Piston assembly, pump body, compressor and refrigeration device

Abstract

This invention provides a piston assembly, a pump body, a compressor, and a refrigeration device. The piston assembly serves as the pump body for the compressor and includes: a piston body with a hinge portion on its outer peripheral surface; a hinge member disposed at and cooperating with the hinge portion; and a sliding plate, one end of which is disposed at the hinge member. The sliding plate and the piston body are hinged together through the cooperation of the hinge portion and the hinge member. The piston assembly provided by this invention additionally provides a separate hinge member for hinged connection with the piston body, thus increasing the contact area with the hinge portion compared to a solution where the sliding plate directly abuts against the piston body. This reduces frictional power consumption while ensuring no refrigerant leakage. This not only improves the energy efficiency of the compressor and reduces unnecessary energy loss but also reduces heat generation during compressor operation, extends the service life of various components, and reduces maintenance costs.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, and more specifically, to a piston assembly, a pump body, a compressor, and a refrigeration device. Background Technology

[0002] In the field of rotary compressors, the core working structure involves the piston and vane separating the internal space of the cylinder through arc-shaped contact, forming independent intake and exhaust sides. This structure is the key foundation for the compressor to complete the intake and exhaust cycle. Currently, the contact force between the piston and vane is mainly provided by a spring at the tail of the vane. The magnitude of this contact force directly determines the refrigerant leakage at the arc-shaped tip of the vane during compressor operation. Refrigerant easily leaks from the high-pressure side of the cylinder through the gap between the vane tip and the piston arc-shaped surface to the low-pressure side, and this leakage problem has a significant impact on the compressor's energy efficiency. However, the existing structure relying on springs to provide contact force presents an irreconcilable technical contradiction: under the same operating conditions, increasing the contact force provided by the spring can reduce the gap between the vane tip and the piston arc-shaped surface, thereby reducing refrigerant leakage, but it also leads to increased friction between the vane, piston, and cylinder, significantly increasing the compressor's power consumption. Conversely, reducing the contact force to reduce frictional power consumption will increase the gap at the vane tip, leading to increased refrigerant leakage, which will also affect the compressor's energy efficiency.

[0003] Therefore, designing a piston assembly that can reduce refrigerant leakage at the tip of the vane and reduce frictional power consumption, thus achieving synergistic optimization of both, has become an urgent problem to be solved. Summary of the Invention

[0004] The present invention aims to at least solve the problems of large refrigerant leakage and high frictional power consumption at the tip of the sliding vane in related technologies.

[0005] Therefore, a first aspect of the present invention provides a piston assembly.

[0006] A second aspect of the present invention provides a pump body.

[0007] A third aspect of the present invention provides a compressor.

[0008] A fourth aspect of the present invention provides a refrigeration device.

[0009] In view of this, a first aspect of the present invention provides a piston assembly for a pump body of a compressor, the piston assembly comprising: a piston body having a hinge portion on its outer peripheral surface; a hinge member disposed on the hinge portion and cooperating with the hinge portion; and a slide plate having one end disposed on the hinge member, the slide plate and the piston body being hinged together by the cooperation of the hinge portion and the hinge member.

[0010] The piston assembly provided by this invention can be used in the pump body of a compressor. For example, the piston assembly can cooperate with the cylinder of the pump body to compress refrigerant. The piston assembly includes a piston body, a hinge, and a slide. The outer peripheral surface of the piston assembly has a hinge portion. The hinge can be mounted on the hinge portion and cooperate with it. One end of the slide is connected to the hinge. Thus, when the piston body swings, the piston body and the slide can be hinged through the hinge. It is understood that, because this application additionally provides a separate hinge for hinged connection with the piston body, compared to the solution where the slide directly abuts against the piston body, this application increases the contact area with the hinge portion by separately providing a hinge for hinged connection with the piston body. During the working swing of the piston body, this larger contact area can effectively reduce the fit clearance between the hinge and the hinge portion, thereby significantly reducing the possibility of refrigerant leaking from the high-pressure side of the cylinder to the low-pressure side through this fit clearance. Compared to the traditional method of relying on increased spring resistance to reduce gaps, this application directly solves the refrigerant leakage problem caused by gaps through structural design, improving the compressor's refrigerant compression efficiency and thus enhancing the compressor's overall energy efficiency. Furthermore, since there's no need to increase spring resistance to prevent refrigerant leakage as in traditional solutions, the friction between the vane, piston body, and cylinder is reduced. In traditional structures, while increasing spring resistance reduces refrigerant leakage, it exacerbates friction between the vane and other components, increasing power consumption. However, the piston assembly in this application, through optimized connection structure, reduces frictional power consumption while ensuring no refrigerant leakage. This not only improves the compressor's energy utilization efficiency and reduces unnecessary energy loss but also reduces heat generation during compressor operation, extends the service life of components, and reduces maintenance costs.

[0011] Furthermore, compared to a design that hinges the sliding plate to the piston body at one end, this application reduces the machining difficulty of the sliding plate and improves machining efficiency. Simultaneously, the separate design of the sliding plate and the hinge component alleviates stress concentration, reduces the risk of fatigue fracture at the connection point, and improves structural reliability.

[0012] In some embodiments, the hinge portion is optionally a hinge groove disposed on the outer peripheral surface of the piston body, and the hinge element is a cylindrical pin disposed in the hinge groove. Both the hinge groove and the cylindrical pin extend along the thickness direction of the piston body.

[0013] In these embodiments, the hinge portion can be a hinge groove provided on the outer peripheral surface of the piston body. The hinge element can be a cylindrical pin, which is installed in this hinge groove. Both the hinge groove and the cylindrical pin extend along the thickness direction of the piston body. One end of the slide is connected to the cylindrical pin, and the hinge between the slide and the piston body is achieved through the engagement of the cylindrical pin and the hinge groove. When the piston body oscillates within the cylinder to compress the refrigerant, the cylindrical pin rotates within the hinge groove, allowing the slide to slide within the cylinder's groove. By setting the hinge groove to engage with the cylindrical pin, the outer peripheral surface of the cylindrical pin contacts the inner peripheral surface of the hinge groove. Compared to the slide directly contacting the piston body, this increases the contact length and contact area with the piston body, making it more difficult for the refrigerant to leak from the fit gap when the piston body oscillates, thus improving compressor efficiency. Simultaneously, due to the increased contact area, a sealing effect can be ensured without excessive contact force, reducing friction between the slide and the piston body / cylinder, lowering frictional power consumption, reducing component wear, and extending service life.

[0014] In some embodiments, the outer peripheral surface of the cylindrical pin is optionally provided with a groove extending along the axial direction of the cylindrical pin, one end of the slide is located in the groove, and the portion of the slide located in the groove is adapted to the groove.

[0015] In these embodiments, a groove can be provided on the outer circumferential surface of the cylindrical pin, extending along the axial direction of the cylindrical pin. This allows one end of the sliding vane to be fitted into the groove, achieving a connection between the vane and the cylindrical pin. The precise fit between the groove on the outer circumferential surface of the cylindrical pin and one end of the sliding vane greatly enhances the stability of the connection between the cylindrical pin and the sliding vane. During compressor operation, various complex forces and vibrations are generated, and this fitting structure can effectively resist these external forces, reducing the risk of the sliding vane dislodging from the groove of the cylindrical pin. For example, when the compressor operates at high speed, even under the influence of large centrifugal forces and vibrations, the sliding vane can still be firmly held in the groove, working in conjunction with the cylindrical pin to ensure the normal operation of the piston assembly and improve the overall reliability of the compressor.

[0016] In some embodiments, the portion of the slide located within the groove may optionally have a clearance fit with the groove.

[0017] In these embodiments, the portion of the slide plate located within the groove has a clearance fit with the groove. This clearance fit allows the slide plate to better adapt to changes in the piston's motion. During compressor operation, the piston's speed, direction, and stress conditions constantly change. The clearance between the slide plate and the groove provides the slide plate with a certain amount of buffering and adjustment space, allowing it to more flexibly follow the piston's movement under different operating conditions. For example, when the compressor load suddenly changes, the piston's swing amplitude may change. The slide plate can adjust its position within the groove through the clearance, maintaining a good fit with the piston and cylinder, ensuring stable compressor operation. The clearance fit also facilitates assembly. Compared to tight-fitting methods requiring high-precision installation, the clearance fit allows for installation adjustments within a certain range, reducing assembly difficulty and improving production efficiency. Furthermore, during equipment maintenance, if the slide plate or cylindrical pin needs to be replaced, the clearance fit makes disassembly easier, facilitating maintenance personnel and further improving equipment maintainability.

[0018] In some embodiments, the depth of the groove may be greater than or equal to 0.2 times the diameter of the cylindrical pin and less than or equal to 0.9 times the diameter of the cylindrical pin.

[0019] In these embodiments, the depth of the groove is greater than or equal to 0.2 times the diameter of the cylindrical pin and less than or equal to 0.9 times the diameter of the cylindrical pin. By limiting the depth of the groove, a good balance between the stability and flexibility of the connection between the slide and the cylindrical pin is ensured. When the groove depth is greater than or equal to 0.2 times the diameter of the cylindrical pin, the slide has sufficient embedment depth within the groove, ensuring a firm connection between the two during movement. This effectively transmits the movement and force of the piston body, and even under the vibration generated by the compressor operation and the action of complex external forces, the slide is not easily dislodged from the groove. Meanwhile, the groove depth being less than or equal to 0.9 times the diameter of the cylindrical pin ensures the strength of the cylindrical pin itself, preventing it from being easily damaged due to insufficient strength.

[0020] In some embodiments, the slider may be positioned at a depth greater than or equal to 0.3 times the depth of the groove.

[0021] In these embodiments, the depth of the slide within the groove can be limited to greater than or equal to 0.3 times the groove depth. A certain embedding depth of the slide within the groove enhances the stability of the connection between the slide and the cylindrical pin. During compressor operation, various complex forces are generated, such as centrifugal force, inertial force, and forces arising from changes in refrigerant pressure. Sufficient embedding depth strengthens the bond between the slide and the cylindrical pin, effectively resisting these external forces and ensuring the slide stably follows the movement of the cylindrical pin within the groove. Simultaneously, sufficient embedding depth of the slide within the groove makes its position more stable during movement, thereby better controlling the gap between the slide and the cylindrical pin and preventing refrigerant leakage from these areas.

[0022] In some embodiments, optionally, the cylindrical pin has a continuous curved surface along its circumferential direction, the angle of the continuous curved surface being greater than or equal to 120°.

[0023] In these embodiments, the cylindrical pin has a continuous curved surface along its circumferential direction, with an angle greater than or equal to 120°. By setting a continuous curved surface with an angle greater than or equal to 120° in the circumferential direction of the cylindrical pin, synergistic optimization of refrigerant leakage at the tip of the slide and frictional power consumption at the hinge is achieved. Specifically, this large-angle continuous curved surface forms a larger and more stable arc surface fit with the hinge groove of the piston body. This design, on the one hand, expands the circumferential coverage of the sealing contact zone, significantly extending the potential leakage path of the refrigerant, thereby enhancing the stability and continuity of the seal at the structural root and effectively suppressing refrigerant leakage from the hinge gap. On the other hand, the wide contact surface significantly reduces the local contact stress of the hinge pair, which reduces the preload required for the spring on the back of the slide while maintaining the same sealing effect, thereby directly reducing the sliding frictional power consumption between the slide and the cylinder. At the same time, the lower contact stress also significantly reduces the wear of the cylindrical pin and the hinge groove itself. Therefore, this design works together from two dimensions: "enhanced sealing" and "reduced load and wear," effectively resolving the technical contradiction of the traditional solution where "leakage prevention" and "low friction" are difficult to achieve simultaneously. This improves the compressor's energy efficiency while also enhancing its operational reliability.

[0024] In some embodiments, optionally, the groove is U-shaped along the axial direction of the cylindrical pin, the width of the groove is B0, and the thickness of the slider is B1 in the width direction of the groove, wherein B0-B1≤50μm.

[0025] In these embodiments, the groove is U-shaped along the axial direction of the cylindrical pin. The width of the U-shaped groove is B0, and the thickness of the slide is B1 in the width direction of the groove, where B0-B1≤50μm. By limiting the difference between the groove width B0 and the slide thickness B1 to less than or equal to 50μm, a synergistic effect of maximizing refrigerant leakage and reducing frictional losses is achieved while ensuring flexible slide movement. Specifically, this micron-level gap significantly limits the flow cross-sectional area of ​​refrigerant leakage between the slide and the groove sidewall, effectively blocking the main leakage path from the high-pressure side to the low-pressure side, thereby significantly improving sealing performance and compressor efficiency. On the other hand, the precise fit significantly enhances the radial positioning stability of the slide in the groove, greatly reducing its lateral sway and impact during operation. This not only reduces the power consumption and wear caused by collision and friction between the slide and the groove, but also makes the transmission of driving force more stable and direct, further improving mechanical efficiency and operational reliability, and optimizing the contradictory relationship between leakage and friction in traditional structures.

[0026] In some embodiments, optionally, the groove is V-shaped along the axial direction of the cylindrical pin, and the bottom width of the groove is less than the minimum width of one end of the slider.

[0027] In these embodiments, the groove is V-shaped along the axial direction of the cylindrical pin, with the bottom width of the groove being less than the minimum width of one end of the slide. By designing the groove as V-shaped and limiting its bottom width to be less than the minimum width of one end of the slide, a synergistic optimization of guiding stability and effective sealing is achieved while reducing frictional losses. Specifically, this structure allows the end of the slide to form line contact or partial small-area contact with the two inclined surfaces of the V-shaped groove. At the sealing level, this contact form and dimensional fit create a varying wedge-shaped gap between the slide and the cylindrical pin, significantly extending the refrigerant leakage path and increasing flow resistance, forming a highly efficient "labyrinth" sealing effect. This effectively suppresses lateral refrigerant leakage through the hinge and improves the volumetric efficiency of the compressor. At the friction and operation level, the inclined surfaces of the V-groove provide precise radial positioning and automatic centering guidance for the slide, greatly limiting its lateral movement and impact during operation and ensuring smooth movement. At the same time, the line contact mode significantly reduces the contact area compared to the surface contact, which not only directly reduces sliding friction power consumption but also facilitates the formation and retention of lubricating oil in the contact area, further reducing wear. Furthermore, this structure is more adaptable to machining and assembly errors of parts, thus improving reliability. Therefore, this design, through a unique "V-shaped guide contact" and "wedge seal" mechanism, synergistically optimizes leak-proof and low-friction performance.

[0028] In some embodiments, optionally, the groove is V-shaped along the axial direction of the cylindrical pin, the included angle of the groove is a2, the shape of the portion of the slider located inside the groove is V-shaped, and the included angle of the slider is a1, wherein -60°≤a1-a2≤60°.

[0029] In these embodiments, along the axial direction of the cylindrical pin, the groove is V-shaped with an included angle of a2. The portion of the slide plate located within the groove is also V-shaped with an included angle of a1, where -60° ≤ a1 - a2 ≤ 60°. By limiting the difference between the included angle a1 of the slide plate and the included angle a2 of the groove to a range of -60° to 60°, synergistic optimization of sealing performance and friction loss is achieved under diverse contact conditions. Specifically, this angular tolerance design allows the slide plate and the V-shaped inclined surface of the groove to form various controllable fit states, ranging from surface contact to stable line contact. At the sealing level, regardless of whether the two are tightly fitted or have a small wedge gap, this fit effectively extends the refrigerant leakage path and forms a local throttling effect, thereby significantly suppressing lateral refrigerant leakage through the hinge and ensuring the volumetric efficiency of the compressor. At the friction and operation level, this design avoids local stress concentration or point contact caused by severe angular mismatch, resulting in a more reasonable contact pressure distribution and reducing frictional power consumption and wear. Meanwhile, the inherent centering and guiding characteristics of the V-shaped structure are fully utilized, ensuring the smoothness and reliability of the slider's movement. Furthermore, this limited angle range enhances adaptability to manufacturing and assembly errors, improving production feasibility.

[0030] In some embodiments, the hinge groove and the cylindrical pin may optionally be clearance fit.

[0031] In these embodiments, the hinge groove and the cylindrical pin are in a clearance fit. By setting a clearance fit between the hinge groove and the cylindrical pin, synergistic optimization is achieved in multiple aspects, including controlling refrigerant leakage, reducing frictional power consumption, improving operational reliability, and facilitating assembly. Specifically, in terms of sealing, this clearance, together with the large-angle continuous curved surface of the cylindrical pin, forms a tortuous leakage channel, significantly increasing the flow resistance of the refrigerant, thereby effectively suppressing leakage without relying on interference compression and ensuring compression efficiency. In terms of friction and operation, the clearance fit avoids rigid contact, greatly reducing friction and wear between the hinge pairs, directly reducing power consumption. At the same time, the reserved reasonable clearance provides the necessary compensation space for the thermal expansion of parts and manufacturing tolerances, effectively preventing the risk of jamming and enhancing the reliability of the component under high-speed variable operating conditions. In addition, the clearance fit reduces the stringent requirements for assembly precision, making assembly more convenient.

[0032] In some embodiments, optionally, the hinge groove is circular with an opening along the thickness direction of the piston body, and the width of the opening is greater than or equal to the diameter of the hinge groove minus 0.3 mm and less than or equal to the diameter of the hinge groove minus 0.1 mm.

[0033] In these embodiments, along the thickness direction of the piston body, the hinge groove is a circular opening with a width greater than or equal to the diameter of the hinge groove minus 0.3 mm and less than or equal to the diameter of the hinge groove minus 0.1 mm. By setting the opening width of the hinge groove within the range of "hinge groove diameter minus 0.3 mm" to "hinge groove diameter minus 0.1 mm", the constraint stability, sealing reliability, and operational smoothness of the cylindrical pin are optimized while ensuring assembly feasibility. Specifically, this design first ensures that the cylindrical pin can be smoothly and efficiently installed into the hinge groove, meeting the assembly process requirements of mass production. More importantly, the precisely controlled opening width forms a tight and reasonable radial constraint with the cylindrical pin, effectively limiting the radial movement and vibration of the cylindrical pin during operation, thereby stabilizing the relative position of the sliding vane and the piston body. This stability directly translates into two core benefits: in terms of sealing, it allows a uniform and controllable small gap to be maintained between the cylindrical pin and the hinge groove, effectively suppressing refrigerant leakage along this path. In terms of mechanical performance, it avoids impact, noise, and abnormal wear caused by an excessively loose fit, reduces frictional power consumption, and improves the lifespan of the hinge pair and overall operational reliability. Therefore, this refined design of the opening width achieves the best balance between "easy assembly," "stable constraint," and "reliable operation."

[0034] In some embodiments, optionally, along the axial direction of the cylindrical pin, the outer diameter of the cylindrical pin is D0, and the inner diameter of the hinge groove is D1, wherein 5μm≤D1-D0≤80μm.

[0035] In these embodiments, along the axial direction of the cylindrical pin, the outer diameter of the cylindrical pin is D0, and the inner diameter of the hinge groove is D1, where 5μm≤D1-D0≤80μm. By controlling the difference between the inner diameter D1 of the hinge groove and the outer diameter D0 of the cylindrical pin within the range of 5μm to 80μm, synergistic optimization of refrigerant leakage, friction loss, and operational reliability is achieved under extremely small and uniform fit clearance. Specifically, this clearance range design allows the cylindrical pin to rotate smoothly within the hinge groove while being precisely constrained. In terms of sealing, this uniform, micron-level clearance greatly limits the flow cross-sectional area and flow velocity of refrigerant leakage. Combined with the large-angle continuous curved surface of the cylindrical pin, it forms a highly efficient labyrinth seal effect, thereby significantly reducing the amount of refrigerant leakage through the hinge pair. In terms of friction and operation, this clearance ensures that the rotating pair is in a good fluid lubrication state, avoiding dry friction or boundary friction between metals, directly reducing frictional power consumption and wear. Meanwhile, precise clearance control prevents impacts, vibrations, and noise caused by excessively loose fits, thus improving operational stability and reliability.

[0036] In some embodiments, the surface hardness of the hinge member may be greater than the surface hardness of the hinge portion.

[0037] In these embodiments, by setting the surface hardness of the hinge component to be higher than that of the hinge portion, a synergistic optimization is achieved in maintaining stable sealing performance, reducing friction and wear, and improving the overall lifespan and operational economy of the components during long-term operation. Specifically, in terms of sealing and fit stability, the harder hinge component can better resist plastic deformation and wear under cyclic loads, thereby maintaining the precisely designed initial fit clearance between the hinge component and the hinge slot for a long time. This avoids the problem of increased refrigerant leakage caused by the increased clearance due to rapid wear of the hinge component, ensuring the compressor's sustained and efficient operation.

[0038] In some embodiments, the hinge may optionally have a hardness greater than HRC20 (Rockwell Hardness C Scale 20, where the hardness value on the Rockwell hardness C scale is 20).

[0039] In these embodiments, by limiting the hardness of the hinge to greater than HRC20, it is ensured that the hinge has sufficient basic strength and resistance to deformation, and can reliably transmit working loads.

[0040] In some embodiments, optionally, along the thickness direction of the piston body, the height of the hinge is H0, the height of the piston body is H1, and the height of the slider is H2; wherein, -30μm≤H1-H0≤30μm; or -30μm≤H0-H2≤30μm; or H2≤H0≤H1.

[0041] In these embodiments, along the thickness direction of the piston body, the height of the hinge is H0, the height of the piston body is H1, and the height of the sliding vane is H2; wherein, -30μm≤H1-H0≤30μm; or -30μm≤H0-H2≤30μm; or H2≤H0≤H1. By defining the dimensional relationship between the hinge height H0, the piston body height H1, and the sliding vane height H2, synergistic optimization of end-face sealing, friction uniformity, and operational reliability in the axial dimension of the compressor is achieved. Specifically, firstly, the precise equivalence of H1 and H0 (within ±30μm) ensures that after the hinge is installed in the piston body, its end face is nearly flush with the piston body end face. This minimizes or even eliminates the refrigerant leakage path that may occur axially through the gap between the hinge end and adjacent components, greatly suppressing axial leakage. Secondly, the precise matching of H0 and H2 (within ±30μm) ensures optimal fit and load-bearing relationship between the slide and the cylindrical pin in the height direction. This avoids abnormal local contact and friction caused by an excessively high slide, and also prevents uneven force or poor lubrication caused by an excessively low slide, thereby reducing frictional power consumption and wear. Finally, the hierarchical relationship of H2≤H0≤H1 clearly defines the reasonable allocation of axial space, prevents motion interference, and ensures smooth and stable movement of the piston assembly within the cylinder.

[0042] In some embodiments, the material of the hinge may optionally include at least one or a combination of the following: carbon steel, stainless steel, and bearing steel.

[0043] In these embodiments, by limiting the material of the hinge to a combination of carbon steel, stainless steel and / or bearing steel, the core requirements of high strength and high wear resistance of the hinge are met, while also taking into account corrosion resistance, processability and economy, thus providing key material assurance for the long-term stable, efficient and reliable operation of the piston assembly.

[0044] In some embodiments, the surface of the hinge may optionally have a hardened layer or coating.

[0045] In these embodiments, by providing a hardened layer or coating to the surface of the hinge, the wear resistance of the hinge pair is significantly improved, the coefficient of friction is reduced, and the corrosion resistance is enhanced, thereby achieving the key effect of maintaining a low leakage and low friction state continuously and stably during the long-term operation of the compressor.

[0046] In some embodiments, the other end of the slider may optionally have a spring mounting groove.

[0047] In these embodiments, by providing a spring mounting groove for the slide at the opposite end to the hinge, the advantages of traditional spring force application are retained while working in conjunction with the novel hinge structure. This achieves a comprehensive effect of efficient sealing, low-friction operation, and stable reliability under a more optimized spring force setting. Specifically, this spring mounting groove allows the spring to provide a basic resisting force towards the piston center to the slide in a traditional and reliable manner.

[0048] A second aspect of the invention provides a pump body comprising the piston assembly of any of the technical solutions in the first aspect.

[0049] The pump body provided by this invention includes the piston assembly as described in any of the technical solutions of the first aspect. Since the pump body includes the piston assembly as described in any of the technical solutions of the first aspect, the pump body provided by this invention also possesses all the beneficial effects of the piston assembly as described in any of the technical solutions of the first aspect, which will not be elaborated further here.

[0050] A third aspect of the invention provides a compressor comprising the piston assembly of any of the technical solutions of the first aspect; and / or the pump body of any of the technical solutions of the second aspect.

[0051] The compressor provided by this invention includes a piston assembly as described in any of the first aspects; and / or a pump body as described in any of the second aspects. Since the compressor includes the piston assembly as described in any of the first aspects; and / or the pump body as described in any of the second aspects, the compressor provided by this invention also possesses all the beneficial effects of the piston assembly as described in any of the first aspects and / or the pump body as described in any of the second aspects, which will not be elaborated further here.

[0052] A fourth aspect of the present invention provides a refrigeration device, comprising a piston assembly as described in any of the first aspects; and / or a pump body as described in any of the second aspects; and / or a compressor as described in any of the third aspects.

[0053] The refrigeration device provided by this invention includes a piston assembly as described in any of the first aspects; and / or a pump body as described in any of the second aspects; and / or a compressor as described in any of the third aspects. Since the refrigeration device includes the piston assembly as described in any of the first aspects; and / or a pump body as described in any of the second aspects; and / or a compressor as described in any of the third aspects, the refrigeration device provided by this invention also possesses all the beneficial effects of the piston assembly as described in any of the first aspects and / or the pump body as described in any of the second aspects and / or the compressor as described in any of the third aspects, which will not be elaborated further here.

[0054] Additional aspects and advantages of the invention will become apparent in the following description or may be learned by practice of the invention. Attached Figure Description

[0055] The above and / or additional aspects and advantages of the present invention will become apparent and readily understood from the description of the embodiments taken in conjunction with the following drawings, in which:

[0056] Figure 1 One of the schematic diagrams of a piston assembly according to an embodiment of the present invention is shown;

[0057] Figure 2 A second schematic diagram of the piston assembly according to an embodiment of the present invention is shown;

[0058] Figure 3 One of the schematic diagrams of a piston assembly according to an embodiment of the present invention is shown;

[0059] Figure 4 A second schematic diagram of a partial structure of a piston assembly according to an embodiment of the present invention is shown;

[0060] Figure 5 A third schematic diagram of a partial structure of a piston assembly according to an embodiment of the present invention is shown;

[0061] Figure 6 A fourth schematic diagram of a partial structure of a piston assembly according to an embodiment of the present invention is shown;

[0062] Figure 7 A third schematic diagram of the piston assembly according to an embodiment of the present invention is shown;

[0063] Figure 8 A fourth schematic diagram of the piston assembly according to an embodiment of the present invention is shown;

[0064] Figure 9 Fifth schematic diagram of a partial structure of a piston assembly according to an embodiment of the present invention is shown;

[0065] Figure 10 A partial structural schematic diagram of a piston assembly according to an embodiment of the present invention is shown in Figure 6.

[0066] Figure 11 The seventh schematic diagram shows a partial structural diagram of a piston assembly according to an embodiment of the present invention.

[0067] Among them, 1 is the piston assembly; 11 is the piston body; 111 is the hinge; 112 is the hinge groove; 113 is the opening; 12 is the hinge element; 121 is the cylindrical pin; 1211 is the groove; 122 is the continuous curved surface; 13 is the slider; and 131 is the spring mounting groove. Detailed Implementation

[0068] To better understand the above-mentioned objectives, features, and advantages of the present invention, the present invention will be further described in detail below with reference to the accompanying drawings and specific embodiments. It should be noted that, unless otherwise specified, the embodiments and features described in these embodiments can be combined with each other.

[0069] Many specific details are set forth in the following description in order to provide a full understanding of the invention. However, the invention may also be practiced in other ways different from those described herein, and therefore the scope of protection of the invention is not limited to the specific embodiments disclosed below.

[0070] The following reference Figures 1 to 11 The present invention describes piston assemblies, pump bodies, compressors, and refrigeration devices according to some embodiments thereof.

[0071] According to an embodiment of the first aspect of the present invention, such as Figure 1 , Figure 2 , Figure 3 , Figure 4 , Figure 5 , Figure 6 , Figure 7 , Figure 8 , Figure 9 , Figure 10 and Figure 11 As shown, a first aspect of the present invention provides a piston assembly 1 for a pump body of a compressor. The piston assembly 1 includes a piston body 11, a hinge member 12, and a slide 13. The outer peripheral surface of the piston body 11 has a hinge portion 111. The hinge member 12 is disposed on the hinge portion 111 and cooperates with the hinge portion 111. One end of the slide 13 is disposed on the hinge member 12, and the slide 13 and the piston body 11 are hinged together by the cooperation of the hinge portion 111 and the hinge member 12.

[0072] The piston assembly 1 provided by this invention can be used in the pump body of a compressor. For example, the piston assembly 1 can cooperate with the cylinder of the pump body to compress refrigerant. The piston assembly 1 includes a piston body 11, a hinge member 12, and a slide 13. The outer peripheral surface of the piston assembly 1 has a hinge portion 111. The hinge member 12 can be mounted on the hinge portion 111 and cooperate with the hinge portion 111. One end of the slide 13 is connected to the hinge member 12. Thus, when the piston body 11 swings, the piston body 11 and the slide 13 can be hinged through the hinge member 12. It is understood that, since this application additionally provides a hinge member 12 to hinge with the piston body 11, compared with the solution where the slide 13 directly abuts against the piston body 11, this application increases the contact area with the hinge portion 111 by separately providing a hinge member 12 to hinge with the piston body 11. During the piston body 11's oscillation, this larger contact area effectively reduces the clearance between the hinge 12 and the hinge portion 111, significantly reducing the possibility of refrigerant leaking from the high-pressure side of the cylinder to the low-pressure side through this clearance. Compared to the traditional method of relying on springs to increase the contact force to reduce the clearance, this application directly solves the refrigerant leakage problem caused by the clearance through structural design, improving the compressor's refrigerant compression efficiency and thus enhancing the compressor's overall energy efficiency. Furthermore, since there is no need to increase the spring contact force to prevent refrigerant leakage as in traditional solutions, the friction between the sliding vane 13 and the piston body 11 and cylinder is reduced. In traditional structures, increasing the spring contact force can reduce refrigerant leakage, but it also exacerbates the friction between the sliding vane 13 and other components, increasing power consumption. However, the piston assembly 1 of this application, through optimized connection structure, reduces frictional power consumption while ensuring no refrigerant leakage. This not only improves the compressor's energy utilization efficiency and reduces unnecessary energy loss, but also reduces heat generation during compressor operation, extends the service life of various components, and reduces maintenance costs.

[0073] Furthermore, compared to the design where a connecting structure is provided at one end of the slide plate 13 to hinge it to the piston body 11, this application can reduce the machining difficulty of the slide plate 13 and improve machining efficiency. At the same time, the separate arrangement of the slide plate 13 and the hinge 12 can alleviate stress concentration, reduce the risk of fatigue fracture at the connection, and improve structural reliability.

[0074] In some embodiments, optionally, such as Figures 1 to 11 As shown, the hinge portion 111 is a hinge groove 112 provided on the outer peripheral surface of the piston body 11, and the hinge member 12 is a cylindrical pin 121. The cylindrical pin 121 is disposed in the hinge groove 112, and both the hinge groove 112 and the cylindrical pin 121 are along the thickness direction of the piston body 11 (e.g., Figure 2 (Extends in the direction indicated by H in the middle).

[0075] In these embodiments, the hinge portion 111 can be a hinge groove 112 provided on the outer peripheral surface of the piston body 11. The hinge member 12 can be a cylindrical pin 121, which is installed in the hinge groove 112. Both the hinge groove 112 and the cylindrical pin 121 extend along the thickness direction of the piston body 11. One end of the slide 13 is connected to the cylindrical pin 121, and the hinge between the slide 13 and the piston body 11 is realized through the cooperation between the cylindrical pin 121 and the hinge groove 112. When the piston body 11 swings and compresses the refrigerant in the cylinder, the cylindrical pin 121 rotates in the hinge groove 112, thereby allowing the slide 13 to slide in the groove of the cylinder. By setting the hinge groove 112 to cooperate with the cylindrical pin 121, the outer circumferential surface of the cylindrical pin 121 contacts the inner circumferential surface of the hinge groove 112. Compared with the sliding vane 13 directly abutting against the piston body 11, this increases the contact length and contact area with the piston body 11. This makes it more difficult for refrigerant to leak from the mating gap when the piston body 11 swings, which helps to improve the compressor's energy efficiency. At the same time, due to the increased contact area, a sealing effect can be guaranteed without excessive contact force, which can reduce the friction between the sliding vane 13 and the piston body 11 and cylinder, reduce frictional power consumption, reduce component wear, and extend service life.

[0076] In some embodiments, optionally, such as Figures 1 to 11 As shown, a groove 1211 is provided on the outer circumferential surface of the cylindrical pin 121, and the groove 1211 is along the axial direction of the cylindrical pin 121 (e.g., Figure 2 The piston body 11 extends in the direction indicated by H (the thickness direction of the piston body 11 is the same as the axial direction of the cylindrical pin 121), one end of the slide 13 is located in the groove 1211, and the part of the slide 13 located in the groove 1211 is adapted to the groove 1211.

[0077] In these embodiments, a groove 1211 can be provided on the outer peripheral surface of the cylindrical pin 121, extending along the axial direction of the cylindrical pin 121. This allows one end of the sliding vane 13 to be fitted into the groove 1211, achieving a connection between the sliding vane 13 and the cylindrical pin 121. The groove 1211 on the outer peripheral surface of the cylindrical pin 121 precisely matches one end of the sliding vane 13, greatly enhancing the stability of the connection between the cylindrical pin 121 and the sliding vane 13. During compressor operation, various complex forces and vibrations are generated, and this fitting structure can effectively resist these external forces, reducing the risk of the sliding vane 13 dislodging from the groove 1211 of the cylindrical pin 121. For example, when the compressor operates at high speed, even under the influence of large centrifugal forces and vibrations, the sliding vane 13 can still be firmly held within the groove 1211, working in conjunction with the cylindrical pin 121 to ensure the normal operation of the piston assembly 1 and improve the overall reliability of the compressor.

[0078] In some embodiments, optionally, such as Figures 1 to 11As shown, the portion of the slider 13 located within the groove 1211 has a clearance fit with the groove 1211.

[0079] In these embodiments, the portion of the slide vane 13 located within the groove 1211 is in a clearance fit with the groove 1211. This clearance fit allows the slide vane 13 to better adapt to changes in the movement state of the piston body 11. During compressor operation, the speed, direction, and force of the piston body 11 constantly change. The clearance between the slide vane 13 and the groove 1211 provides the slide vane 13 with a certain amount of buffering and adjustment space, enabling it to more flexibly follow the movement of the piston body 11 under different operating conditions. For example, when the compressor load suddenly changes, the swing amplitude of the piston body 11 may change. The slide vane 13 can adjust its position within the groove 1211 through the clearance, maintaining a good fit with the piston body 11 and the cylinder, ensuring stable compressor operation. The clearance fit also makes assembly more convenient. Compared to a tight fit requiring high-precision installation, a clearance fit allows for installation adjustments within a certain range, reducing assembly difficulty and improving production efficiency. Meanwhile, during equipment maintenance, if it is necessary to replace the sliding plate 13 or the cylindrical pin 121, the clearance fit makes the disassembly process easier, which is convenient for maintenance personnel to operate and further improves the maintainability of the equipment.

[0080] In some embodiments, the depth L2 of the groove 1211 is optionally greater than or equal to 0.2 times the diameter of the cylindrical pin 121 and less than or equal to 0.9 times the diameter of the cylindrical pin 121.

[0081] In these embodiments, the depth of the groove 1211 is greater than or equal to 0.2 times the diameter of the cylindrical pin 121 and less than or equal to 0.9 times the diameter of the cylindrical pin 121. By limiting the depth of the groove 1211, a good balance between the stability and flexibility of the connection between the slide 13 and the cylindrical pin 121 is ensured. When the depth of the groove 1211 is greater than or equal to 0.2 times the diameter of the cylindrical pin 121, the slide 13 has sufficient embedding depth in the groove 1211, making the connection between the two firm during movement and effectively transmitting the movement and force of the piston body 11. Even under the vibration generated by the operation of the compressor and the action of complex external forces, the slide 13 is not easily dislodged from the groove 1211. On the other hand, the depth of the groove 1211 being less than or equal to 0.9 times the diameter of the cylindrical pin 121 ensures the strength of the cylindrical pin 121 itself and avoids the cylindrical pin 121 being easily damaged due to insufficient strength.

[0082] In some embodiments, optionally, such as Figures 1 to 11 As shown, the depth of the slider 13 within the groove 1211 is greater than or equal to 0.3 times the depth of the groove 1211.

[0083] In these embodiments, the depth of the slider 13 within the groove 1211 can be limited to 0.3 times the depth of the groove 1211. The slider 13 achieving a certain embedding depth within the groove 1211 enhances the stability of the connection between the slider 13 and the cylindrical pin 121. During compressor operation, various complex forces are generated, such as centrifugal force, inertial force, and forces caused by changes in refrigerant pressure. Sufficient embedding depth strengthens the bond between the slider 13 and the cylindrical pin 121, effectively resisting these external forces and ensuring that the slider 13 stably follows the movement of the cylindrical pin 121 within the groove 1211. Simultaneously, the sufficient embedding depth of the slider 13 within the groove 1211 makes its position more stable during movement, thereby better controlling the gap between the slider 13 and the cylindrical pin 121 and preventing refrigerant leakage from these areas.

[0084] In some embodiments, optionally, such as Figures 1 to 6 As shown, along the circumferential direction of the cylindrical pin 121 (e.g.) Figure 4 (Z indicates the direction), the cylindrical pin 121 has a continuous curved surface 122, and the angle of the continuous curved surface 122 is greater than or equal to 120°.

[0085] In these embodiments, the cylindrical pin 121 has a continuous curved surface 122 along its circumferential direction, with an angle greater than or equal to 120°. By providing a continuous curved surface 122 with an angle greater than or equal to 120° around the cylindrical pin 121, synergistic optimization of refrigerant leakage at the tip of the slide 13 and frictional power consumption at the hinge is achieved. Specifically, this large-angle continuous curved surface 122 forms a larger and more stable arc surface fit with the hinge groove 112 of the piston body 11. This design, on the one hand, expands the circumferential coverage of the sealing contact band, significantly extending the potential leakage path of the refrigerant, thereby enhancing the stability and continuity of the seal at the structural root and effectively suppressing refrigerant leakage from the hinge gap. On the other hand, the wide contact surface significantly reduces the local contact stress of the hinge pair, which reduces the requirement for the preload of the spring on the back of the slide 13 while maintaining the same sealing effect, thereby directly reducing the sliding frictional power consumption between the slide 13 and the cylinder. Meanwhile, the lower contact stress also significantly reduces the wear of the cylindrical pin 121 and the hinge groove 112 themselves. Therefore, this design works together from the two dimensions of "enhanced sealing" and "reduced load and wear" to synergistically solve the technical contradiction of "leak prevention" and "low friction" that are difficult to achieve simultaneously in traditional solutions, thereby improving the compressor's energy efficiency and enhancing its operational reliability.

[0086] In some embodiments, optionally, such as Figures 1 to 6 As shown, along the axial direction of the cylindrical pin 121, the groove 1211 is U-shaped, and the width of the groove 1211 is B0. In the width direction of the groove 1211 (e.g....) Figure 4In the direction indicated by K, the thickness of the slider 13 is B1, where B0-B1≤50μm.

[0087] In these embodiments, the groove 1211 is U-shaped along the axial direction of the cylindrical pin 121. The width of the U-shaped groove 1211 is B0, and the thickness of the slide 13 is B1 in the width direction of the groove 1211, wherein B0-B1≤50μm. By limiting the difference between the width B0 of the groove 1211 and the thickness B1 of the slide 13 to less than or equal to 50μm, a synergistic effect of maximizing the suppression of refrigerant leakage and reducing frictional losses is achieved while ensuring the flexible swing of the slide 13. Specifically, this micron-level gap greatly limits the flow cross-sectional area of ​​refrigerant leakage between the slide 13 and the sidewall of the groove 1211, effectively blocking the main leakage path from the high-pressure side to the low-pressure side, thereby significantly improving sealing performance and compressor efficiency. On the other hand, the precise fit significantly enhances the radial positioning stability of the slider 13 in the groove 1211, greatly reducing its lateral sway and impact during operation. This not only reduces the power consumption and wear caused by collision and friction between the slider 13 and the groove 1211, but also makes the transmission of driving force more stable and direct, further improving mechanical efficiency and operational reliability, and optimizing the contradictory relationship between leakage and friction in the traditional structure.

[0088] In some embodiments, B0-B1 ≤ 40 μm.

[0089] In some embodiments, B0-B1 ≤ 30 μm.

[0090] In some embodiments, B0-B1 ≤ 20 μm.

[0091] In some embodiments, B0-B1 ≤ 10 μm.

[0092] In some embodiments, optionally, such as Figures 7 to 11 As shown, along the axial direction of the cylindrical pin 121, the groove 1211 is V-shaped, and the bottom width of the groove 1211 is less than the minimum width of one end of the slider 13.

[0093] In these embodiments, along the axial direction of the cylindrical pin 121, the groove 1211 is V-shaped, and the bottom width of the groove 1211 is less than the minimum width of one end of the slide vane 13. By designing the groove 1211 as V-shaped and limiting its bottom width to be less than the minimum width of one end of the slide vane 13, a synergistic optimization of guiding stability and effective sealing is achieved while reducing frictional losses. Specifically, this structure allows the end of the slide vane 13 to form line contact or partial small-area contact with the two inclined surfaces of the V-shaped groove 1211. At the sealing level, this contact form and dimensional fit create a varying wedge-shaped gap between the slide vane 13 and the cylindrical pin 121, significantly extending the refrigerant leakage path and increasing flow resistance, forming a highly efficient "labyrinth" sealing effect, thereby effectively suppressing lateral refrigerant leakage through the hinge and improving the volumetric efficiency of the compressor. At the friction and operation level, the inclined surface of the V-groove provides precise radial positioning and automatic centering guidance for the slide vane 13, greatly limiting its lateral movement and impact during operation, and ensuring smooth movement. Meanwhile, the line contact mode significantly reduces the contact area compared to surface contact, which not only directly reduces sliding friction power consumption but also facilitates the formation and retention of lubricating oil in the contact area, further reducing wear. Furthermore, this structure is more adaptable to machining and assembly errors of parts, improving reliability. Therefore, this design, through a unique "V-shaped guide contact" and "wedge seal" mechanism, synergistically optimizes leak prevention and low-friction performance.

[0094] In some embodiments, optionally, such as Figures 7 to 11 As shown, along the axial direction of the cylindrical pin 121, the groove 1211 is V-shaped, and the included angle of the groove 1211 is a2. The part of the slider 13 located inside the groove 1211 is V-shaped, and the included angle of the slider 13 is a1. Wherein, -60°≤a1-a2≤60°.

[0095] In these embodiments, along the axial direction of the cylindrical pin 121, the groove 1211 is V-shaped with an included angle of a2. The portion of the slide plate 13 located within the groove 1211 is also V-shaped with an included angle of a1, where -60° ≤ a1 - a2 ≤ 60°. By limiting the difference between the included angle a1 of the slide plate and the included angle a2 of the groove to a range of -60° to 60°, synergistic optimization of sealing performance and friction loss is achieved under diverse contact conditions. Specifically, this angular tolerance design allows the V-shaped bevel of the slide plate 13 and the groove 1211 to form various controllable mating states, from surface contact to stable line contact. At the sealing level, regardless of whether the two are tightly fitted or have a small wedge-shaped gap, this fit effectively extends the refrigerant leakage path and forms a local throttling effect, thereby significantly suppressing lateral refrigerant leakage through the hinge and ensuring the volumetric efficiency of the compressor. At the friction and operation level, this design avoids localized stress concentration or point contact caused by severe angle mismatch, resulting in a more reasonable contact pressure distribution and reducing frictional power consumption and wear. Simultaneously, the inherent centering and guiding characteristics of the V-shaped structure are fully utilized, ensuring the smoothness and reliability of the slider 13's movement. Furthermore, this limited angle range enhances adaptability to manufacturing and assembly errors, improving production feasibility.

[0096] In some embodiments, -50° ≤ a1 - a2 ≤ 50°.

[0097] In some embodiments, -40° ≤ a1 - a2 ≤ 40°.

[0098] In some embodiments, -30° ≤ a1 - a2 ≤ 30°.

[0099] In some embodiments, -20° ≤ a1 - a2 ≤ 20°.

[0100] In some embodiments, the hinge groove 112 and the cylindrical pin 121 are optionally clearance-fitted.

[0101] In these embodiments, the hinge groove 112 and the cylindrical pin 121 are in a clearance fit. By setting a clearance fit between the hinge groove 112 and the cylindrical pin 121, synergistic optimization is achieved in multiple aspects, including controlling refrigerant leakage, reducing frictional power consumption, improving operational reliability, and facilitating assembly. Specifically, in terms of sealing, this clearance, together with the large-angle continuous curved surface 122 of the cylindrical pin 121, forms a tortuous leakage channel, significantly increasing the flow resistance of the refrigerant, thereby effectively suppressing leakage without relying on interference compression and ensuring compression efficiency. In terms of friction and operation, the clearance fit avoids rigid contact, greatly reducing friction and wear between the hinge pairs, and directly reducing power consumption. At the same time, the reserved reasonable clearance provides the necessary compensation space for the thermal expansion of parts and manufacturing tolerances, effectively preventing the risk of jamming and enhancing the reliability of the component under high-speed variable operating conditions. In addition, the clearance fit reduces the stringent requirements for assembly precision, making assembly more convenient.

[0102] In some embodiments, optionally, along the thickness direction of the piston body 11, the hinge groove 112 is circular with an opening 113, the width of the opening 113 being greater than or equal to the diameter of the hinge groove 112 minus 0.3 mm and less than or equal to the diameter of the hinge groove 112 minus 0.1 mm.

[0103] In these embodiments, along the thickness direction of the piston body 11, the hinge groove 112 is circular with an opening 113. The width of the opening 113 is greater than or equal to the diameter of the hinge groove 112 minus 0.3 mm, and less than or equal to the diameter of the hinge groove 112 minus 0.1 mm. By setting the width of the opening 113 of the hinge groove 112 within the range of "diameter of the hinge groove 112 minus 0.3 mm" to "diameter of the hinge groove 112 minus 0.1 mm", the constraint stability, sealing reliability, and operational smoothness of the cylindrical pin 121 are optimized while ensuring assembly feasibility. Specifically, this design first ensures that the cylindrical pin 121 can be smoothly and efficiently installed into the hinge groove 112, meeting the assembly process requirements of mass production. More importantly, the precisely controlled width of the opening 113 forms a tight and reasonable radial constraint with the cylindrical pin 121, effectively limiting the radial movement and vibration of the cylindrical pin 121 during operation, thereby stabilizing the relative position of the slide 13 and the piston body 11. This stability directly translates into two core benefits: in terms of sealing, it allows for the maintenance of a uniform and controllable micro-gap between the cylindrical pin 121 and the hinge groove 112, effectively suppressing refrigerant leakage along this path. In terms of mechanical performance, it avoids impacts, noise, and abnormal wear caused by an excessively loose fit, reduces frictional power consumption, and improves the lifespan of the hinge pair and overall operational reliability. Therefore, this refined design of the opening 113 width achieves an optimal balance between ease of assembly, robust constraint, and reliable operation.

[0104] In some embodiments, optionally, along the axial direction of the cylindrical pin 121, the outer diameter of the cylindrical pin 121 is D0, and the inner diameter of the hinge groove 112 is D1, wherein 5μm≤D1-D0≤80μm.

[0105] In these embodiments, along the axial direction of the cylindrical pin 121, the outer diameter of the cylindrical pin 121 is D0, and the inner diameter of the hinge groove 112 is D1, wherein 5μm≤D1-D0≤80μm. By controlling the difference between the inner diameter D1 of the hinge groove 112 and the outer diameter D0 of the cylindrical pin 121 within the range of 5μm to 80μm, synergistic optimization of refrigerant leakage, friction loss, and operational reliability is achieved under extremely small and uniform fitting clearance. Specifically, the design of this clearance range allows the cylindrical pin 121 to rotate smoothly within the hinge groove 112 while being precisely constrained. In terms of sealing, this uniform, micron-level clearance greatly limits the flow cross-sectional area and flow velocity of refrigerant leakage. Combined with the large-angle continuous curved surface 122 of the cylindrical pin 121, a highly efficient labyrinth seal effect is formed, thereby significantly reducing the amount of refrigerant leakage through the hinge pair. In terms of friction and operation, this clearance ensures that the rotating pair is in a good fluid lubrication state, avoiding dry friction or boundary friction between metals, and directly reducing frictional power consumption and wear. At the same time, precise clearance control prevents shocks, vibrations and noise caused by excessively loose fit, improving operational smoothness and reliability.

[0106] In some embodiments, optionally, 5μm≤D1-D0≤80μm.

[0107] In some embodiments, optionally, 15μm≤D1-D0≤70μm.

[0108] In some embodiments, optionally, 25μm≤D1-D0≤60μm.

[0109] In some embodiments, optionally, 35μm≤D1-D0≤50μm.

[0110] In some embodiments, the surface hardness of the hinge 12 may be greater than the surface hardness of the hinge portion 111.

[0111] In these embodiments, by setting the surface hardness of the hinge 12 to be higher than that of the hinge portion 111, a synergistic optimization is achieved in maintaining stable sealing performance, reducing friction and wear, and improving the overall lifespan and operating economy of the components during long-term operation. Specifically, in terms of sealing and fit stability, the harder hinge 12 can better resist plastic deformation and wear under cyclic loads, thereby maintaining the precisely designed initial fit clearance between it and the hinge groove 112 for a long time. This avoids the problem of increased refrigerant leakage caused by the increased clearance due to the rapid wear of the hinge 12, ensuring the long-term and efficient operation of the compressor.

[0112] In some embodiments, the stiffness of the hinge 12 may be greater than HRC20.

[0113] In these embodiments, by limiting the hardness of the hinge 12 to greater than HRC20, it is ensured that the hinge 12 has sufficient basic strength and resistance to deformation, and can reliably transmit working loads.

[0114] In some embodiments, optionally, along the thickness direction of the piston body 11, the height of the hinge 12 is H0, the height of the piston body 11 is H1, and the height of the slide plate 13 is H2; wherein, -30μm≤H1-H0≤30μm; or -30μm≤H0-H2≤30μm; or H2≤H0≤H1.

[0115] In these embodiments, along the thickness direction of the piston body 11, the height of the hinge 12 is H0, the height of the piston body 11 is H1, and the height of the slide 13 is H2; wherein -30μm≤H1-H0≤30μm; or -30μm≤H0-H2≤30μm; or H2≤H0≤H1. By defining the dimensional relationship between the height H0 of the hinge 12, the height H1 of the piston body 11, and the height H2 of the slide 13, synergistic optimization of end-face sealing, friction uniformity, and operational reliability in the axial dimension of the compressor is achieved. Specifically, firstly, the precise equivalence of H1 and H0 (within ±30μm) ensures that after the hinge 12 is installed in the piston body 11, its end face is nearly flush with the end face of the piston body 11. This minimizes or even eliminates the leakage channel that the refrigerant may pass through the gap between the end of the hinge 12 and adjacent components along the axial direction, greatly suppressing axial leakage. Secondly, the precise matching of H0 and H2 (within ±30μm) ensures optimal fit and load-bearing relationship between the slider 13 and the cylindrical pin 121 in the height direction. This avoids abnormal local contact and friction caused by the slider 13 being too high, and also prevents uneven force or poor lubrication caused by the slider 13 being too low, thereby reducing frictional power consumption and wear. Finally, the hierarchical relationship of H2≤H0≤H1 clarifies the reasonable allocation of axial space, prevents motion interference, and ensures smooth and stable movement of the piston assembly 1 within the cylinder.

[0116] In some embodiments, optionally, -20μm≤H1-H0≤20μm.

[0117] In some embodiments, optionally, -10μm≤H1-H0≤10μm.

[0118] In some embodiments, optionally, -20μm≤H0-H2≤20μm.

[0119] In some embodiments, optionally, -10μm≤H0-H2≤10μm.

[0120] In some embodiments, the material of the hinge 12 may optionally include at least one or a combination of the following: carbon steel, stainless steel, and bearing steel.

[0121] In these embodiments, by limiting the material of the hinge 12 to a combination of carbon steel, stainless steel and / or bearing steel, the core requirements of high strength and high wear resistance of the hinge 12 are met, while also taking into account corrosion resistance, processability and economy, thereby providing key material guarantee for the long-term stable, efficient and reliable operation of the piston assembly 1.

[0122] In some embodiments, the carbon steel may optionally be 65Mn.

[0123] In some embodiments, the surface of the hinge 12 may optionally have a hardened layer or coating.

[0124] In these embodiments, by providing a hardened layer or coating on the surface of the hinge 12, the wear resistance of the hinge pair is significantly improved, the coefficient of friction is reduced, and the corrosion resistance is enhanced, thereby achieving the key effect of maintaining a low leakage and low friction state continuously and stably during the long-term operation of the compressor.

[0125] In some embodiments, the hardening layer may optionally include a nitriding layer.

[0126] In some embodiments, the coating may optionally include a DLC (Diamond-Like Carbon) coating.

[0127] In some embodiments, the other end of the slider 13 may optionally have a spring mounting groove 131.

[0128] In these embodiments, by providing a spring mounting groove 131 for the slide 13 at the opposite end to the hinge 12, the advantages of the traditional spring force application method are retained while working in conjunction with the new hinge structure. This achieves a comprehensive effect of efficient sealing, low-friction operation, and stable reliability under a better spring force setting. Specifically, this spring mounting groove 131 allows the spring to provide a basic abutment force to the slide 13 pointing towards the piston center in a traditional and reliable manner.

[0129] A first aspect of the present invention provides a piston assembly for a compressor pump body, the piston assembly comprising a piston (piston body) with a hole (hinged groove) on its edge, a grooved cylindrical pin, and a mass-produced vane.

[0130] A sliding plate (thickness B1) is embedded in a grooved cylindrical pin (groove width B0) with a clearance fit, satisfying B0-B1≤50μm. The cylindrical pin (outer diameter D0) and the piston edge bore (inner diameter D1) also have a clearance fit, with a clearance ≤80μm, i.e., D1-D0≤80μm. Figure 2 As shown, the area enclosed by the circular dashed line represents the mounting position of the elastomer at the tail of the slider. The grooved cylindrical pin can be machined from standard metal parts, and the material can be, but is not limited to, carbon steel, stainless steel, bearing steel, etc., specifically 65Mn, etc. The cylindrical pin undergoes overall surface hardening or coating treatment. Nitriding or DLC coating is acceptable, but not limited to. The groove depth is between 1 / 4 and 4 / 5 of the outer diameter of the cylindrical pin. The outer edge of the cylindrical pin has a continuous curved surface with an angle ≥120°. The height H0 of the cylindrical pin, the piston height H1, and the slider height H2 satisfy the following conditions: -30μm≤H1-H0≤30μm; -30μm≤H0-H2≤30μm; and H2≤H0≤H1. The surface hardness of the cylindrical pin is higher than the hardness of the piston hinge groove. The slider width is between 1.5mm and 5.0mm. The sliding vane has a spring mounting groove at its tail and a tapered bevel at its head with an angle of a1. The cylindrical pin and the piston edge notch are clearance-fitted, with a clearance range of 10μm to 80μm. One end of the sliding vane, with its beveled structure, is embedded in the cylindrical pin notch, while the tail end is supported by an elastic body to ensure the vane does not detach from the piston edge notch during compressor operation. The cylindrical pin has a hardness greater than HRC20. A V-shaped groove with the same taper as the sliding vane is machined through the center, with a bottom width less than the minimum width of the vane head to ensure contact between the two V-shaped sides when the vane and cylindrical pin are engaged. The difference between the cylindrical pin notch angle a2 and the vane head bevel angle a1 is within 60°, i.e., -60°≤a1-a2≤60°. The cylindrical pin notch depth L2 ranges from 0.2×D0≤L2≤0.9×D0, and the depth of the vane extending into the cylindrical pin notch is not less than 0.3×L2. The piston is designed with an open circular hole, the diameter of which is 5μm~80μm larger than the diameter of the cylindrical pin, and the minimum width of the opening is equal to the diameter of the circular hole minus 0.1mm~0.3mm.

[0131] This embodiment proposes an embedded vane-piston structure to address the vane tip leakage problem during compressor operation. The aim is to reduce vane tip leakage and frictional power consumption, thereby improving compressor energy efficiency. The overall structure consists of a piston with a notched outer diameter edge, a cylindrical pin with an angled notch, and a plate-shaped vane. The cylindrical pin is inserted into the open circular hole of the piston. Under the action of spring force and gas, the vane ensures that it does not disengage from the cylindrical pin. When the piston moves under the action of the crankshaft eccentricity, the cylindrical pin can only rotate within the piston's circular hole due to the action of the vane on it. Because of the increased contact length, refrigerant leakage from the high-pressure side to the low-pressure side due to pressure difference can be reduced.

[0132] A second aspect of the invention provides a pump body including the piston assembly 1 in any embodiment of the first aspect.

[0133] The pump body provided by the present invention includes the piston assembly 1 in any embodiment of the first aspect. Since the pump body includes the piston assembly 1 in any embodiment of the first aspect, the pump body provided by the present invention also possesses all the beneficial effects of the piston assembly 1 in any embodiment of the first aspect, which will not be elaborated further here.

[0134] A third aspect of the invention provides a compressor comprising a piston assembly 1 as described in any embodiment of the first aspect; and / or a pump body as described in any embodiment of the second aspect.

[0135] The compressor provided by the present invention includes a piston assembly 1 as described in any embodiment of the first aspect; and / or a pump body as described in any embodiment of the second aspect. Since the compressor includes the piston assembly 1 as described in any embodiment of the first aspect; and / or the pump body as described in any embodiment of the second aspect, the compressor provided by the present invention also possesses all the beneficial effects of the piston assembly 1 as described in any embodiment of the first aspect and / or the pump body as described in any embodiment of the second aspect, which will not be elaborated further here.

[0136] A fourth aspect of the invention provides a refrigeration device comprising a piston assembly 1 as described in any embodiment of the first aspect; and / or a pump body as described in any embodiment of the second aspect; and / or a compressor as described in any embodiment of the third aspect.

[0137] The refrigeration device provided by the present invention includes a piston assembly 1 as described in any embodiment of the first aspect; and / or a pump body as described in any embodiment of the second aspect; and / or a compressor as described in any embodiment of the third aspect. Since the refrigeration device includes the piston assembly 1 as described in any embodiment of the first aspect; and / or the pump body as described in any embodiment of the second aspect; and / or the compressor as described in any embodiment of the third aspect, the refrigeration device provided by the present invention also possesses all the beneficial effects of the piston assembly 1 as described in any embodiment of the first aspect and / or the pump body as described in any embodiment of the second aspect and / or the compressor as described in any embodiment of the third aspect, which will not be elaborated further here.

[0138] In this invention, the term "multiple" refers to two or more unless otherwise explicitly defined. The terms "installed," "connected," "linked," and "fixed," etc., should be interpreted broadly. For example, "connected" can be a fixed connection, a detachable connection, or an integral connection; "linked" can be a direct connection or an indirect connection through an intermediate medium. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0139] In the description of this specification, the terms "one embodiment," "some embodiments," "specific embodiment," etc., refer to a specific feature, structure, material, or characteristic described in connection with that embodiment or example, which is included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0140] The above description is merely a preferred embodiment of the present invention and is not intended to limit the invention. Various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A piston assembly, characterized in that, Pump body for compressor, the piston assembly includes: A piston body, wherein the outer peripheral surface of the piston body has a hinge portion; A hinge member is disposed at the hinge portion and cooperates with the hinge portion; A sliding plate, one end of which is disposed on the hinge member, and the sliding plate and the piston body are hinged together by the cooperation of the hinge part and the hinge member.

2. The piston assembly according to claim 1, characterized in that, The hinge portion is a hinge groove provided on the outer peripheral surface of the piston body, and the hinge element is a cylindrical pin. The cylindrical pin is disposed in the hinge groove, and both the hinge groove and the cylindrical pin extend along the thickness direction of the piston body.

3. The piston assembly according to claim 2, characterized in that, The outer circumferential surface of the cylindrical pin is provided with a groove, which extends along the axial direction of the cylindrical pin. One end of the slider is located in the groove, and the portion of the slider located in the groove is adapted to the groove.

4. The piston assembly according to claim 3, characterized in that, The portion of the slider located within the groove has a clearance fit with the groove.

5. The piston assembly according to claim 3, characterized in that, The depth of the groove is greater than or equal to 0.2 times the diameter of the cylindrical pin and less than or equal to 0.9 times the diameter of the cylindrical pin.

6. The piston assembly according to claim 3, characterized in that, The depth of the slider within the groove is greater than or equal to 0.3 times the depth of the groove.

7. The piston assembly according to claim 3, characterized in that, Along the circumferential direction of the cylindrical pin, the cylindrical pin has a continuous curved surface with an angle greater than or equal to 120°.

8. The piston assembly according to claim 3, characterized in that, Along the axial direction of the cylindrical pin, the groove is U-shaped, the width of the groove is B0, and the thickness of the slider is B1 in the width direction of the groove, wherein B0-B1≤50μm.

9. The piston assembly according to claim 3, characterized in that, Along the axial direction of the cylindrical pin, the groove is V-shaped, and the bottom width of the groove is less than the minimum width of one end of the slider.

10. The piston assembly according to claim 3, characterized in that, Along the axial direction of the cylindrical pin, the groove is V-shaped with an included angle of a2. The portion of the slider located inside the groove is V-shaped with an included angle of a1, wherein -60°≤a1-a2≤60°.

11. The piston assembly according to claim 2, characterized in that, The hinge groove and the cylindrical pin are in clearance fit.

12. The piston assembly according to claim 2, characterized in that, Along the thickness direction of the piston body, the hinge groove is a circular opening with a width greater than or equal to the diameter of the hinge groove minus 0.3 mm and less than or equal to the diameter of the hinge groove minus 0.1 mm.

13. The piston assembly according to claim 2, characterized in that, Along the axial direction of the cylindrical pin, the outer diameter of the cylindrical pin is D0, and the inner diameter of the hinge groove is D1, wherein 5μm≤D1-D0≤80μm.

14. The piston assembly according to any one of claims 1 to 13, characterized in that, The surface hardness of the hinge element is greater than the surface hardness of the hinge portion; and / or The hardness of the hinge is greater than HRC20.

15. The piston assembly according to any one of claims 1 to 13, characterized in that, Along the thickness direction of the piston body, the height of the hinge is H0, the height of the piston body is H1, and the height of the slider is H2; wherein, -30μm≤H1-H0≤30μm; or -30μm≤H0-H2≤30μm; or H2≤H0≤H1.

16. The piston assembly according to any one of claims 1 to 13, characterized in that, The material of the hinge includes at least one of the following or a combination thereof: carbon steel, stainless steel and bearing steel.

17. The piston assembly according to any one of claims 1 to 13, characterized in that, The surface of the hinge has a hardened layer or coating.

18. The piston assembly according to any one of claims 1 to 13, characterized in that, The other end of the slider has a spring mounting groove.

19. A pump body, characterized in that, include: The piston assembly as claimed in any one of claims 1 to 18.

20. A compressor, characterized in that, include: Piston assembly as claimed in any one of claims 1 to 18; and / or The pump body as described in claim 19.

21. A refrigeration device, characterized in that, include: Piston assembly as claimed in any one of claims 1 to 18; and / or The pump body as described in claim 19; and / or The compressor as described in claim 20.

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