Compressor and refrigeration apparatus

Abstract

This application provides a compressor and a refrigeration device, relating to the field of compressor technology. The compressor includes: a cylinder with a compression chamber formed within it, and a vane groove on the cylinder; a piston disposed in the compression chamber; a first hinge portion on the outer circumferential surface of the piston; a vane slidably disposed within the vane groove; a second hinge portion at one end of the vane extending into the compression chamber and hinged to the first hinge portion; the second hinge portion having a second contact surface for contacting the first hinge portion, and the first hinge portion having a first contact surface for contacting the second contact surface; wherein the ratio of the hardness of the first contact surface to the hardness of the second contact surface is in the range of 0.28 to 0.63. This suppresses adhesive wear and controls uneven wear damage, thereby transforming the wear mode between the vane and the piston into uniform, slow, benign wear, thus improving the reliability and lifespan of the compressor and improving its operating conditions.

Description

Technical Field

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

[0002] Currently, to improve the working efficiency of compressors, the sliding vanes are hinged to the piston. However, during long-term operation of the compressor, the hinged structure is prone to accelerated wear, which affects the performance and service life of the compressor.

[0003] In related technologies, by eliminating heat treatment of the original piston and reducing the piston hardness (from 45HRC-55HRC (Rockwell Hardness C Scale) to 15HRC-25HRC), the hardness difference between the piston and the sliding vane grinding surfaces is increased, thus avoiding adhesive wear caused by the hardness of the sliding vane head being close to the hardness of the piston hinge groove, thereby solving the problem of accelerated wear of the hinge structure.

[0004] However, if the piston is too soft, although it is not easy for adhesive wear to occur, the soft piston will wear too quickly, thus affecting the performance and service life of the compressor. Summary of the Invention

[0005] The purpose of this application is to provide a compressor and refrigeration equipment that can solve the problem of excessive piston wear caused by excessively reducing piston hardness to prevent adhesive wear in related technologies.

[0006] In a first aspect, this application provides a compressor, comprising: a cylinder having a compression chamber formed therein and a vane groove provided on the cylinder; a piston disposed in the compression chamber; a first hinge portion provided on the outer peripheral surface of the piston; a vane slidably disposed in the vane groove; a second hinge portion provided at one end of the vane, the second hinge portion extending into the compression chamber and hinged to the first hinge portion; the second hinge portion having a second contact surface for contacting the first hinge portion, and the first hinge portion having a first contact surface for contacting the second contact surface; wherein the ratio of the hardness of the first contact surface to the hardness of the second contact surface is in the range of 0.28 to 0.63.

[0007] In the above embodiments, the ratio of the hardness of the first contact surface to the hardness of the second contact surface is in the range of 0.28 to 0.63. This can suppress adhesive wear and control uneven wear damage, thereby transforming the wear mode between the vane and the piston into uniform and slow benign wear, which can improve the reliability and life of the compressor and improve the compressor's operating conditions.

[0008] In some technical solutions, optionally, the ratio of the circumferential angle of the projection of the portion of the second contact surface and the first contact surface in contact along the piston axis to 360° is greater than or equal to 0.58.

[0009] This ensures a sufficiently large contact area between the second hinge and the first hinge, thereby reducing wear.

[0010] In some technical solutions, an oil-retaining groove is formed between the first contact surface and the second contact surface.

[0011] In the above technical solution, the oil reservoir can create an oil storage space between the first and second contact surfaces to store lubricating oil. When relative movement occurs between the sliding vane and the piston, the lubricating oil in the oil reservoir can be promptly carried between the contact surfaces to form a lubricating oil film; ensuring that the hinged joint between the sliding vane and the piston is always in a good liquid lubrication state, reducing wear.

[0012] In some technical solutions, the second contact surface may optionally be provided with a groove, which forms an oil-receiving groove.

[0013] In the above technical solution, a groove is machined on the second contact surface to form an oil-receiving groove, which facilitates processing.

[0014] In some technical solutions, optionally, the first contact surface is an arc surface, and the inner wall surface of the groove is an arc surface; in the axial direction of the piston, the ratio of the arc length formed by the projection of the inner wall surface of the groove to the arc length formed by the projection of the first contact surface is in the range of 0.04 to 0.13.

[0015] In the above technical solution, the curved surface is more likely to form and maintain a lubricating oil film, thereby reducing wear. In addition, limiting the ratio of the arc length of the groove to the arc length of the first contact surface to the range of 0.04 to 0.13 ensures that the groove has basic and effective oil storage and guiding capacity, thereby improving lubrication, while also ensuring that the groove does not excessively weaken the effective bearing area of ​​the contact surface, avoiding premature failure caused by excessive stress.

[0016] In some technical solutions, the surface of the second hinge portion is provided with a first hardened layer.

[0017] In the above technical solution, a first hardening layer is provided on the surface of the second hinge portion. By strengthening the local surface, the problems of easy fatigue and difficult processing caused by high overall hardness can be avoided.

[0018] In some technical solutions, the first hardened layer can optionally be a nitrided layer, with the surface of the nitrided layer forming the second contact surface; or the first hardened layer can be a diamond-like carbon coating, with the diamond-like carbon coating forming the second contact surface. This improves the surface hardness and wear resistance of the second hinge portion.

[0019] In some technical solutions, optionally, the hardness of the first contact surface is in the range of 400 Hv to 700 Hv; and / or the hardness of the second contact surface is greater than or equal to 1100 Hv; and / or the hardness of the side surface of the vane is greater than 900 Hv. This avoids accelerated wear between the first and second contact surfaces and prevents excessive wear due to overly soft pistons and vanes, thus ensuring long-term stable and efficient operation of the compressor and extending its overall service life. Furthermore, the hardness of the side surface of the vane can be greater than 900 Hv. This makes the side surface of the vane less prone to wear during contact and relative movement with the vane groove, further improving the reliability of the compressor.

[0020] In some technical solutions, the piston may optionally be made of gray cast iron.

[0021] In the above technical solution, gray cast iron has good wear resistance and self-lubricating properties, which can effectively reduce the wear of the piston.

[0022] In some technical solutions, the compressor may optionally include a crankshaft; the crankshaft includes a main shaft, a secondary shaft, and an eccentric portion; the eccentric portion is connected between the main shaft and the secondary shaft; the piston is sleeved on the eccentric portion and can rotate relative to the crankshaft.

[0023] During the operation of the compressor, the piston can rotate eccentrically in the compression chamber of the cylinder under the drive of the crankshaft. As the piston rotates eccentrically, it can drive the sliding vane to move along the sliding vane groove. The working chamber can be divided into the intake chamber and the compression chamber by the sliding vane and the piston. As the piston rotates, the volume of the exhaust chamber and the intake chamber changes, thereby compressing the working medium.

[0024] In some technical solutions, the crankshaft surface may optionally have a second hardened layer. This improves the crankshaft's wear resistance, thereby further enhancing the compressor's reliability.

[0025] In some technical solutions, the second hardened layer can optionally be a manganese phosphate layer. The manganese phosphate layer has high hardness and good friction-reducing properties, effectively resisting friction and thus reducing wear on the crankshaft surface, preventing crankshaft deformation and breakage caused by excessive wear.

[0026] In some technical solutions, the compressor may optionally include: a main bearing, which mates with the main shaft; and a secondary bearing, which mates with the secondary shaft; wherein the piston has a first end face and a second end face located at both ends of the piston axially; the main bearing has a first bearing surface that mates with the first end face, the hardness of the first end face being less than the hardness of the first bearing surface; and the secondary bearing has a second bearing surface that mates with the second end face, the hardness of the second end face being less than the hardness of the second bearing surface.

[0027] In the above technical solution, the piston, as the core component of reciprocating motion, has its first and second end faces at both axial ends in dynamic contact with the first bearing surface of the main bearing and the second bearing surface of the auxiliary bearing, respectively. The hardness of the first end face is less than that of the first bearing surface; the hardness of the second end face is less than that of the second bearing surface. This creates a "soft support, hard" contact mode. The surface with lower hardness can undergo micro-elastic deformation at the moment of contact, which not only makes the contact stress distribution more uniform but also accommodates some abrasive particles, thereby improving adhesive wear and ultimately enhancing the reliability and lifespan of the compressor, thus improving its operating conditions.

[0028] In some technical solutions, the ratio of the hardness of the first end face to the hardness of the first bearing face is in the range of 0.09 to 0.25; and / or, the ratio of the hardness of the second end face to the hardness of the second bearing face is in the range of 0.09 to 0.25.

[0029] In the above technical solution, the piston and bearing can form a relatively ideal wear matching mode during mutual contact and friction. This can effectively avoid excessive wear on the piston caused by the bearing being too hard, and also prevent the piston from wearing too quickly due to being too soft. This ensures the long-term stable and efficient operation of the compressor and extends the overall service life of the compressor.

[0030] In some technical solutions, the main bearing and the secondary bearing have the same hardness.

[0031] In the above technical solution, the main bearing and the auxiliary bearing have the same hardness. In other words, the main bearing and the auxiliary bearing can be made of the same material or materials from the same series, and undergo the same heat treatment process with a uniform hardness index. This reduces manufacturing costs and facilitates assembly.

[0032] In some technical solutions, optionally, the piston is sleeved on the eccentric part by a roller; the length of the slide along the radial direction of the roller is L, and the height of the slide along the axial direction of the roller is H; wherein, 1≤L / H≤1.5.

[0033] In this way, when the vane and piston are hinged, the rigidity and stability of the vane can be guaranteed while ensuring the stability of the connection between the vane and piston. This makes the operation of the piston and vane more stable and smooth, improving the energy efficiency of the compressor, and also reducing wear.

[0034] A second aspect of this application provides a refrigeration device, including the compressor provided by any of the above-described technical solutions. Therefore, the refrigeration device possesses all the beneficial effects of any of the above-described technical solutions, which will not be elaborated further here.

[0035] Additional aspects and advantages of embodiments of this application will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of embodiments of this application. Attached Figure Description

[0036] The above and / or additional aspects and advantages of the embodiments of this application will become apparent and readily understood from the description of the embodiments in conjunction with the following drawings, wherein:

[0037] Figure 1 This is a structural diagram of a compressor in related technologies;

[0038] Figure 2 These are schematic diagrams of the compressor structure according to some embodiments of this application;

[0039] Figure 3 yes Figure 2 Enlarged structural diagram at point A;

[0040] Figure 4 This is one of the structural schematic diagrams of the piston and slide plate in some embodiments of this application;

[0041] Figure 5 This is a second schematic diagram of the piston and slide plate in some embodiments of this application;

[0042] Figure 6 This is a schematic diagram of the crankshaft structure according to some embodiments of this application;

[0043] Figure 7 This is a schematic diagram of the main bearing structure of some embodiments of this application;

[0044] Figure 8 This is a schematic diagram of the structure of the secondary bearing in some embodiments of this application;

[0045] Figure 9 These are schematic diagrams of the roller structure according to some embodiments of this application;

[0046] Figure 10 This is a structural block diagram of a refrigeration device according to some embodiments of this application.

[0047] In the attached figures, the following labels are used:

[0048] 100' sliding plate; 200' piston;

[0049] 100 Compressor; 110 Cylinder; 111 Compression Chamber; 112 Sliding Vane Groove; 120 Piston; 121 First Hinge; 122 First Contact Surface; 123 First End Face; 124 Second End Face; 130 Sliding Vane; 131 Second Hinge; 132 Second Contact Surface; 133 Oil Groove; 134 Recess; 140 Crankshaft; 141 Main Shaft; 142 Sub-Shaft; 143 Eccentric Part; 150 Main Bearing; 151 First Inner Bore Surface; 160 Sub-Bearing; 161 Second Inner Bore Surface; 170 Roller;

[0050] 200 refrigeration equipment. Detailed Implementation

[0051] The technical solutions of the embodiments of this application will be clearly described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, not all embodiments. Examples of embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain this application, and should not be construed as limiting this application. All other embodiments obtained by those skilled in the art based on the embodiments of this application without creative effort are within the scope of protection of this application.

[0052] The terms "first," "second," etc., used in the specification and claims of this application are used to distinguish similar objects and not to describe a specific order or sequence. It should be understood that such use of data can be interchanged where appropriate so that embodiments of this application can be implemented in orders other than those illustrated or described herein, and the objects distinguished by "first," "second," etc., are generally of the same class and the number of objects is not limited; for example, a first object can be one or more. Furthermore, in the specification and claims, "and / or" indicates at least one of the connected objects, and the character " / " generally indicates that the preceding and following objects are in an "or" relationship.

[0053] In the description of this application, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc., indicating the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this application.

[0054] In the description of this application, it should be noted that, unless otherwise expressly specified and limited, the terms "installation," "connection," and "linking" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection between two components. Those skilled in the art can understand the specific meaning of the above terms in this application based on the specific circumstances.

[0055] Currently, in the refrigeration cycle, the compressor is a device that raises low-pressure gas to high-pressure gas. The working principle of the existing rotary compressor is as follows: the crankshaft is directly driven to rotate by the electric motor, and the crankshaft then drives the eccentric compressor piston to rotate in the compression chamber of the cylinder, causing a change in the volume of the compression chamber, thereby compressing the refrigerant gas.

[0056] Reference Figure 1 In the traditional structure, the end of the compressor vane 100' near the piston 200' is usually in contact with the piston. There is no connection between the vane 100' and the piston 200'. This structure is prone to gas leakage and generates a lot of noise. The compressor has low energy efficiency and reliability.

[0057] In related technologies, to improve compressor efficiency, sliding vanes are hinged to the piston. Compared to compressors with traditional structures, this effectively reduces gas leakage during gas compression, improves noise levels, and enhances compressor energy efficiency and reliability.

[0058] However, at the same time, the intake side of the articulated structure also bears greater pressure, which can easily lead to increased local wear of the articulated structure during long-term operation of the compressor, affecting the performance and service life of the compressor.

[0059] To address the aforementioned issues, the piston hardness was reduced (from 45HRC-55HRC to 15HRC-25HRC) by eliminating heat treatment. This increased the hardness difference between the piston and the sliding vane surfaces, preventing adhesive wear caused by the sliding vane head's hardness being too close to the piston's hinge groove hardness, thus resolving the problem of accelerated wear in the hinge structure. However, while excessively low piston hardness reduces the likelihood of adhesive wear, the resulting soft piston wears too quickly, impacting compressor performance and lifespan.

[0060] In view of this, in order to solve the problem of excessive piston wear caused by excessively reducing piston hardness to prevent adhesive wear in related technologies, this application provides a compressor including a cylinder, a piston, and a vane. The cylinder has a compression chamber and a vane groove; the piston is disposed in the compression chamber; a first hinge portion is provided on the outer circumferential surface of the piston; the vane is slidably disposed in the vane groove; one end of the vane has a second hinge portion, which extends into the compression chamber and is hinged to the first hinge portion; the second hinge portion has a second contact surface for contacting the first hinge portion, and the first hinge portion has a second contact surface for contacting the second contact surface; wherein the ratio of the hardness of the first contact surface and the second contact surface is in the range of 0.28 to 0.63. By limiting the ratio of the hardness of the first contact surface and the second contact surface to the range of 0.28 to 0.63, adhesive wear due to excessively similar hardness between the two contact surfaces can be prevented, and piston uneven wear due to excessive hardness difference between the two contact surfaces can also be avoided.

[0061] It is understood that the compressor provided in this application embodiment is used in refrigeration equipment or other industrial equipment that requires compression functions. Refrigeration equipment includes, but is not limited to, air conditioners, refrigerators, and freezers. Industrial equipment includes, but is not limited to, heat pump systems and industrial gas compression equipment.

[0062] The following is combined Figures 2 to 10 The compressor and refrigeration equipment provided in the embodiments of this application will be described in detail.

[0063] Reference Figure 2 , Figure 3 and Figure 4 In some embodiments, this application provides a compressor 100, the structure of which includes a cylinder 110, a piston 120 and a vane 130.

[0064] A compression chamber 111 is formed within a cylinder 110, and a sliding vane groove 112 is provided on the cylinder 110. A piston 120 is disposed in the compression chamber 111; a first hinge portion 121 is provided on the outer peripheral surface of the piston 120. A sliding vane 130 is slidably disposed within the sliding vane groove 112; a second hinge portion 131 is provided at one end of the sliding vane 130, the second hinge portion 131 extends into the compression chamber 111 and is hinged to the first hinge portion 121; the second hinge portion 131 has a second contact surface 132 for contacting the first hinge portion 121, and the first hinge portion 121 has a first contact surface 122 for contacting the second contact surface 132. The ratio of the hardness of the first contact surface 122 to the hardness of the second contact surface 132 is in the range of 0.28 to 0.63.

[0065] Specifically, the piston 120 is disposed in the compression chamber 111 and contacts the inner wall surface of the compression chamber 111. When the compressor 100 is working, the piston 120 rotates eccentrically in the compression chamber 111, and compression is achieved by changing the volume of the compression chamber 111.

[0066] The slide vane 130 slides within the slide vane groove 112, and one end is provided with a second hinge portion 131, which is always hinged to the first hinge portion 121 of the piston 120. As the piston 120 rotates eccentrically, it drives the slide vane 130 to slide along the slide vane groove 112. In this way, the compression chamber 111 can be dynamically divided into a high-pressure zone and a low-pressure zone, thereby preventing gas leakage and improving noise levels.

[0067] The second hinge portion 131 has a second contact surface 132, and the first hinge portion 121 has a first contact surface 122. The first contact surface 122 and the second contact surface 132 are in contact to form a friction pair. When the piston 120 drives the slide plate 130 to move, the first contact surface 122 and the second contact surface 132 come into contact and rub against each other. The ratio of the hardness of the first contact surface 122 to the hardness of the second contact surface 132 is in the range of 0.28 to 0.63. On the one hand, this can prevent adhesive wear between the two contact surfaces due to their hardness being too close; on the other hand, it can also avoid uneven wear of the piston 120 due to a large difference in hardness between the two contact surfaces. Adhesive wear refers to a form of wear in which two contacting solid surfaces adhere to each other when they slide or roll relative to each other due to local high pressure and frictional heat, and then the material is transferred from one surface to the other due to shearing action, even forming wear debris.

[0068] The reasons for this are twofold. On the one hand, when the hardness of the two contact surfaces is too similar, under the combined action of high pressure and high temperature, the micro-protrusions on the contact surfaces are prone to plastic deformation and the formation of metal adhesion points. With relative sliding, the adhesion points will be sheared and broken, causing material to transfer from the softer surface to the harder surface, forming wear debris and aggravating wear. On the other hand, if the hardness difference between the two contact surfaces is too large, the harder surface of the sliding plate 130 will have a grinding effect on the surface of the piston 120, causing the piston 120 to wear unevenly.

[0069] Therefore, in the above embodiments, by setting the ratio of the hardness of the first contact surface 122 to the hardness of the second contact surface 132 within the range of 0.28 to 0.63, both adhesive wear and uneven wear damage can be suppressed. This transforms the wear mode between the sliding vane 130 and the piston 120 into uniform and slow benign wear, thereby improving the reliability and lifespan of the compressor 100 and improving its operating conditions. Compared with the conventional structure, the compressor 100 provided in this embodiment can improve the compressor 100's energy efficiency by 1.5%. Furthermore, under the same base material conditions, the lifespan of the compressor 100 can be increased tenfold.

[0070] In some embodiments, the outer peripheral surface of the piston 120 is provided with a hinge groove. The hinge groove extends through the piston 120 along the axial direction of the piston 120 to form a first hinge portion 121. A second hinge portion 131 is fitted into the hinge groove.

[0071] In some embodiments, the ratio of the circumferential angle β of the projection of the portion of the second contact surface 132 and the first contact surface 122 that contacts in the axial direction of the piston 120 to 360° is greater than or equal to 0.58. It can be understood that the axial direction of the piston 120 can be understood as the axial direction of the cylinder 110 or the axial direction of the roller 170.

[0072] Specifically, this is a top view taken from the axial direction of the compressor 100. In this view, the first hinge portion 121 of the piston 120 appears as a hole, into which the second hinge portion 131 of the slide 130 is embedded and hinged. At this point, the projection of the actual contact area between the second contact surface 132 and the first contact surface 122 is an arc, with the ratio of its circumferential angle to 360° being greater than or equal to 0.58. This ensures a sufficiently large contact area between the second hinge portion 131 and the first hinge portion 121, thereby reducing wear.

[0073] In some embodiments, an oil groove 133 is formed between the first contact surface 122 and the second contact surface 132.

[0074] The oil reservoir 133 creates an oil storage space between the first contact surface 122 and the second contact surface 132 for storing lubricating oil. When relative movement occurs between the sliding vane 130 and the piston 120, the lubricating oil in the oil reservoir 133 can be promptly carried between the contact surfaces to form a lubricating oil film, ensuring that the hinged joint between the sliding vane 130 and the piston 120 is always in a good state of liquid lubrication and reducing wear.

[0075] In some embodiments, the second contact surface 132 is provided with a groove 134, which forms an oil-receiving groove 133. By machining the groove 134 on the second contact surface 132 to form the oil-receiving groove 133, it is easier to process.

[0076] It is understandable that the second contact surface 132 and the first contact surface 122 can also be clearance-fitted to form an oil groove 133.

[0077] In practical applications, the first contact surface 122 can be an arc surface. It is understood that the relative movement between the piston 120 and the sliding vane 130 is oscillation rather than simple sliding, and an arc surface can better accommodate this oscillation. Furthermore, arc surface contact can create a more uniform stress distribution, avoiding stress concentration. In addition, an arc surface makes it easier to form and maintain a lubricating oil film, thereby reducing wear.

[0078] In the above embodiment, the inner wall surface of the groove 134 is an arc surface. In the axial direction of the piston 120, the ratio of the arc length formed by the projection of the inner wall surface of the groove 134 to the arc length formed by the projection of the first contact surface 122 is in the range of 0.04 to 0.13.

[0079] The curved surface has a continuous and smooth curve shape, which guides the lubricating oil to flow more smoothly compared to a flat surface or a sharp corner. When the slider 130 and piston 120 move relative to each other, the lubricating oil can be evenly spread on the contact surface along the curved surface of the groove 134, forming a lubricating oil film of uniform thickness and stability. It is understood that if the groove 134 is too small, the oil storage and supply capacity will be insufficient; if the groove 134 is too large, the contact area between the second contact surface 132 and the first contact surface 122 will be reduced, which will lead to an increase in contact stress. Therefore, in this embodiment, the ratio of the arc length of the groove 134 to the arc length of the first contact surface 122 is limited to the range of 0.04 to 0.13. This ensures that the groove 134 has a basic and effective oil storage and guiding capacity, thereby improving lubrication, while also ensuring that the groove 134 does not excessively weaken the effective bearing area of ​​the contact surface, avoiding premature failure due to excessive stress.

[0080] In some embodiments, the surface of the second hinge portion 131 is provided with a first hardening layer. By providing a first hardening layer on the surface of the second hinge portion 131, the problems of easy fatigue and difficult processing caused by high overall hardness can be avoided by strengthening the local surface.

[0081] In practical applications, the first hardened layer is a nitrided layer, and the surface of the nitrided layer forms the second contact surface. Specifically, the surface of the second hinge portion 131 is nitrided, and a bright white layer is retained after the treatment. This bright white layer is a compound layer formed on the surface after nitriding, which has extremely high hardness and wear resistance. Therefore, the surface hardness and wear resistance of the second hinge portion 131 can be improved.

[0082] Understandably, the first hardened layer is a diamond-like carbon (DLC) coating, which forms the second contact surface 132.

[0083] Specifically, the surface of the second hinge portion 131 is treated with DLC to form an extremely thin film layer. DLC has extremely high hardness and an extremely low coefficient of friction. Therefore, the surface hardness and wear resistance of the second hinge portion 131 can be improved.

[0084] It is understandable that a material with higher hardness can be used to make the slide 130, and a material with relatively lower hardness can be used to make the piston 120.

[0085] In some embodiments, the hardness of the first contact surface 122 can be in the range of 400 Hv (Vickers Hardness) to 700 Hv. The hardness of the second contact surface 132 can be greater than or equal to 1100 Hv. This avoids accelerated wear between the first contact surface 122 and the second contact surface 132, and also prevents excessive wear of the piston 120 and the sliding vane 130 due to excessive softness, thereby ensuring the long-term stable and efficient operation of the compressor 100 and extending its overall service life. It is understood that the upper limit of the hardness of the second contact surface 132 can be determined based on the hardness of the first contact surface 122 and the range of their ratio.

[0086] In practical applications, the hardness of the side surface of the vane 130 can be greater than 900 Hv. This reduces wear on the side surface of the vane 130 during contact and relative movement with the vane groove 112, thereby further improving the reliability of the compressor 100. It is understandable that the hardness of the side surface of the vane 130 can be less than or equal to the hardness of the second contact surface 132, which can effectively reduce costs.

[0087] Piston 120 can be manufactured using gray cast iron. Firstly, gray cast iron is a relatively common and inexpensive raw material, saving significant costs compared to materials like alloy steel. Furthermore, its production process is mature, facilitating large-scale production and further reducing unit product costs. Secondly, gray cast iron possesses excellent wear resistance and self-lubricating properties, effectively reducing the wear on piston 120.

[0088] Reference Figure 2 and Figure 6 In some embodiments, the compressor 100 further includes a crankshaft 140. The crankshaft 140 includes a main shaft 141, a secondary shaft 142, and an eccentric portion 143. The eccentric portion 143 is connected between the main shaft 141 and the secondary shaft 142. A piston 120 is fitted onto the eccentric portion 143 and is rotatable relative to the crankshaft 140.

[0089] In this way, during the operation of the compressor 100, the piston 120 can rotate eccentrically in the compression chamber 111 of the cylinder 110 under the drive of the crankshaft 140. As the piston 120 rotates eccentrically, it can drive the slide vane 130 to move along the slide vane groove 112. The working chamber can be divided into the intake chamber and the compression chamber 111 by the slide vane 130 and the piston 120. As the piston 120 rotates, the volume of the exhaust chamber and the intake chamber changes, thereby compressing the working medium.

[0090] In some embodiments, the surface of the crankshaft 140 is provided with a second hardened layer. In other words, the surfaces of the main shaft 141, the auxiliary shaft 142, and the eccentric portion 143 are all provided with a second hardened layer. This improves the wear resistance of the crankshaft 140, thereby further improving the reliability of the compressor 100.

[0091] The second hardened layer can be a manganese phosphate layer. The manganese phosphate layer has high hardness and good friction-reducing properties, which can effectively resist friction, thereby reducing wear on the surface of crankshaft 140 and preventing problems such as deformation and breakage of crankshaft 140 caused by excessive wear.

[0092] Understandably, the second hardened layer can also be a nitrided layer.

[0093] Reference Figure 2 , Figure 6 , Figure 7 , Figure 8 and Figure 9 In some embodiments, the main shaft 141 engages with the first inner surface 151 of the main bearing 150 of the compressor 100; the auxiliary shaft 142 engages with the second inner surface 161 of the auxiliary bearing 160 of the compressor 100; thereby supporting the crankshaft 140. By supporting the crankshaft 140 with bearings, the stability of the compressor 100 during operation can be improved.

[0094] The piston 120 has a first end face 123 and a second end face 124 located at both axial ends of the piston 120; the main bearing 150 has a first bearing surface that corresponds to and cooperates with the first end face 123, and the hardness of the first end face 123 is less than the hardness of the first bearing surface; the auxiliary bearing 160 has a second bearing surface that corresponds to and cooperates with the second end face 124, and the hardness of the second end face 124 is less than the hardness of the second bearing surface.

[0095] During the operation of the compressor 100, the first end face 123 and the end face of the main bearing 150 come into contact and rub against each other, and the second end face 124 and the end face of the auxiliary bearing 160 come into contact and rub against each other. Therefore, in this embodiment, the hardness of the first end face 123 is made less than the hardness of the first bearing surface, and the hardness of the second end face 124 is made less than the hardness of the second bearing surface. In this way, a "soft support hard" contact mode is formed. The surface with lower hardness can undergo micro-elastic deformation at the moment of contact, which can not only make the contact stress distribution more uniform, but also accommodate some abrasive particles, thereby improving adhesive wear, and thus improving the reliability and life of the compressor and improving the compressor's operating conditions.

[0096] In some embodiments, the ratio of the hardness of the first end face 123 to the hardness of the first bearing surface is in the range of 0.09 to 0.25.

[0097] The hardness ratio between the first end face 123 and the first bearing surface of the main bearing 150 can be within the range of 0.09 to 0.25. By increasing the hardness difference between the first end face 123 and the first bearing surface of the main bearing 150, the adhesive wear between the piston 120 and the main bearing 150 can be improved. Within this hardness ratio range, the piston 120 and the bearing can form a more ideal wear matching mode during mutual contact and friction. This effectively avoids excessive wear on the piston 120 due to excessively hard bearings, and also prevents excessive wear on the piston 120 due to excessively soft bearings. This ensures the long-term stable and efficient operation of the compressor 100 and extends the overall service life of the compressor 100. It is understood that the hardness ratio between the second end face 124 and the second bearing surface of the auxiliary bearing 160 can also be within the range of 0.09 to 0.25.

[0098] It is understandable that the main bearing 150 and the auxiliary bearing 160 have the same hardness. In other words, the main bearing 150 and the auxiliary bearing 160 can be made of the same material or materials from the same series, and undergo the same heat treatment process with a uniform hardness index. This reduces manufacturing costs and facilitates assembly.

[0099] Reference Figure 5 and Figure 6 In some embodiments, the piston 120 is sleeved on the eccentric portion 143 via a roller 170. The length of the slide 130 along the radial direction of the roller 170 is L, and the height of the slide 130 along the axial direction of the roller 170 is H. Wherein, 1≤L / H≤1.5.

[0100] It is understood that the radial length L of the slide vane 130 along the piston 120 is the length of the slide vane 130, and the axial height H of the slide vane 130 along the piston 120 is the thickness of the slide vane 130. The sliding of the slide vane 130 within the groove generates friction. Its lateral frictional resistance is directly proportional to the contact area between the side of the slide vane 130 and the groove wall; in other words, the greater the height, the larger the lateral contact area, and the greater the frictional resistance. Therefore, in the above embodiment, the ratio of the length to the height of the slide vane 130 is limited to the range of 1 to 1.5. In this way, when the slide vane 130 is hinged to the piston 120, the rigidity and stability of the slide vane 130 are ensured while maintaining a stable connection between the two, thus making the operation of the piston 120 and the slide vane 130 more stable and smooth, improving the energy efficiency of the compressor 100; and reducing wear.

[0101] Reference Figure 10 In some embodiments, this application may also provide a refrigeration device 200, including the compressor 100 provided in any of the above embodiments. Thus, the refrigeration device 200 possesses all the beneficial effects of any of the above embodiments, which will not be elaborated further here.

[0102] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "illustrative embodiment," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of this application. 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.

[0103] Although embodiments of this application have been shown and described, those skilled in the art will understand that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of this application, the scope of which is defined by the claims and their equivalents.

Claims

1. A compressor, characterized in that, include: A cylinder, wherein a compression chamber is formed inside the cylinder, and a sliding vane groove is provided on the cylinder; A piston is disposed in the compression chamber; the outer peripheral surface of the piston is provided with a first hinge portion; A slider is slidably disposed in the slider groove; one end of the slider is provided with a second hinge portion, the second hinge portion extends into the compression cavity and is hinged with the first hinge portion; the second hinge portion has a second contact surface for contacting the first hinge portion, and the first hinge portion has a first contact surface for contacting the second contact surface; The ratio of the hardness of the first contact surface to the hardness of the second contact surface is in the range of 0.28 to 0.

63.

2. The compressor according to claim 1, characterized in that, Along the axial direction of the piston, the ratio of the circumferential angle of the projection of the portion of the second contact surface that contacts the first contact surface to 360° is greater than or equal to 0.

58.

3. The compressor according to claim 1, characterized in that, An oil groove is formed between the first contact surface and the second contact surface.

4. The compressor according to claim 3, characterized in that, The second contact surface is provided with a groove, which forms the oil-containing groove.

5. The compressor according to claim 4, characterized in that, The first contact surface is an arc surface; the inner wall surface of the groove is an arc surface; in the axial direction of the piston, the ratio of the arc length formed by the projection of the inner wall surface of the groove to the arc length formed by the projection of the first contact surface is in the range of 0.04 to 0.

13.

6. The compressor according to claim 2, characterized in that, The surface of the second hinge portion is provided with a first hardening layer.

7. The compressor according to claim 6, characterized in that, The first hardened layer is a nitrided layer, and the surface of the nitrided layer forms the second contact surface; or The first hardened layer is a diamond-like carbon coating, which forms the second contact surface.

8. The compressor according to claim 1, characterized in that, The piston has a hardness in the range of 400 Hv to 700 Hv; and / or The hardness of the second contact surface is greater than or equal to 1100 Hv; and / or The hardness of the side of the slider is greater than 900 Hv.

9. The compressor according to claim 1, characterized in that, The piston is made of gray cast iron.

10. The compressor according to any one of claims 1 to 9, characterized in that, The compressor also includes a crankshaft; The crankshaft includes a main shaft, a secondary shaft, and an eccentric portion; the eccentric portion connects the main shaft and the secondary shaft. The piston is fitted onto the eccentric portion and can rotate relative to the crankshaft.

11. The compressor according to claim 10, characterized in that, The surface of the crankshaft is provided with a second hardened layer.

12. The compressor according to claim 11, characterized in that, The second hardened layer is a manganese phosphate layer.

13. The compressor according to claim 10, characterized in that, The compressor also includes: Main bearing, which mates with the main shaft; A secondary bearing, which mates with the secondary shaft; The piston has a first end face and a second end face located at both ends of the piston's axial direction; the main bearing has a first bearing surface that mates with the first end face, and the hardness of the first end face is less than the hardness of the first bearing surface; the auxiliary bearing has a second bearing surface that mates with the second end face, and the hardness of the second end face is less than the hardness of the second bearing surface.

14. The compressor according to claim 13, characterized in that, The ratio of the hardness of the first end face to the hardness of the first bearing surface is in the range of 0.09 to 0.25; and / or The ratio of the hardness of the second end face to the hardness of the second bearing surface is in the range of 0.09 to 0.

25.

15. The compressor according to claim 13, characterized in that, The main bearing and the secondary bearing have the same hardness.

16. The compressor according to claim 10, characterized in that, The piston is mounted on the eccentric part via a roller; the length of the slide along the radial direction of the roller is L, and the height of the slide along the axial direction of the roller is H; wherein, 1≤L / H≤1.

5.

17. A refrigeration device, characterized in that, Includes the compressor as described in any one of claims 1 to 16.

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