotor 61. The lower cover 43 seals the bottom of the shell 4 , and the upper cover 41 is provided with an exhaust passage communicating with the central exhaust hole of the fixed scroll 51 .

[0053] When the compressor starts, the motor stator 62 of the drive assembly 6 excites the motor rotor 61 to rotate, driving the crankshaft 1 to rotate in the forward direction. The crankshaft 1 drives the movable scroll 52 of the compression assembly 5 to rotate and translate through the cross ring 53, forming a crescent-shaped compression chamber with the static scroll 51: the low-temperature refrigerant enters from the air intake of the static scroll 51, is pushed to the center for compression, and is discharged through the exhaust channel of the upper cover 41. At this time, the limiter 31 of the anti-reversal structure 3, under the spring thrust of the elastic member 32, its spherical surface slides adaptively along the arc surface of the groove 22 of the lower bracket 2, and the lubricating oil lubricates the contact pair from the central oil hole 12 of the crankshaft 1 through the through hole 11. The 90° circumferential distribution of the four sets of limiters 31 offsets the centrifugal force vibration. At the moment of shutdown, the high-pressure gas on the exhaust side flows back to the compression chamber through the upper cover 41, pushing the movable scroll 52 to apply force in the opposite direction to reverse the crankshaft 1. At this point, the nearest stopper 31 contacts the limit surface 23 of the groove 22 within a reversal angle of no more than 45° (for example, the 0° stopper 31 contacts the 0° limit surface 23). Simultaneously, the 180°-opposite stopper 31 contacts the 180° limit surface 23. This dual-point rigid block locks the crankshaft 1 within its maximum reversal travel of 90°. The spring absorbs most of the impact energy, the lubricating oil cools the friction surfaces, and the sealed environment of the housing 4 ensures reliable resetting of the moving parts, completely eliminating the traditional valve plate breakage and reversal noise problems.

[0054] The compressor of this embodiment realizes efficient and reliable operation in the closed environment of the shell 4 by integrating the anti-reversal structure 3 of embodiment 1: during normal operation, the motor rotor 61 of the drive component 6 drives the crankshaft 1 to rotate forward, so that the static scroll 51 and the movable scroll 52 of the compression component 5 engage to compress the refrigerant; when the high-pressure gas flows back at the moment of shutdown, the four groups of limit members 31 of the anti-reversal structure 3 synchronously touch the double limit surfaces 23 of the groove 22 of the lower bracket 2 within the 45° reversal stroke, constraining the maximum reversal angle of the crankshaft 1 within 90°, and the spring absorbs impact energy and cooperates with the continuous lubrication of the center oil hole 12 of the crankshaft 1, completely eliminating the risk of traditional valve plate breakage and reversal noise.

[0055] In summary, it is easy for those skilled in the art to understand that, under the premise of no conflict, the above-mentioned advantageous technical features can be freely combined and superimposed.

[0056] The above are merely preferred embodiments of the present invention and do not constitute any form of limitation to the present invention. Any simple modifications, equivalent changes and modifications made to the above embodiments based on the technical essence of the present invention still fall within the scope of the technical solution of the present invention.

Claims

1. An anti-reversal structure, characterized in that: The anti-reversal structure is used to prevent the crankshaft from reversing. The crankshaft is inserted into the center hole of the lower bracket. The crankshaft is radially provided with a through hole. The side wall of the center hole has a groove, and the side wall of the groove has a limiting surface. The anti-reversal structure includes a limiting member and an elastic member. One end of the elastic member abuts against the through hole, and the other end of the elastic member cooperates with one end of the limiting member. The other end of the limiting member can slide in contact with the side wall of the groove when the crankshaft rotates forward, and can be blocked by the limiting surface when the groove reverses.

2. The anti-reversal structure according to claim 1, characterized in that: The other end of the limiting member is a first curved surface, the side wall of the groove is a second curved surface, and the first curved surface cooperates with the second curved surface; when the crankshaft rotates forward, the first curved surface slides along the second curved surface.

3. The anti-reversal structure according to claim 2, characterized in that: The limiting surface is a vertically arranged plane, and the plane is adjacent to the second curved surface; when the crankshaft is reversed, the first curved surface and the plane form an obstruction.

4. The anti-reversal structure according to claim 1, characterized in that: One end of the limiting member is provided with a matching hole, and the other end of the elastic member is located in the matching hole.

5. The anti-reversal structure according to claim 1, characterized in that: The crankshaft has a central oil hole, and the through hole is connected to the central oil hole to form an oil supply channel; when the crankshaft rotates, lubricating oil enters the through hole through the oil supply channel to lubricate the contact surface between the limit member and the inner wall of the through hole.

6. The anti-reversal structure according to claim 2, characterized in that: The first curved surface is a spherical surface, and the second curved surface is an arc curved surface. The curvature radius of the spherical surface is smaller than the curvature radius of the arc curved surface to form a line contact sliding fit.

7. The anti-reversal structure according to claim 1, characterized in that: There are four through holes, which are evenly distributed along the circumference of the crankshaft, and each through hole is provided with a corresponding limiting member and elastic member; there are two limiting surfaces, which are arranged oppositely on the side walls of the groove.

8. The anti-reversal structure according to claim 1, characterized in that: Two limiting surfaces are provided, and the two limiting surfaces are symmetrically distributed at 180° with the crankshaft axis as the center, and when any one of the limiting members contacts the limiting surface, the maximum reversal angle of the crankshaft is no more than 90°.

9. The anti-reversal structure according to any one of claims 1 to 8, characterized in that: The elastic member is a spring.

10. A compressor comprising a crankshaft, a lower bracket, a housing, a compression assembly, a drive assembly, and the anti-reverse structure according to any one of claims 1 to 9, characterized in that: The crankshaft, the lower bracket, the compression assembly and the driving assembly are all arranged in the housing, and the anti-reversal structure is arranged between the through hole and the groove.

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