Compressor piston, reciprocating compressor and refrigeration equipment

Abstract

The utility model discloses a compressor piston, a reciprocating compressor and refrigeration equipment, the compressor piston comprises a piston body, the piston body is internally provided with a mounting groove for a connecting rod to penetrate, piston pin holes are respectively arranged on two symmetrical sides of the piston body along the radial direction of the piston body, and the piston pin holes on the two sides are respectively communicated with the mounting groove; the outer wall of the piston body is provided with two weight reduction grooves and an oil groove, the two weight reduction grooves are symmetrically formed in the two sides of the piston body, the weight reduction grooves in the two sides communicate with the piston pin holes in the two sides, and the weight reduction grooves and the piston body are arranged at intervals along the two axial end faces of the piston body. The oil grooves are formed in the circumferential direction of the piston body and communicate with the weight reducing grooves in the two sides, and a plurality of oil holes communicating with the mounting groove are formed in the bottom walls of the oil grooves and are formed in the circumferential direction of the piston body at intervals. The mass of the piston body is light, inertia excitation generated during reciprocating motion can be effectively reduced, friction between the piston body and the inner wall of a cylinder hole can be reduced, and noise is reduced.

Description

Technical Field

[0001] The utility model relates to the technical field of compressors, in particular to a compressor piston, a reciprocating compressor and a refrigeration device. Background Art

[0002] The compressor is the core power source of the refrigerator. The refrigerator compressor is a typical reciprocating structure. The reciprocating motion of the piston and the connecting rod forms an irremovable reciprocating inertial excitation. This excitation acts on the compressor and is the main source of vibration and noise. In order to reduce the reciprocating inertial excitation, the relevant technology has made a lightweight design for the piston. Although it reduces the mass, it ignores its structural strength and the wear between the piston and the cylinder, making the application of lightweight pistons difficult. Utility Model Content

[0003] The utility model aims to solve at least one of the technical problems existing in the prior art. To this end, the utility model proposes a compressor piston, the piston body of which is light in weight, which can not only effectively reduce the inertial excitation generated by the reciprocating motion of the piston body, but also reduce the friction between the outer peripheral wall of the piston body and the inner wall of the cylinder hole, thereby reducing noise.

[0004] The utility model also provides a reciprocating compressor and a refrigeration device comprising the compressor piston.

[0005] The compressor piston according to the first embodiment of the utility model comprises:

[0006] A piston body, wherein a mounting groove for inserting a connecting rod is provided in the piston body, and piston pin holes are respectively provided on two symmetrical sides of the piston body along the radial direction of the piston body, and the piston pin holes on both sides are respectively connected to the mounting groove;

[0007] The outer wall of the piston body is provided with a weight-reducing groove and an oil groove, wherein two weight-reducing grooves are provided and are symmetrically arranged on both sides of the piston body, the weight-reducing grooves on both sides are communicated with the piston pin holes on both sides, and the weight-reducing grooves are spaced apart from the two end surfaces of the piston body along the axial direction of the piston body; the oil groove is arranged along the circumferential direction of the piston body and is communicated with the weight-reducing grooves on both sides, and the bottom wall of the oil groove is provided with a plurality of oil holes communicated with the mounting groove, and the plurality of oil holes are spaced apart along the circumferential direction of the piston body.

[0008] The compressor piston according to the embodiment of the utility model has at least the following beneficial effects:

[0009] A mounting groove is provided in the piston body, and the interior of the piston body is hollow, which is conducive to reducing weight. After the end of the connecting rod is inserted into the mounting groove, it is directly fixed in the piston body through a pin shaft, which can ensure the connection strength between the piston body and the connecting rod; by arranging weight-reducing grooves on both sides of the symmetrical piston body, the overall weight can be further reduced, and the inertial excitation of the piston body during the reciprocating motion is reduced, which is conducive to reducing the vibration and noise generated during the reciprocating motion of the oil plug; by arranging an oil groove connected to the weight-reducing groove on the piston body, and arranging a plurality of oil holes on the bottom wall of the oil groove, during the reciprocating motion of the piston body, the lubricating oil can pass through the oil holes and flow along the oil groove and the weight-reducing groove to the contact portion between the piston body and the inner wall of the cylinder bore, which is conducive to reducing the friction between the outer peripheral wall of the piston body and the inner wall of the cylinder bore, thereby reducing the wear between the piston body and the inner wall of the cylinder bore.

[0010] According to the compressor piston of the first aspect of the present invention, the weight reducing groove is arranged along the tangential direction of the outer circumference of the piston body, and along the radial direction of the piston body, at least part of the piston pin hole is formed on the bottom wall of the weight reducing groove and is located in the middle position of the weight reducing groove along the tangential direction.

[0011] According to the compressor piston of the first aspect of the utility model, the maximum depth of the weight-reducing groove along the radial direction of the piston body ranges from 8 mm to 10 mm, and the maximum width of the weight-reducing groove along the axial direction of the piston body ranges from 16 mm to 18 mm.

[0012] According to the compressor piston of the first aspect of the present utility model, the oil groove is formed at the middle position of the piston body along its axial direction, and the maximum width of the oil groove along the axial direction of the piston body ranges from 2 mm to 6 mm.

[0013] According to the compressor piston of the embodiment of the first aspect of the utility model, the number of the oil holes ranges from 4 to 8, and the diameter of the oil holes ranges from 1 mm to 4 mm.

[0014] According to the compressor piston of the first embodiment of the utility model, along the axial direction of the piston body, the height range of the piston body is 18mm to 20mm, and the height range of the mounting groove is 16mm to 18mm.

[0015] According to the compressor piston of the first aspect of the utility model embodiment, the piston pin hole is used to insert the pin shaft, and along the axial direction of the piston body, the end face where the opening of the mounting groove is located is the first end face, and the first end face is provided with a pin hole for the pin to pass through to lock the pin shaft, and the pin hole passes through the first end face and the inner wall of the piston pin hole. Along the axial direction perpendicular to the piston pin hole, two symmetrically arranged corners are respectively provided at both ends of the mounting groove, and the width between the two symmetrical corners is greater than the width of the middle position of the mounting groove.

[0016] According to the compressor piston of the first aspect of the present invention, a convex edge is provided on the circumference of the first end face, the convex edge is arranged along the circumference of the piston body, and the height of the convex edge protruding from the first end face ranges from 2mm to 6mm.

[0017] A reciprocating compressor according to a second embodiment of the utility model comprises:

[0018] A crankcase having a shaft hole and a cylinder hole;

[0019] A crankshaft, comprising a main shaft and a secondary shaft eccentrically arranged with the main shaft, wherein the main shaft is rotatably connected to the shaft hole;

[0020] A connecting rod, one end of which is connected to the secondary shaft;

[0021] The compressor piston provided by the embodiment of the first aspect of the utility model comprises a piston body disposed in the cylinder hole, and the piston body is connected to the other end of the connecting rod.

[0022] The reciprocating compressor according to the embodiment of the utility model has at least the following beneficial effects:

[0023] By arranging a weight reduction groove and an oil groove on the compressor piston and arranging an oil hole on the bottom wall of the oil groove, not only the inertial excitation generated by the reciprocating motion of the piston body is effectively reduced, but also the friction between the outer periphery of the piston body and the inner wall of the cylinder hole can be reduced, thereby reducing the vibration and noise generated during the operation of the reciprocating compressor and increasing the service life of the reciprocating compressor.

[0024] According to the refrigeration device of the embodiment of the third aspect of the utility model, the refrigeration device comprises the reciprocating compressor provided by the embodiment of the second aspect of the utility model, and the refrigeration device has all the beneficial effects of the reciprocating compressor.

[0025] Additional aspects and advantages of the present invention will be given in part in the following description, and in part will become apparent from the following description, or will be learned through the practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0026] The present invention is further described below with reference to the accompanying drawings and embodiments, wherein:

[0027] Figure 1 This is a schematic structural diagram of a compressor piston according to an embodiment of the utility model;

[0028] Figure 2 A schematic structural diagram of a compressor piston from another angle according to an embodiment of the utility model;

[0029] Figure 3 A cross-sectional view of a compressor piston according to an embodiment of the utility model;

[0030] Figure 4 This is a schematic structural diagram of a first end surface of a compressor piston according to an embodiment of the utility model;

[0031] Figure 5 A cross-sectional view of a compressor piston from another angle according to an embodiment of the utility model;

[0032] Figure 6 The figure is an exploded schematic diagram of a compression mechanism of a reciprocating compressor according to an embodiment of the utility model.

[0033] Figure Number:

[0034] Compressor piston 100; piston body 110; ring 111; mounting groove 120; piston pin hole 130; weight reduction groove 140; oil groove 150; oil hole 160; first end surface 170; pin hole 180; corner 190; convex edge 200; concave corner 210;

[0035] Compression mechanism 300 ; crankcase 310 ; shaft hole 311 ; cylinder hole 312 ; crankshaft 320 ; main shaft 321 ; secondary shaft 322 ; connecting rod 330 ; pin 340 ; latch 350 ; bearing 360 . DETAILED DESCRIPTION

[0036] The embodiments of the present invention are described in detail below, and examples of the embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and cannot be understood as limiting the present invention.

[0037] In the description of the present invention, it should be understood that descriptions involving orientation, such as up, down, left, right, etc., indicating orientations or positional relationships, are based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present invention.

[0038] In the description of the utility model, if there is a description of first and second, it is only for the purpose of distinguishing the technical features, and cannot be understood as indicating or implying the relative importance or implicitly indicating the number of the indicated technical features or implicitly indicating the order of the indicated technical features.

[0039] In the description of the present invention, unless otherwise clearly defined, terms such as setting, installing, connecting, etc. should be understood in a broad sense, and technicians in the relevant technical field can reasonably determine the specific meanings of the above terms in the present invention based on the specific content of the technical solution.

[0040] The embodiment of the present utility model provides a compressor piston 100, which is applied to a reciprocating compressor and a refrigeration device. The specific structure and function of the compressor piston 100 provided by the embodiment of the present utility model will be further described below in combination with text and drawings.

[0041] Reference Figures 1 to 3 As shown, in some embodiments, the compressor piston 100 includes: a piston body 110, the piston body 110 is generally cylindrical, and one end thereof is concave to form a mounting groove 120 for inserting the connecting rod 330, and the interior of the piston body 110 forms a hollow structure, which is conducive to reducing weight. Along the radial direction of the piston body 110, piston pin holes 130 are respectively provided on both sides of the piston body 110 symmetrically, and the piston pin holes 130 on both sides extend toward the center of the piston body 110 and communicate with the mounting groove 120. When installing the connecting rod 330, after the end of the connecting rod 330 is inserted into the mounting groove 120, the pin shaft 340 is inserted from the piston pin holes 130 on either side of the piston body 110, so as to directly connect the connecting rod 330 with the piston body 110, which can ensure the connection strength between the piston body 110 and the connecting rod 330.

[0042] It is understandable that the piston body 110 will generate more heat during the reciprocating motion. By providing the mounting groove 120 inside the piston body 110, a hollow structure is formed inside the piston body 110, and part of the lubricating oil can enter the mounting groove 120 and contact the inner wall of the mounting groove 120, which is beneficial to increase the contact area between the piston body 110 and the lubricating oil, and is beneficial to improve the heat dissipation efficiency between the piston body 110 and the lubricating oil, and reduce the friction loss caused by the thermal expansion of the piston body 110, thereby extending the service life of the reciprocating compressor.

[0043] It can be understood that the inertial excitation during the reciprocating motion of the piston body 110 can be understood as the inertial force of the reciprocating motion of the piston body 110 in the cylinder hole 312, and can be specifically calculated according to the formula: F=-Ma (F is the inertial force received by the piston body 110 during the reciprocating motion, in units of N; M is the mass of the piston body 110, in units of kg; a represents the acceleration of the piston body 110 during the reciprocating motion, in units of m / s).

[0044] Reference Figures 1 to 3As shown, in some embodiments, the outer wall of the piston body 110 is cut to form a weight-reducing groove 140. Two weight-reducing grooves 140 are provided and symmetrically arranged on both sides of the piston body 110, which is conducive to reducing the weight of the piston body 110. According to the calculation formula F=-Ma, when the acceleration a remains unchanged, the weight of the piston body 110 is reduced, and the inertial force of the piston body 110 during the reciprocating motion is also reduced accordingly, that is, the inertial excitation of the piston body 110 during the reciprocating motion is reduced. The weight-reducing grooves 140 on both sides of the piston body 110 are connected to the piston pin holes 130 on both sides, and part of the lubricating oil in the installation groove 120 can flow through the piston pin holes 130 to the weight-reducing grooves 140, ensuring that the lubricating oil can be distributed between the piston body 110 and the pin shaft 340, which is conducive to improving the lubrication effect.

[0045] Reference Figure 2 and Figure 3 As shown, in some embodiments, along the axial direction of the piston body 110, the two ends of the weight reduction groove 140 are spaced from the two end surfaces of the piston body 110, and ring portions 111 are formed at the two ends of the piston body 110 respectively. The ring portions 111 at the axial ends of the piston body 110 fit with the inner wall of the cylinder bore 312 of the crankcase 310, ensuring good sealing between the piston body 110 and the inner wall of the cylinder bore 312, and greatly reducing the possibility of leakage due to poor sealing during the compression process.

[0046] Reference Figures 1 to 3 As shown, in some embodiments, the outer wall of the piston body 110 is concave to form an oil groove 150, which extends along the circumference of the piston body 110 and is connected to the weight reduction grooves 140 on both sides of the piston body 110. The bottom wall of the oil groove 150 is provided with a plurality of oil holes 160 connected to the mounting groove 120, and the plurality of oil holes 160 are arranged at intervals along the circumference of the piston body 110. During the reciprocating motion of the piston body 110, the lubricating oil can pass through the oil holes 160 and flow along the oil groove 150 and the weight reduction groove 140 to the contact portion between the piston body 110 and the inner wall of the cylinder bore 312, which is beneficial to reduce the friction between the outer circumferential wall of the piston body 110 and the inner wall of the cylinder bore 312, thereby reducing the wear between the piston body 110 and the inner wall of the cylinder bore 312.

[0047] It can be understood that the oil groove 150 is located in the axial middle part of the piston body 110, which is conducive to ensuring the supply of lubricating oil to the axial ends of the piston body 110, thereby reducing the friction between the piston body 110 and the inner wall of the cylinder hole 312, and reducing the noise and vibration during the operation of the reciprocating compressor.

[0048] It should be noted that when the weight-reducing groove 140, the oil groove 150 and the oil hole 160 are processed on the piston body 110, part of the material of the piston body 110 is cut, which is beneficial to reducing the overall weight of the piston; and because the weight-reducing groove 140 and the oil groove 150 are provided on the piston body 110, the total contact area between the piston body 110 and the inner wall of the cylinder bore 312 is reduced, which is beneficial to reducing the friction between the outer periphery of the piston body 110 and the inner wall of the cylinder bore 312.

[0049] Reference Figure 2 and Figure 3 As shown, in some embodiments, the weight-reducing groove 140 is arranged along the tangent direction of the outer periphery of the piston body 110, and the weight-reducing groove 140 can be directly processed on the outer periphery of the piston body 110 by cutting during the processing. Along the radial direction of the piston body 110, at least part of the piston pin hole 130 is formed on the bottom wall of the weight-reducing groove 140, and another part of the piston pin hole 130 is formed on the side wall of the weight-reducing groove 140. This design can ensure that the weight of the piston body 110 is reduced while making the structure of the piston body 110 more compact.

[0050] Reference Figure 1 In some embodiments, the piston pin hole 130 is located in the middle position of the weight reduction groove 140 along the tangential direction, so that the center of mass of the piston body 110 as a whole is on the axis of the center of the piston pin hole 130. During the operation of the reciprocating compressor, the force on the piston body 110 is provided by the connecting rod 330 and the pin 340. Since the center of mass of the piston body 110 as a whole is on the axis of the center of the piston pin hole 130, the center of mass of the piston body 110 coincides with the center axis of the pin 340 providing the force, thereby reducing the dynamic unbalanced force of the piston body 110 in the reciprocating motion, reducing the intensity of the knocking between the piston body 110 and the inner wall of the cylinder hole 312, and thus reducing vibration and noise.

[0051] It can be understood that by rationally designing the positions of the piston pin hole 130 and the weight-reducing groove 140 so that the center of mass of the piston body 110 as a whole is on the axis of the center of the piston pin hole 130, the intensity of the knocking between the piston body 110 and the inner wall of the cylinder hole 312 can be reduced while also reducing the wear between the piston body 110 and the inner wall of the cylinder hole 312, which is beneficial to increasing the service life.

[0052] Reference Figure 2 and Figure 3As shown, in some embodiments, along the radial direction of the piston body 110, the weight reducing groove 140 extends from the outer periphery toward the inside of the piston body 110, and the maximum depth of the weight reducing groove 140 is A, wherein the value of A cannot be too small, otherwise it will easily affect the weight reducing effect; in addition, the value of A cannot be too large, otherwise it will easily affect the structural strength of the piston body 110; specifically, the range of the maximum depth A of the weight reducing groove 140 satisfies: 8mm≤A≤10mm. The maximum depth A of the weight reducing groove 140 is kept within this range, which can ensure a sufficiently good weight reducing effect and the structural strength of the piston body 110.

[0053] It is understandable that the maximum depth A of the weight reducing groove 140 can be 8.5 mm, 9 mm, 9.5 mm, etc. In actual application, the depth of the weight reducing groove 140 can be designed according to the weight reduction requirements of the piston body 110, so as to reduce the overall weight of the piston body 110 and reduce the inertial excitation during the reciprocating motion of the piston body 110, which is beneficial to reduce the vibration and noise generated during the reciprocating motion of the piston body 110.

[0054] It should be noted that along the radial direction of the piston body 110, the wall thickness of the piston body 110 is greater than the maximum depth A of the weight reduction groove 140, that is, along the radial direction of the piston body 110, the wall thickness of the piston body 110 is greater than 10 mm. The thicker wall thickness of the piston body 110 is beneficial to ensure the structural strength of the piston body 110.

[0055] Reference Figure 1 and Figure 3 As shown, in some embodiments, along the axial direction of the piston body 110, the maximum width of the weight-reducing groove 140 is B, wherein the value of B cannot be too small, otherwise the weight-reducing effect is not ideal; in addition, the value of B cannot be too large, otherwise the width of the rings 111 at both ends of the piston body 110 is easily affected, and the sealing performance between the piston body 110 and the inner wall of the cylinder bore 312 is easily affected. Specifically, the maximum width B of the weight-reducing groove 140 satisfies: 16mm≤B≤18mm. The maximum width B of the weight-reducing groove 140 is kept within this range, which can ensure a sufficiently good weight-reducing effect and the sealing performance between the piston body 110 and the inner wall of the cylinder bore 312.

[0056] It can be understood that the maximum depth B of the weight-reducing groove 140 can be 16 mm, 16.5 mm, 17.5 mm, etc. In actual application, the maximum width B of the weight-reducing groove 140 can be designed according to the weight reduction requirements of the piston body 110 and the sealing requirements between the two ends of the piston body 110 and the inner wall of the cylinder bore 312, so that the piston body 110 can meet the weight reduction requirements while also ensuring the sealing between the two ends of the piston body 110 and the inner wall of the cylinder bore 312.

[0057] It should be noted that along the axial direction of the piston body 110, the width of the piston body 110 is greater than the maximum width B of the weight reduction groove 140, that is, along the axial direction of the piston body 110, the width of the piston body 110 needs to be greater than 18 mm, so that there is enough space at both ends of the piston body 110 to form a ring portion 111 that cooperates with the inner wall of the cylinder hole 312.

[0058] Reference Figure 1 and Figure 2 As shown, in some embodiments, the oil groove 150 is formed at the middle position of the piston body 110 along its axial direction. During the reciprocating motion of the piston body 110, the lubricating oil can pass through the oil hole 160 and flow along the oil groove 150 and the weight reduction groove 140 to the contact portion between the piston body 110 and the inner wall of the cylinder bore 312, which is beneficial to ensure the supply of lubricating oil to both axial ends of the piston body 110, thereby reducing the friction between the piston body 110 and the inner wall of the cylinder bore 312.

[0059] It should be noted that the lubricating oil can absorb and take away the heat generated by the piston body 110 during high-speed reciprocating motion when passing through the oil groove 150 and the weight-reducing groove 140, effectively reducing the temperature of the piston and the inner wall of the cylinder hole 312, and ensuring the stable operation of the reciprocating compressor. In addition, the lubricating oil can also form an oil film between the piston body 110 and the inner wall of the cylinder hole 312, which can reduce the friction between the piston body 110 and the inner wall of the cylinder hole 312, and can also enhance the sealing between the piston body 110 and the inner wall of the cylinder hole 312.

[0060] Reference Figure 1 and Figure 2As shown, in some embodiments, along the axial direction of the piston body 110, the maximum width of the oil groove 150 is C, wherein the value of C cannot be too small. If the value of the maximum width C of the oil groove 150 is too small, the resistance of the lubricating oil flowing in the oil groove 150 is large, which is not conducive to the flow of the lubricating oil, and the amount of lubricating oil flowing in the oil groove 150 is small, and it is difficult to form an oil film between the piston body 110 and the inner wall of the cylinder hole 312, which is easy to affect the sealing performance; in addition, the value of C cannot be too large. If the value of the maximum width C of the oil groove 150 is too large, it is easy to cause the lubricating oil to flow slowly in the oil groove 150, which is easy to affect the heat dissipation. Specifically, it is satisfied that: the maximum width C of the oil groove 150 satisfies: 2mm≤C≤6mm. The maximum width C of the oil groove 150 is kept within this range, which can ensure sufficient oil supply and the sealing performance between the piston body 110 and the inner wall of the cylinder hole 312.

[0061] Reference Figure 2 and Figure 3 As shown, in some embodiments, the number of the oil holes 160 is multiple, specifically between 4 and 8, and the multiple oil holes 160 are spaced apart and distributed on the outer wall of the piston body 110 to facilitate the lubricating oil to fully flow into the oil groove 150 .

[0062] It is understandable that the number of the oil holes 160 may be 4, 6, 8, etc. The specific number of the oil holes 160 may be set according to actual needs; for example, referring to Figure 5 As shown, in some embodiments, the number of the oil holes 160 is 4, and the 4 oil holes 160 are divided into two groups, each group includes 2 oil holes 160, and the two groups of oil holes 160 are disposed on both sides of the piston body 110 and are staggered with the weight reduction groove 140. This arrangement is conducive to ensuring the structural strength of the piston body 110.

[0063] Reference Figure 5 As shown, in some embodiments, the diameter of the oil hole 160 is D, which satisfies 1mm≤D≤4mm, and can be 1mm, 2mm, 3mm, etc. The specific value of the diameter D of the oil hole 160 can be set according to actual needs. The diameter range D of the oil hole 160 is kept within this range, which can ensure that the lubricating oil can pass through the oil hole 160 smoothly, and prevent the oil hole 160 from being too large, which will cause the structural strength of the piston body 110 to decrease.

[0064] Reference Figure 3As shown, in some embodiments, along the axial direction of the piston body 110, the height of the piston body 110 is E, wherein the height range E of the piston body 110 cannot be too large, otherwise it will easily lead to a large contact area and large friction between the piston body 110 and the inner wall of the cylinder bore 312; in addition, the height range E of the piston body 110 cannot be too small, otherwise it will easily lead to poor sealing between the piston body 110 and the inner wall of the cylinder bore 312. Specifically, the height range E of the piston body 110 satisfies: 18mm≤E≤20mm. The height range E of the piston body 110 is kept within this range, which can not only ensure the sealing between the piston body 110 and the inner wall of the cylinder bore 312, but also avoid the excessive contact area between the piston body 110 and the inner wall of the cylinder bore 312, which will lead to increased friction.

[0065] Reference Figure 3 As shown, in some embodiments, along the axial direction of the piston body 110, the height of the mounting groove 120 is F, which satisfies 16 mm ≤ F ≤ 18 mm, and can be specifically 16 mm, 17 mm, 18 mm, etc. The height F of the mounting groove 120 can be specifically set according to actual needs. The height F of the mounting groove 120 is kept within this range, which can ensure that there is enough space for the connecting rod 330 to penetrate, and is also conducive to improving the weight reduction effect.

[0066] It should be noted that along the axial direction of the piston body 110, the height E of the piston body 110 is always greater than the height F of the mounting groove 120. For example, when the height F of the mounting groove 120 is 18 mm, the height E of the piston body 110 is a value greater than 18 mm. The difference between the height E of the piston body 110 and the height F of the mounting groove 120 can be set according to actual needs.

[0067] Reference Figure 3 and Figure 4 As shown, in some embodiments, along the axial direction of the piston body 110, the end face where the opening of the mounting groove 120 is located is the first end face 170, and the first end face 170 is provided with a pin hole 180, and the pin hole 180 passes through the first end face 170 and the inner wall of the piston pin hole 130. During installation, one end of the connecting rod 330 is inserted into the mounting groove 120, and then the pin shaft 340 is inserted into the piston pin hole 130 on one side of the piston body 110, and the end of the pin shaft 340 passes through the end of the connecting rod 330 and then passes out from the piston pin hole 130 on the other side of the piston body 110, and then the pin 350 is inserted from the pin hole 180 at the first end face 170 to lock the pin shaft 340, so that the connecting rod 330 and the piston body 110 are installed as a whole, and the installation process is simple and convenient.

[0068] It is understandable that the pin shaft 340 is provided with a socket matching the shape of the plug pin 350, and the plug pin 350 passes through the plug hole 180 and is inserted into the socket on the pin shaft 340, so that the pin shaft 340 can be fixed in the piston pin hole 130. In addition, the shape of the plug pin 350 can be round, square, etc., which can be set according to actual needs.

[0069] Reference Figure 4 As shown, in some embodiments, there are two latch holes 180 on the first end surface 170, and the two latch holes 180 are disposed on both sides of the mounting groove 120. The two latch holes 180 correspond to each other one by one and penetrate the inner wall of the piston pin hole 130. A latch pin 350 is inserted in each of the two latch holes 180 to fix the pin shaft 340 on the piston body 110.

[0070] Reference Figure 4 and Figure 5 As shown, in some embodiments, along the axial direction perpendicular to the piston pin hole 130, two symmetrically arranged corners 190 are formed at both ends of the mounting groove 120 by cutting or the like, and concave corners 210 are formed at both ends of the corners 190 connected to the mounting groove 120 by cutting or the like, and the two symmetrically arranged corners 190 respectively form four concave corners 210 with the two ends of the mounting groove 120, which is beneficial to reducing the mass of the piston body 110. From the direction toward the first end surface 170, the two corners 190 are arc-shaped, and along the radial direction of the piston body 110, the width of the corners 190 is greater than the width of the middle position of the mounting groove 120, and an "I"-shaped structure is formed between the two corners 190 and the mounting groove 120, which is beneficial to improving the structural strength of the piston body 110.

[0071] Reference Figure 3 and Figure 4 As shown, in some embodiments, along the axial direction of the piston body 110, the circumference of the first end face 170 protrudes to form a cam 200, and the cam 200 is arranged along the circumference of the piston body 110 and is connected to the ring portion 111 of the piston body 110. The cam 200 cooperates with the ring portion 111 to effectively improve the sealing between the piston body 110 and the inner wall of the cylinder bore 312.

[0072] Reference Figure 3As shown, in some embodiments, the height G of the convex edge 200 protruding from the first end face 170 is G, wherein the value of G should not be too large, as a too large value may easily lead to a longer overall length of the piston body 110, a large contact area between the piston body 110 and the inner wall of the cylinder bore 312, and a large friction force; specifically, the height G of the convex edge 200 protruding from the first end face 170 satisfies 2mm≤G≤6mm, and the height G of the convex edge 200 protruding from the first end face 170 is maintained within this range, which can not only ensure the sealing between the piston body 110 and the inner wall of the cylinder bore 312, but also avoid the excessive contact area between the piston body 110 and the inner wall of the cylinder bore 312 causing increased friction.

[0073] Reference Figure 6 As shown, a reciprocating compressor according to an embodiment of the second aspect of the utility model includes a compression mechanism 300, and the compression mechanism 300 includes a crankcase 310, a crankshaft 320, a connecting rod 330 and a compressor piston 100 provided in the embodiment of the first aspect of the utility model, wherein the crankcase 310 is provided with an axial hole 311 and a cylinder hole 312; the crankshaft 320 includes a main shaft 321 and a secondary shaft 322 eccentrically arranged with the main shaft 321, a bearing 360 is provided in the axial hole 311, the main shaft 321 is penetrated through the axial hole 311 and is connected to the bearing 360 in the axial hole 311; the piston body 110 is arranged in the cylinder hole 312, one end of the connecting rod 330 is connected to the secondary shaft 322, and the other end is connected to the piston body 110 through a pin 340.

[0074] According to the reciprocating compressor of the embodiment of the utility model, by setting a weight reduction groove 140 and an oil groove 150 on the compressor piston 100, and setting an oil hole 160 on the bottom wall of the oil groove 150, not only the inertial excitation generated by the reciprocating motion of the piston body 110 is effectively reduced, but also the friction between the outer periphery of the piston body 110 and the inner wall of the cylinder hole 312 can be reduced, thereby reducing the vibration and noise generated during the operation of the reciprocating compressor and improving the service life of the reciprocating compressor.

[0075] According to the refrigeration device of the embodiment of the third aspect of the utility model, the refrigeration device comprises the reciprocating compressor provided by the embodiment of the second aspect of the utility model, and the refrigeration device has all the beneficial effects of the reciprocating compressor.

[0076] It is understandable that the refrigeration equipment may be a refrigerator, a freezer, etc.

[0077] Of course, the present invention is not limited to the above-mentioned embodiments, and technicians familiar with the field may make equivalent modifications or substitutions without violating the spirit of the present invention. These equivalent modifications or substitutions are all included in the scope defined by the claims of this application.

Claims

1. A compressor piston, characterized in that: include: A piston body, wherein a mounting groove for inserting a connecting rod is provided in the piston body, and piston pin holes are respectively provided on two symmetrical sides of the piston body along the radial direction of the piston body, and the piston pin holes on both sides are respectively connected to the mounting groove; The outer wall of the piston body is provided with a weight-reducing groove and an oil groove, wherein two weight-reducing grooves are provided and are symmetrically arranged on both sides of the piston body, the weight-reducing grooves on both sides are communicated with the piston pin holes on both sides, and the weight-reducing grooves are spaced apart from the two end surfaces of the piston body along the axial direction of the piston body; the oil groove is arranged along the circumferential direction of the piston body and is communicated with the weight-reducing grooves on both sides, and the bottom wall of the oil groove is provided with a plurality of oil holes communicated with the mounting groove, and the plurality of oil holes are spaced apart along the circumferential direction of the piston body.

2. The compressor piston according to claim 1, characterized in that The weight-reducing groove is arranged along the tangent direction of the outer circumference of the piston body. Along the radial direction of the piston body, at least a portion of the piston pin hole is formed on the bottom wall of the weight-reducing groove and is located at the middle position of the weight-reducing groove along the tangent direction.

3. The compressor piston according to claim 2, characterized in that The maximum depth of the weight-reducing groove along the radial direction of the piston body ranges from 8 mm to 10 mm, and the maximum width of the weight-reducing groove along the axial direction of the piston body ranges from 16 mm to 18 mm.

4. The compressor piston according to claim 1, characterized in that The oil groove is formed at a middle position of the piston body along the axial direction thereof, and the maximum width of the oil groove along the axial direction of the piston body ranges from 2 mm to 6 mm.

5. The compressor piston according to claim 1, characterized in that The number of the oil holes ranges from 4 to 8, and the diameter of the oil holes ranges from 1 mm to 4 mm.

6. The compressor piston according to claim 1, characterized in that Along the axial direction of the piston body, the height of the piston body ranges from 18 mm to 20 mm, and the height of the mounting groove ranges from 16 mm to 18 mm.

7. The compressor piston according to claim 1, characterized in that The piston pin hole is used to insert a pin shaft. Along the axial direction of the piston body, the end face where the opening of the mounting groove is located is the first end face. The first end face is provided with a pin hole for a pin to pass through to lock the pin shaft. The pin hole passes through the first end face and the inner wall of the piston pin hole. Along the axial direction perpendicular to the piston pin hole, two symmetrically arranged corners are respectively provided at both ends of the mounting groove, and the width between the two symmetrical corners is greater than the width of the middle position of the mounting groove.

8. The compressor piston according to claim 7, characterized in that A convex edge is provided on the periphery of the first end surface, and the convex edge is arranged along the circumference of the piston body. The height of the convex edge protruding from the first end surface ranges from 2 mm to 6 mm.

9. A reciprocating compressor, characterized in that: include: A crankcase having a shaft hole and a cylinder hole; A crankshaft, comprising a main shaft and a secondary shaft eccentrically arranged with the main shaft, wherein the main shaft is rotatably connected to the shaft hole; A connecting rod, one end of which is connected to the secondary shaft; The compressor piston according to any one of claims 1 to 8, wherein the piston body is disposed in the cylinder hole, and the piston body is connected to the other end of the connecting rod.

10. A refrigeration device, characterized in that: A reciprocating compressor comprising the method of claim 9.

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