Compressor and refrigeration equipment

Abstract

The utility model discloses a compressor and refrigeration equipment, the compressor comprises a crankcase, a crankshaft, a piston and a connecting rod, the crankcase comprises a body part and a cylinder part, the body part is provided with a shaft hole, and the cylinder part is provided with a compression cavity; the crankshaft penetrates through the shaft hole, is in running fit with the body part and is provided with an eccentric part; the piston is slidably mounted in the compression cavity and comprises a sealing part, an oil storage part and a guide part which are sequentially connected, the outer circumferential wall of the sealing part is in sealing fit with the inner circumferential wall of the compression cavity, the oil storage part is provided with an oil groove, the oil groove is arranged in the circumferential direction of the compression cavity, the piston is further provided with a pin hole, and the outer circumferential wall of the guide part is provided with a first groove body sunken inwards. The first groove body is positioned at at least one end of the guide part along the axis direction of the pin hole; one end of the connecting rod is hinged to the eccentric part, and the other end of the connecting rod is hinged to the piston through a shaft pin penetrating through the pin hole. According to the compressor, the friction loss between the piston and the inner circumferential wall of the compression cavity can be reduced, and the energy efficiency of the compressor is effectively improved.

Description

Technical Field

[0001] This utility model relates to the field of compressor technology, and in particular to a compressor and refrigeration equipment. Background Technology

[0002] In the operation of a reciprocating compressor, the crankshaft drives the piston to reciprocate within the compression chamber of the cylinder via the connecting rod, compressing the refrigerant to perform work. During this reciprocating motion, friction exists between the piston and the inner wall of the compression chamber, and this frictional loss accounts for a significant proportion of the compressor's total frictional loss. In existing compressors, the substantial frictional loss between the piston and the inner wall of the compression chamber leads to a decrease in compressor efficiency. Utility Model Content

[0003] This invention aims to solve at least one of the technical problems existing in the prior art. To this end, this invention proposes a compressor that can reduce frictional losses between the piston and the inner peripheral wall of the compression chamber, effectively improving the compressor's energy efficiency.

[0004] This utility model also provides a refrigeration device having the above-mentioned compressor.

[0005] A compressor according to a first aspect of the present invention includes a crankcase, a body portion, and a cylinder portion. The body portion has a shaft hole, and the cylinder portion is connected to one end of the body portion radially along the shaft hole. The cylinder portion has a compression chamber. A crankshaft passes through the shaft hole and rotatably engages with the body portion. The crankshaft has an eccentric portion. A piston is slidably mounted in the compression chamber along the central axis of the compression chamber. The piston includes a sealing portion, an oil reservoir portion, and a guide portion. The sealing portion, the oil reservoir portion, and the guide portion are along the central axis. The lines are connected sequentially in the direction of the oil reservoir, and the sealing part is located at the end of the oil reservoir away from the crankshaft. The outer peripheral wall of the sealing part is sealed to the inner peripheral wall of the compression chamber. The oil reservoir is provided with an oil groove, which is arranged circumferentially along the compression chamber. The piston is also provided with a pin hole. The outer peripheral wall of the guide part is provided with an inwardly recessed first groove, which is located on at least one side of the guide part along the axial direction of the pin hole. The connecting rod is hinged at one end to the eccentric part and at the other end to the piston through a shaft pin, which passes through the pin hole.

[0006] The compressor according to the first aspect of this utility model has at least the following beneficial effects: By providing a first groove on the outer peripheral wall of the piston guide portion, the contact area between the guide portion and the inner peripheral wall of the compression chamber can be reduced without affecting the sealing performance between the piston and the inner peripheral wall of the compression chamber, i.e., the contact area between the piston and the inner peripheral wall of the compression chamber is reduced, thereby effectively reducing frictional losses between the piston and the inner peripheral wall of the compression chamber and effectively improving the energy efficiency of the compressor. Simultaneously, since the first groove is provided on both sides of the guide portion along the axial direction of the pin hole, the pressure-bearing area on both sides of the guide portion along the direction perpendicular to the pin hole axis can be ensured to be sufficiently large, enabling the guide portion to play a stable guiding role, and ensuring that the minimum thickness of the oil film between the guide portion and the inner peripheral wall of the compression chamber is sufficiently large, improving lubricity, reducing wear, and further reducing frictional losses.

[0007] According to some embodiments of the present invention, the first groove extends through the end faces of both ends of the guide portion along the direction of the central axis.

[0008] According to some embodiments of the present invention, a plane passing through the central axis of the piston and the axis of the pin hole is a reference plane, and the first groove is arranged symmetrically about the reference plane.

[0009] According to some embodiments of the present invention, the angle between the two ends of the first groove along the circumferential direction of the guide portion and the center of the piston is θ, which satisfies: 0°<θ≤140°.

[0010] According to some embodiments of the present invention, the depth of the first groove is equal at all points along the circumference of the guide portion; or, the depth of the first groove decreases from the middle to both ends along the circumference of the guide portion.

[0011] According to some embodiments of this utility model, the maximum depth of the first groove is D, which satisfies: 0 < D ≤ 1 mm.

[0012] According to some embodiments of the present invention, the inner peripheral wall of the compression cavity is provided with a plurality of second grooves, each of which is located at one end of the compression cavity near the crankshaft, and the plurality of second grooves are respectively located on at least one side of the compression cavity along the axial direction of the pin hole.

[0013] According to some embodiments of the present invention, the cylinder portion is provided with a first clearance groove and a second clearance groove. The first clearance groove is located on the side of the cylinder portion away from the body portion along the axial direction of the pin hole, and the first clearance groove penetrates the inner peripheral wall of the compression cavity and the outer peripheral wall of the cylinder portion along the radial direction of the compression cavity. The second clearance groove is located on the side of the cylinder portion close to the body portion along the axial direction of the pin hole. A plurality of second grooves are respectively located at both ends of the first clearance groove along the circumference of the compression cavity and at both ends of the second clearance groove along the circumference of the compression cavity.

[0014] According to some embodiments of the present invention, the second groove penetrates the inner peripheral wall of the compression cavity and the outer peripheral wall of the cylinder portion along the radial direction of the compression cavity.

[0015] According to some embodiments of the present invention, along the direction of the central axis of the compression chamber, the length of the cylinder part is L1, the length of the sealing part is L2, and the length of the second groove is L3, satisfying: L3≤L1-L2-2*r, where r is the eccentricity of the eccentric part.

[0016] The refrigeration device according to a second aspect of the present invention includes the compressor of the first aspect of the present invention.

[0017] The refrigeration equipment according to the second aspect of this utility model has at least the following beneficial effects: Because the refrigeration equipment uses the aforementioned compressor, by providing a first groove on the outer peripheral wall of the piston guide portion, the contact area between the guide portion and the inner peripheral wall of the compression chamber can be reduced without affecting the sealing performance between the piston and the inner peripheral wall of the compression chamber. This effectively reduces frictional losses between the piston and the inner peripheral wall of the compression chamber, thereby improving the compressor's energy efficiency. Simultaneously, since the first groove is located on both sides of the guide portion along the axial direction of the pin hole, the bearing area on both sides of the guide portion along the direction perpendicular to the pin hole is sufficiently large, enabling the guide portion to perform a stable guiding function. It also ensures that the minimum thickness of the oil film between the guide portion and the inner peripheral wall of the compression chamber is sufficiently large, improving lubrication, reducing wear, and further reducing frictional losses.

[0018] Additional aspects and advantages of this invention 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 the invention. Attached Figure Description

[0019] The present invention will be further described below with reference to the accompanying drawings and embodiments, wherein:

[0020] Figure 1 This is a schematic diagram of the internal structure of the compressor in an embodiment of this utility model;

[0021] Figure 2 This is a top view of the piston in an embodiment of this utility model;

[0022] Figure 3 This is an axial schematic diagram of the piston in some embodiments of this utility model;

[0023] Figure 4 This is an axial schematic diagram of the piston in some other embodiments of this utility model;

[0024] Figure 5 This is a front sectional view of the crankcase in an embodiment of this utility model;

[0025] Figure 6 This is a schematic diagram of the crankcase structure in some embodiments of this utility model;

[0026] Figure 7 This is a structural schematic diagram of the crankcase in some other embodiments of this utility model;

[0027] Figure 8 This is a top sectional view of the crankcase in an embodiment of this utility model;

[0028] Figure 9 This is a front view of the crankshaft in an embodiment of this utility model.

[0029] Figure label:

[0030] Crankcase 100; Body 110; Shaft hole 111; Cylinder section 120; Compression chamber 121; First clearance groove 122; Second clearance groove 123; Second groove body 124;

[0031] Crankshaft 200; Main shaft 210; Bearing section 220; Eccentric section 230;

[0032] Piston 300; Sealing part 310; Oil reservoir 320; Oil groove 321; Guide part 330; First groove 331; Air-proof structure 332; Pin hole 340;

[0033] Link 400; First connecting part 410; Second connecting part 420;

[0034] Reference plane P; Detailed Implementation

[0035] The embodiments of this utility model are described in detail below. Examples of these 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 utility model, and should not be construed as limiting this utility model.

[0036] In the description of this utility model, it should be understood that the directional descriptions, such as up, down, front, back, left, right, etc., indicate the directional or positional relationship based on the directional or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this utility model 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. Therefore, they should not be construed as limitations on this utility model.

[0037] In the description of this utility model, "several" means one or more, "multiple" means two or more, "greater than," "less than," and "exceeding" are understood to exclude the stated number, while "above," "below," and "within" are understood to include the stated number. If "first" or "second" is used in the description, it is only for the purpose of distinguishing technical features and should not be construed as indicating or implying relative importance, or implicitly indicating the number of indicated technical features, or implicitly indicating the order of the indicated technical features.

[0038] In the description of this utility model, unless otherwise explicitly defined, terms such as setting, installing, connecting, assembling, and cooperating should be interpreted broadly, and those skilled in the art can reasonably determine the specific meaning of the above terms in this utility model in conjunction with the specific content of the technical solution.

[0039] In the operation of a reciprocating compressor, the crankshaft drives the piston to reciprocate within the compression chamber of the cylinder via the connecting rod, compressing the refrigerant to perform work. During this reciprocating motion, friction occurs between the piston and the inner wall of the compression chamber, resulting in frictional losses. In existing compressors, the frictional losses between the piston and the inner wall of the compression chamber are relatively large, leading to a decrease in compressor efficiency. Since the frictional losses between the piston and the inner wall of the compression chamber account for a significant proportion of the total frictional losses in the compressor, reducing these losses plays a crucial role in improving compressor efficiency.

[0040] Therefore, referring to Figures 1 to 9 As shown, the first aspect of this utility model provides a compressor applied to refrigeration equipment, such as refrigerators or freezers.

[0041] Reference Figure 1 and Figure 8 As shown, it can be understood that the compressor includes a housing and a crankcase 100, a crankshaft 200, a piston 300 and a connecting rod 400 disposed within the housing. Specifically, the crankcase 100 includes a body portion 110 and a cylinder portion 120. The body portion 110 is generally a rectangular platform structure and is arranged in a horizontal direction. The body portion 110 is connected to the bottom of the housing through a shock-absorbing component (such as a spring, an elastic seat, etc.). A shaft hole 111 is provided in the middle of the body portion 110, and the shaft hole 111 penetrates through both end faces of the body portion 110 in a vertical direction.

[0042] Reference Figure 1 and Figure 8 As shown, it can be understood that the cylinder section 120 is connected to the body section 110 and is an integral structure with the body section 110. The cylinder section 120 is located at one end of the body section 110 along the radial direction of the shaft hole 111. Specifically, the cylinder section 120 is connected to the upper end face of the front end of the body section 110. The cylinder section 120 is provided with a compression chamber 121, which extends through both end faces of the cylinder section 120 in the front-rear direction. Generally, a valve plate assembly and a cylinder head are sequentially installed at the end of the cylinder section 120 opposite to the shaft hole 111. The valve plate assembly is provided with an exhaust port, and the cylinder head is provided with an exhaust chamber, which is connected to the compression chamber 121 through the exhaust port.

[0043] Reference Figure 1 , Figure 8 and Figure 9 As shown, it can be understood that the crankshaft 200 passes through the shaft hole 111 and rotates with the body portion 110. Specifically, the crankshaft 200 includes a main shaft 210, a support portion 220, and an eccentric portion 230. The main shaft 210 is arranged in the vertical direction. The support portion 220 is generally plate-shaped and is connected to the upper end of the main shaft 210. The support portion 220 protrudes radially from the outer peripheral wall of the main shaft 210. The eccentric portion 230 is cylindrical and is arranged in the vertical direction. The eccentric portion 230 is connected to the upper end of the support portion 220, and the central axis of the eccentric portion 230 is offset from the central axis of the main shaft 210. The central axis of the eccentric portion 230 is parallel to the central axis of the main shaft 210. The main shaft 210 passes through the shaft hole 111 from top to bottom and rotates in conjunction with the body portion 110. The bearing portion 220 and the eccentric portion 230 are located above the body portion 110, and a plane bearing is provided between the bearing portion 220 and the body portion 110 to provide upward support to the crankshaft 200 and ensure the stable rotation of the crankshaft 200. It is easy to understand that during the operation of the compressor, the crankshaft 200 rotates around the central axis of the main shaft 210, that is, the rotation axis of the crankshaft 200 coincides with the central axis of the main shaft 210.

[0044] Reference Figure 1 and Figure 2 As shown, it can be understood that the piston 300 is slidably mounted in the compression chamber 121 in the front-back direction, which is the direction of the central axis of the compression chamber 121. Specifically, the piston 300 includes a sealing part 310, an oil reservoir 320, and a guide part 330. The sealing part 310, the oil reservoir 320, and the guide part 330 are connected sequentially along the central axis of the compression chamber 121, and the sealing part 310 is located at the end of the oil reservoir 320 away from the crankshaft 200, that is, the guide part 330 is located at the end of the oil reservoir 320 closer to the crankshaft 200.

[0045] Reference Figure 2As shown, the sealing part 310 has a cylindrical structure. The outer peripheral wall of the sealing part 310 abuts against and seals against the inner peripheral wall of the compression chamber 121, thus preventing refrigerant leakage during the reciprocating movement of the piston 300. The oil reservoir 320 has a cylindrical structure and is provided with an oil groove 321, which extends circumferentially along the compression chamber 121. It is easy to understand that the oil groove 321 can store a certain amount of lubricating oil to provide lubrication between the piston 300 and the inner peripheral wall of the compression chamber 121, ensuring stable movement of the piston 300. It also helps reduce wear between the piston 300 and the cylinder 120, improving the reliability of the compressor.

[0046] Reference Figure 2 As shown, it can be understood that the guide portion 330 is generally cylindrical in shape and is used to guide the movement of the piston 300. Specifically, the outer peripheral walls on the left and right sides of the guide portion 330 abut against the inner peripheral wall of the compression chamber 121 to precisely guide the piston 300 to reciprocate in the front-back direction within the compression chamber 121.

[0047] Reference Figure 1 As shown, it can be understood that the connecting rod 400 connects the piston 300 and the crankshaft 200. Specifically, the connecting rod 400 has a first connecting portion 410 and a second connecting portion 420 at its two ends. The first connecting portion 410 is located at the rear end of the rod body, that is, at the end of the rod body closer to the crankshaft 200, and the second connecting portion 420 is located at the front end of the rod body, that is, at the end of the rod body closer to the piston 300.

[0048] Understandably, the first connecting portion 410 is provided with a first connecting hole, which penetrates both end faces of the first connecting portion 410 in a vertical direction, and the central axis of the first connecting hole is arranged in a vertical direction. Similarly, the second connecting portion 420 is provided with a second connecting hole, which penetrates both end faces of the second connecting portion 420 in a vertical direction, and the central axis of the second connecting hole is arranged in a vertical direction. That is to say, both the first connecting portion 410 and the second connecting portion 420 are approximately sleeve structures.

[0049] It is understood that the eccentric part 230 is inserted into the first connecting hole from bottom to top, and the eccentric part 230 is rotatably engaged with the first connecting part 410. That is to say, the first connecting part 410 is hinged to the eccentric part 230, and the hinge axis of the first connecting part 410 and the eccentric part 230 is parallel to the rotation axis of the crankshaft 200.

[0050] Reference Figure 1As shown, it can be understood that the piston 300 is provided with a pin hole 340, which is arranged in the vertical direction, that is, the axis of the pin hole 340 is arranged in the vertical direction. The pin hole 340 is formed in the oil reservoir 320 and the guide portion 330, and does not affect the sealing performance of the sealing portion 310. A pin is connected between the piston 300 and the second connecting portion 420. The pin passes through the pin hole 340 and the second connecting hole, and the pin is rotatably engaged with at least one of the piston 300 and the second connecting portion 420. In this embodiment, the pin is rotatably engaged with the piston 300 and the second connecting portion 420. Therefore, the second connecting portion 420 is hinged to the piston 300, and the hinge axis of the second connecting portion 420 and the piston 300 is parallel to the rotation axis of the crankshaft 200. That is, the hinge axis of the first connecting portion 410 and the eccentric portion 230 and the hinge axis of the second connecting portion 420 and the piston 300 are parallel.

[0051] Understandably, a compressor typically also includes a motor assembly, which is mounted below the main body 110. The motor assembly includes a stator and a rotor. The stator is fixedly connected to the main body 110, and the rotor is fixedly connected to the main shaft 210 and rotatably mounted within the inner bore of the stator. Therefore, during compressor operation, the motor assembly drives the crankshaft 200 to rotate. The crankshaft 200, through the connecting rod 400, drives the piston 300 to reciprocate within the compression chamber 121, thereby compressing the refrigerant to perform work.

[0052] It is easy to understand that during the reciprocating movement of the piston 300 within the compression chamber 121 via the connecting rod 400 driven by the crankshaft 200, the force exerted by the connecting rod 400 on the piston 300 can be decomposed into a first component in the longitudinal direction and a second component in the lateral direction. The first component drives the piston 300 to move longitudinally within the compression chamber 121, while the second component acts on the cylinder 120 via the piston 300, causing the outer peripheral wall of the guide portion 330 on either the left or right side to conform to the inner peripheral wall of the compression chamber 121, thus precisely guiding the piston 300's longitudinal movement within the compression chamber 121. According to the principle of action and reaction, the piston 300 bears the reaction force exerted by the cylinder 120, the direction of which is opposite to the direction of the second component. In other words, the outer peripheral walls on the left and right sides of the guide portion 330 of the piston 300 serve as pressure-bearing surfaces, and the area of ​​these surfaces is large enough to ensure that the guide portion 330 provides stable guidance.

[0053] It is understandable that the two sides of the guide portion 330 along the axial direction of the pin hole 340 are the upper and lower sides of the guide portion 330. The two sides of the guide portion 330 along the direction perpendicular to the axial direction of the pin hole 340 are the left and right sides of the guide portion 330.

[0054] Reference Figures 2 to 4As shown, it can be understood that the outer peripheral wall of the guide portion 330 is provided with an inwardly recessed first groove 331. Specifically, in this embodiment, the guide portion 330 is provided with a first groove 331 on both the upper and lower sides. The first groove 331 located on the upper side of the guide portion 330 is recessed downward and located on the uppermost part of the outer peripheral wall of the guide portion 330, while the first groove 331 located on the lower side of the guide portion 330 is recessed upward and located on the lowermost part of the outer peripheral wall of the guide portion 330.

[0055] Therefore, by providing a first groove 331 on the outer peripheral wall of the guide portion 330 of the piston 300, the contact area between the guide portion 330 and the inner peripheral wall of the compression chamber 121 can be reduced, that is, the contact area between the piston 300 and the inner peripheral wall of the compression chamber 121 can be reduced, thereby effectively reducing the friction loss between the piston 300 and the inner peripheral wall of the compression chamber 121 and effectively improving the energy efficiency of the compressor.

[0056] It is easy to understand that since the first groove 331 is located in the guide portion 330 rather than in the sealing portion 310, the first groove 331 is prevented from affecting the sealing performance between the piston 300 and the inner peripheral wall of the compression chamber 121.

[0057] It is easy to understand that, since the two first grooves 331 are respectively located on the upper and lower sides of the guide portion 330, the area of ​​the pressure-bearing surfaces on the left and right sides of the guide portion 330 (i.e., the pressure-bearing area) is large enough, effectively ensuring that the guide portion 330 plays a stable guiding role, thereby accurately guiding the piston 300 to reciprocate in the front-to-back direction within the compression chamber 121. At the same time, a sufficiently large pressure-bearing area helps to reduce surface pressure, thereby increasing the minimum oil film thickness between the guide portion 330 and the inner peripheral wall of the compression chamber 121, improving lubrication, reducing wear between the guide portion 330 and the cylinder portion 120, and further reducing friction loss.

[0058] It is easy to understand that the first groove 331 can store a certain amount of lubricating oil, thereby supplementing the inner peripheral wall of the piston 300 and the compression chamber 121 with additional lubricating oil, further improving the lubricity between the piston 300 and the inner peripheral wall of the compression chamber 121, reducing the wear between the piston 300 and the cylinder 120, and further reducing friction loss.

[0059] It is understood that in some embodiments, the first groove 331 is provided only on the upper side of the guide portion 330, or only on the lower side of the guide portion 330. This can also reduce the contact area between the guide portion 330 and the inner peripheral wall of the compression chamber 121, that is, reduce the contact area between the piston 300 and the inner peripheral wall of the compression chamber 121, thereby effectively reducing the friction loss between the piston 300 and the inner peripheral wall of the compression chamber 121 and effectively improving the energy efficiency of the compressor. Furthermore, it does not affect the sealing performance between the piston 300 and the inner peripheral wall of the compression chamber 121, ensuring that the guide portion 330 plays a stable guiding role, reducing the wear of the piston 300 and the cylinder portion 120, and further reducing friction loss.

[0060] Reference Figure 2 As shown, it can be understood that the first groove 331 extends through the end faces of both ends of the guide portion 330 along the central axis of the compression chamber 121. In this way, on the one hand, both ends of the first groove 331 along the central axis of the compression chamber 121 are open, facilitating processing; on the other hand, it increases the size of the first groove 331, further reducing the contact area between the guide portion 330 and the inner peripheral wall of the compression chamber 121, i.e., further reducing the contact area between the piston 300 and the inner peripheral wall of the compression chamber 121, thereby effectively reducing frictional losses between the piston 300 and the inner peripheral wall of the compression chamber 121, and effectively improving the energy efficiency of the compressor. Furthermore, while increasing the size of the first groove 331, it ensures that the area (i.e., the pressure-bearing area) of the left and right pressure-bearing surfaces of the guide portion 330 is sufficiently large.

[0061] It is understood that in some other embodiments, the first groove 331 penetrates one of the end faces of the guide portion 330 along the central axis of the compression chamber 121. For example, the first groove 331 penetrates the front end face of the guide portion 330, or the first groove 331 penetrates the rear end face of the guide portion 330. This can also increase the size of the first groove 331 to a certain extent, thereby further reducing the contact area between the guide portion 330 and the inner peripheral wall of the compression chamber 121, that is, further reducing the contact area between the piston 300 and the inner peripheral wall of the compression chamber 121, thereby effectively reducing the frictional loss between the piston 300 and the inner peripheral wall of the compression chamber 121, and effectively improving the energy efficiency of the compressor.

[0062] Reference Figure 3 and Figure 4 As shown, it can be understood that the plane passing through the central axis of the piston 300 and the axis of the pin hole 340 is defined as the reference plane P, and the first groove 331 is arranged symmetrically about the reference plane P. That is, the first groove 331 is arranged symmetrically in the left-right direction. On the one hand, this facilitates processing, and on the other hand, it ensures that the bearing areas on the left and right sides of the guide part 330 are equal, thus guaranteeing that the guide part 330 plays a stable guiding role.

[0063] Reference Figure 3and Figure 4 As shown, it can be understood that the angle between the lines connecting the two ends of the first groove 331 along the circumference of the guide portion 330 and the center of the piston 300 is defined as θ. Generally, the first groove 331 is arranged along the circumference of the guide portion 330 and has an arc-shaped shape. The angle θ can be understood as the central angle corresponding to the arc-shaped first groove 331. The angle θ satisfies: 0°<θ≤140°. If θ>140°, that is, the length of the first groove 331 along the circumference of the guide portion 330 is too large, resulting in too small bearing areas on the left and right sides of the guide portion 330. During the reciprocating movement of the piston 300, the guide portion 330 is easily deformed by force, affecting the guiding function of the guide portion 330. Therefore, by making 0°<θ≤140°, while ensuring the guiding function of the guide part 330, the first groove 331 is enlarged to reduce the contact area between the guide part 330 and the inner peripheral wall of the compression chamber 121, thereby reducing the friction loss between the piston 300 and the inner peripheral wall of the compression chamber 121 and effectively improving the energy efficiency of the compressor.

[0064] Reference Figure 3 and Figure 4 As shown, it can be understood that in order to reduce the weight of the piston 300 and reduce the inertial load, a clearance structure 332 is provided in the middle of the guide portion 330. The larger wall thickness of the guide portion 330 is beneficial to ensuring the structural stability of the guide portion 330. The wall thickness of the guide portion 330 is the distance between the outer peripheral wall of the guide portion 330 and the inner peripheral wall of the clearance structure 332 in the radial direction of the guide portion 330.

[0065] Reference Figure 3 As shown, it can be understood that the depth of the first groove 331 is defined as the radial depth of the first groove 331 along the radial direction of the guide portion 330. The depth of the first groove 331 is equal at all points along the circumference of the guide portion 330, which facilitates processing.

[0066] Reference Figure 4 As shown, it can be understood that in some other embodiments, the depth of the first groove 331 decreases from the middle to both ends along the circumferential direction of the guide portion 330. This reduces the contact area between the guide portion 330 and the inner peripheral wall of the compression cavity 121, and also makes the wall thickness of the guide portion 330 at the first groove 331 gradually change, which helps to ensure the structural stability of the guide portion 330.

[0067] Reference Figure 3 and Figure 4As shown, it can be understood that the maximum depth of the first groove 331 is defined as D, satisfying: 0 < D ≤ 1 mm. For the first groove 331 to have equal depth at all points along the circumference of the guide portion 330, the depth at any point in the first groove 331 is D. For the first groove 331 to decrease in depth from the middle to both ends along the circumference of the guide portion 330, the depth at the middle position of the first groove 331 is D. By ensuring 0 < D ≤ 1 mm, the contact area between the guide portion 330 and the inner circumferential wall of the compression cavity 121 is reduced, while avoiding the guide portion 330 having too small a wall thickness, which would affect the structural stability of the guide portion 330, thus enabling the guide portion 330 to perform a stable guiding function.

[0068] Reference Figures 5 to 7 As shown, it can be understood that a first clearance groove 122 is provided on the upper side of the cylinder section 120. That is, the first clearance groove 122 is located on the side of the cylinder section 120 away from the body section 110 along the axial direction of the pin hole 340. The first clearance groove 122 penetrates the inner peripheral wall of the compression chamber 121 and the outer peripheral wall of the cylinder section 120 radially along the compression chamber 121. Correspondingly, a second clearance groove 123 is also provided on the lower side of the cylinder section 120. The second clearance groove 123 penetrates the inner peripheral wall of the compression chamber 121 and is located directly below the first clearance groove 122. That is, the second clearance groove 123 is located on the side of the cylinder section 120 close to the body section 110 along the axial direction of the pin hole 340. When installing the shaft pin connecting the piston 300 and the connecting rod 400, the shaft pin passes through the first clearance groove 122 into the pin hole 340 of the piston 300 and the second connecting hole of the connecting rod 400, which facilitates installation. By setting a second clearance groove 123 located directly below the first clearance groove 122, it is beneficial to improve the machining accuracy of the inner peripheral wall of the compression cavity 121 when machining the inner peripheral wall of the compression cavity 121.

[0069] Reference Figure 5 and Figure 6As shown, it can be understood that the inner peripheral wall of the compression chamber 121 is also provided with a plurality of second grooves 124. The second grooves 124 are located at one end of the compression chamber 121 near the crankshaft 200, and the plurality of second grooves 124 are respectively located at at least one on the upper and lower sides of the compression chamber 121. In this embodiment, the upper and lower sides of the compression chamber 121 are provided with second grooves 124 respectively located at both ends of the first clearance groove 122 along the circumference of the compression chamber 121, and the lower side of the compression chamber 121 is provided with second grooves 124 respectively located at both ends of the second clearance groove 123 along the circumference of the compression chamber 121. Due to the reduction in the wall thickness of the guide portion 330 of the piston 300, the wall thickness of the guide portion 330 undergoes slight deformation during the reciprocating movement of the piston 300, which causes the outer peripheral walls of the upper and lower sides of the guide portion 330 to contact the inner peripheral wall of the compression chamber 121 and generate frictional wear. By providing the second groove 124, the risk of the outer peripheral walls of the upper and lower sides of the guide portion 330 coming into contact with the inner peripheral wall of the compression cavity 121 can be reduced, thereby effectively reducing frictional loss.

[0070] It is understood that in some other embodiments, a second groove 124 is provided on the inner peripheral wall of the upper or lower side of the compression cavity 121, which can reduce the risk of the outer peripheral wall of the upper and lower sides of the guide portion 330 contacting the inner peripheral wall of the compression cavity 121 to a certain extent, thereby effectively reducing frictional loss.

[0071] Reference Figure 7 As shown, it can be understood that in some other embodiments, the second groove 124 penetrates the inner peripheral wall of the compression cavity 121 and the outer peripheral wall of the cylinder portion 120 along the radial direction of the compression cavity 121. In this case, the second groove 124 located on the upper side of the compression cavity 121 is integrated with the first clearance groove 122, and the second groove 124 located on the lower side of the compression cavity 121 is integrated with the second clearance groove 123, which facilitates processing.

[0072] Reference Figure 2 and Figure 8 As shown, it can be understood that, along the central axis of the compression chamber 121, the length of the cylinder section 120 is defined as L1, the length of the sealing section 310 as L2, and the length of the second groove 124 as L3. The length of the cylinder section 120 is the distance between two end faces of the cylinder section 120 that are opposite to each other along the central axis of the compression chamber 121. Similarly, the length of the sealing section 310 is the distance between two end faces of the sealing section 310 that are opposite to each other along the central axis of the compression chamber 121. The eccentricity of the eccentric section 230 is defined as r, where r is the distance between the central axis of the main shaft 210 and the central axis of the eccentric section 230.

[0073] Reference Figure 2 , Figure 8 and Figure 9As shown, it can be understood that the length L1 of the cylinder section 120, the length L2 of the sealing section 310, the length L3 of the second groove 124, and the eccentricity r of the eccentric section 230 satisfy: L3≤L1-L2-2*r. It is easy to understand that 2r can be understood as the maximum stroke of the piston 300 in the compression chamber 121, and L1-L2-2*r can be understood as the distance in the direction of the central axis of the compression chamber 121 between the end face of the sealing section 310 near the crankshaft 200 and the end face of the cylinder section 120 near the crankshaft 200 when the piston 300 moves to the position closest to the crankshaft 200. Therefore, by ensuring that L3≤L1-L2-2*r, the sealing part 310 of the piston 300 can be prevented from moving to the second groove 124. This prevents the second groove 124 from affecting the sealing performance between the sealing part 310 and the inner peripheral wall of the compression chamber 121 during the reciprocating movement of the piston 300, thus avoiding refrigerant leakage. This enables normal compression of the refrigerant and improves the reliability of the compression chamber 121.

[0074] The refrigeration device of the second aspect of this utility model includes the compressor of the first aspect of this utility model. The refrigeration device here may be a refrigerator, freezer, etc.

[0075] Since the refrigeration equipment adopts all the technical solutions of the compressor in the above embodiments, it has at least all the beneficial effects brought about by the technical solutions in the above embodiments.

[0076] The embodiments of the present utility model have been described in detail above with reference to the accompanying drawings. However, the present utility model is not limited to the above embodiments. Within the scope of knowledge possessed by those skilled in the art, various changes can be made without departing from the spirit of the present utility model.

Claims

1. Compressor, characterized in that, The application relates to a compressor. The compressor comprises a crankcase, a crankshaft, a piston and a connecting rod. The crankcase comprises a body part and a cylinder part, the body part is provided with a shaft hole, the cylinder part is connected to one end of the body part along the radial direction of the shaft hole, and the cylinder part is provided with a compression cavity. The crankshaft is arranged in the shaft hole and rotationally connected with the body part, and the crankshaft is provided with an eccentric part. The piston is slidingly arranged in the compression cavity along the central axis of the compression cavity, and the piston comprises a sealing part, an oil storage part and a guide part.

2. The compressor of claim 1, wherein: The sealing part, the oil storage part and the guide part are sequentially connected along the central axis, and the sealing part is located at one end of the oil storage part away from the crankshaft.

3. The compressor of claim 1, wherein: The outer peripheral wall of the sealing part is sealingly connected with the inner peripheral wall of the compression cavity.

4. The compressor of claim 3, wherein: The oil storage part is provided with an oil groove arranged along the circumferential direction of the compression cavity.

5. The compressor of claim 1, wherein: The guide part is provided with a first groove body recessed inward, and the first groove body is located at least one side of the guide part along the axis direction of the pin hole.

6. The compressor of claim 5, wherein: One end of the connecting rod is hingedly connected with the eccentric part, and the other end of the connecting rod is hingedly connected with the piston through a shaft pin arranged in the pin hole.

7. The compressor of claim 1, wherein: The first groove body penetrates the end faces of both ends of the guide part along the central axis.

8. The compressor of claim 7, wherein: A plane passing through the central axis of the piston and the axis of the pin hole is a reference plane, and the first groove body is symmetrically arranged about the reference plane.

9. The compressor of claim 7 or 8, characterized in that: The included angle between the first groove body and the connecting line of the center of the piston at both ends along the circumferential direction of the guide part is theta, and 0 < theta <= 140.

10. The compressor of claim 7 or 8, wherein: The depth of the first groove body is equal at different positions along the circumferential direction of the guide part; or the depth of the first groove body decreases from the middle to both ends along the circumferential direction of the guide part.

11. A refrigeration appliance characterised in that, The maximum depth of the first groove body is D, and 0 < D <= 1 mm. The inner peripheral wall of the compression cavity is provided with a plurality of second groove bodies, and the plurality of second groove bodies are located at one end of the compression cavity close to the crankshaft. The cylinder part is provided with a first avoiding groove and a second avoiding groove. The first avoiding groove is located at one side of the cylinder part away from the body part along the axis direction of the pin hole, and the first avoiding groove penetrates the inner peripheral wall of the compression cavity and the outer peripheral wall of the cylinder part along the radial direction of the compression cavity. The second avoiding groove is located at one side of the cylinder part close to the body part along the axis direction of the pin hole, and the plurality of second groove bodies are respectively located at both ends of the first avoiding groove along the circumferential direction of the compression cavity and both ends of the second avoiding groove along the circumferential direction of the compression cavity. The second groove body penetrates the inner peripheral wall of the compression cavity and the outer peripheral wall of the cylinder part along the radial direction of the compression cavity. Along the central axis of the compression cavity, the length of the cylinder part is L1, the length of the sealing part is L2, and the length of the second groove body is L3, and L3 <= L1-L2-2*r, wherein r is the eccentric distance of the eccentric part. The application further relates to a compressor comprising any one of claims 1 to 10.

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