Compressor and refrigeration equipment

Abstract

The invention provides a compressor and refrigeration equipment. The compressor comprises a crankshaft, a piston and a slip sheet, the crankshaft comprises a body which comprises a main shaft, an auxiliary shaft and an eccentric part. The eccentric part is sleeved with the piston, and the piston can rotate relative to the body; the slip sheet is hinged with the piston; wherein at least part of the surface of the main shaft is provided with a first phosphate coating, and at least part of the surface of the first phosphate coating is provided with a first solid lubricant coating; a second phosphate coating is arranged on at least part of the surface of the auxiliary shaft, and a second solid lubricant coating is arranged on at least part of the surface of the second phosphate coating; a third phosphate coating is arranged on at least part of the surface of the eccentric part, and a third solid lubricant coating is arranged on at least part of the surface of the third phosphate coating; the thickness of the third solid lubricant coating is greater than that of the first solid lubricant coating; and / or the thickness of the third solid lubricant coating is greater than the thickness of the second solid lubricant coating. The operation efficiency of the compressor is improved, and vibration and noise of the compressor during working are reduced.

Description

Technical Field

[0001] The present invention relates to the technical field of refrigeration equipment, and in particular to a compressor and a refrigeration equipment. Background Art

[0002] At present, the compressor is provided with a crankshaft, a piston and a sliding vane. The piston is sleeved on the crankshaft. The crankshaft can drive the piston to move in the cylinder of the compressor. The piston abuts against the sliding vane to compress the refrigerant. In the related technology, in order to improve the working efficiency of the compressor, the sliding vane is hinged to the piston. However, the hinged connection between the piston and the sliding vane will cause eccentric wear of the crankshaft, thereby shortening the service life of the crankshaft. Summary of the invention

[0003] The present invention aims to solve at least one of the technical problems existing in the prior art or related art.

[0004] To this end, a first aspect of the present invention provides a compressor.

[0005] A second aspect of the present invention provides a refrigeration device.

[0006] In view of this, a first aspect of the present invention provides a compressor, including a crankshaft, a piston and a vane; the crankshaft includes a body, the body includes a main shaft, a secondary shaft and an eccentric portion; the piston is sleeved on the eccentric portion, and the piston can rotate relative to the body; the vane is hinged to the piston; wherein, at least a portion of the surface of the main shaft is arranged with a first phosphating layer, and at least a portion of the surface of the first phosphating layer is arranged with a first solid lubricant coating; at least a portion of the surface of the secondary shaft is arranged with a second phosphating layer, and at least a portion of the surface of the second phosphating layer is arranged with a second solid lubricant coating; at least a portion of the surface of the eccentric portion is arranged with a third phosphating layer, and at least a portion of the surface of the third phosphating layer is arranged with a third solid lubricant coating; the thickness of the third solid lubricant coating is greater than the thickness of the first solid lubricant coating; and / or the thickness of the third solid lubricant coating is greater than the thickness of the second solid lubricant coating.

[0007] The compressor provided in the present application includes a crankshaft, a piston and a vane, wherein the crankshaft includes a body; the body includes a main shaft, a secondary shaft and an eccentric part, the piston is sleeved on the eccentric part, and the body realizes the installation and positioning of the piston through the eccentric part, thereby improving the stability of the crankshaft during the operation of the compressor; the vane is hinged to the piston, and the piston can compress the refrigerant through the cooperation of the vane and the cylinder body of the compressor under the drive of the crankshaft. Since the vane is hinged to the piston, the compressor can have a higher compression efficiency. Specifically, when the materials and sizes of the crankshaft, piston and vane of the compressor are the same, the structure in which the vane is hinged to the piston can improve the working efficiency of the compressor by 1.5% compared with the structure in which the vane and the piston are abutted.

[0008] The crankshaft also includes a phosphating layer, which may include a first phosphating layer, a second phosphating layer and a third phosphating layer. The first phosphating layer is arranged on at least part of the surface of the main shaft, the second phosphating layer is arranged on at least part of the surface of the secondary shaft, and the third phosphating layer is arranged on at least part of the surface of the eccentric part. By phosphating the surface of the body, the surface of the body has higher wear resistance, thereby reducing the wear of the crankshaft during the operation of the compressor and improving the service life of the crankshaft.

[0009] The crankshaft also includes a solid lubricant coating, which includes a first solid lubricant coating, a second solid lubricant coating and a third solid lubricant coating. The first solid lubricant coating is arranged on the surface of at least part of the first phosphating layer, the second solid lubricant coating is arranged on the surface of at least part of the second phosphating layer, and the third solid lubricant coating is arranged on the surface of at least part of the third phosphating layer. During the operation of the compressor, the solid lubricant can improve the friction coefficient of the friction pair, reduce the friction force on the crankshaft, further reduce the wear on the crankshaft, and thus extend the service life of the crankshaft; especially for the crankshaft, by arranging the solid lubricant coating on at least part of the surface of the phosphating layer, the local wear of the crankshaft by the piston and the bearing can be reduced, thereby reducing the probability of eccentric wear of the crankshaft, further improving the matching accuracy of the crankshaft with the piston, the main bearing and the auxiliary bearing, thereby improving the operating efficiency of the compressor and reducing the vibration and noise of the compressor during operation.

[0010] In addition, the solid lubricant coating allows the lubricant to remain on the surface of the crankshaft for a longer period of time and is less likely to be lost due to factors such as temperature, thereby allowing the solid lubricant coating to cover the surface of the crankshaft for a longer period of time, thereby improving the lubrication effect of the solid lubricant coating on the crankshaft.

[0011] The combination of the phosphating layer and the solid lubricant coating can improve the wear resistance of the crankshaft surface and reduce the friction force on the crankshaft during rotation, thereby effectively reducing the wear on the crankshaft during the operation of the compressor, solving the problem of large local wear of the crankshaft, extending the service life of the crankshaft, and improving the stability of the compressor. In addition, since the wear of the crankshaft is reduced by the combination of the phosphating layer and the solid lubricant coating, the matching accuracy of the crankshaft with bearings, pistons and other components can also be improved, thereby avoiding the influence of the compressor efficiency on the compressor due to the reduction of the matching accuracy of the crankshaft with bearings, pistons and other components, so that the energy efficiency of the compressor can be maintained in a better range after a period of use, thereby improving the quality of the compressor. Since the wear of the crankshaft is reduced by the combination of the phosphating layer and the solid lubricant coating, and the matching accuracy of the crankshaft with bearings, pistons and other components is improved, the vibration and noise generated by the compressor during operation can also be reduced, thereby reducing the noise pollution of the compressor to the surrounding environment, and further improving the quality of the compressor.

[0012] The thickness of the third solid lubricant coating is greater than the thickness of the first solid lubricant coating, and / or the thickness of the third solid lubricant coating is greater than the thickness of the second solid lubricant coating, so that the eccentric part with worse working conditions has a thicker solid lubricant coating, thereby reducing the wear of the eccentric part and extending the service life of the eccentric part.

[0013] In addition, the compressor in the above technical solution provided by the present invention may also have the following additional technical features:

[0014] In some technical solutions of the present invention, optionally, the difference between the thickness of the third solid lubricant coating and the thickness of the first solid lubricant coating is greater than or equal to 1 micron and less than or equal to 10 microns; and / or the difference between the thickness of the third solid lubricant coating and the thickness of the second solid lubricant coating is greater than or equal to 1 micron and less than or equal to 10 microns.

[0015] In this technical solution, the difference between the thickness of the third solid lubricant coating and the thickness of the first solid lubricant coating is greater than or equal to 1 micron and less than or equal to 10 microns; and / or the difference between the thickness of the third solid lubricant coating and the thickness of the second solid lubricant coating is greater than or equal to 1 micron and less than or equal to 10 microns, so that the service life and protection effect of the solid lubricant coating at various positions of the crankshaft are more balanced.

[0016] In some technical solutions of the present invention, optionally, the piston is provided with a hinge hole, the slide is provided with a hinge shaft, and the hinge shaft is provided in the hinge hole; the minimum assembly clearance between the hinge shaft and the hinge hole is greater than or equal to 10 microns and less than or equal to 70 microns.

[0017] In this technical solution, the minimum assembly clearance between the articulated shaft and the articulated hole is greater than or equal to 10 microns and less than or equal to 70 microns. While improving the energy efficiency of the compressor through the articulated structure of the piston and the vane, it can also ensure that the solid lubricant coating has sufficient lubrication effect, reduce the wear of the eccentric part caused by the articulated structure of the piston and the vane, and further extend the service life of the crankshaft.

[0018] In some technical solutions of the present invention, optionally, the diameter of the hinge hole is less than or equal to 5 mm.

[0019] In this technical solution, the diameter of the hinge hole is less than or equal to 5 mm, which effectively ensures the rigidity of the piston and improves the stability of the piston and the slide during operation.

[0020] In some technical solutions of the present invention, optionally, the diameter of the hinge hole is less than 0.6 times the wall thickness of the piston.

[0021] In this technical solution, the diameter of the hinge hole is less than 0.6 times the wall thickness of the piston, which effectively ensures the rigidity of the piston and improves the stability of the piston and the sliding plate during operation.

[0022] In some technical solutions of the present invention, optionally, the solid lubricant coating includes resin and molybdenum disulfide particles, and the molybdenum disulfide particles are mixed with the resin.

[0023] In this technical solution, the solid lubricant coating includes resin and molybdenum disulfide particles. The molybdenum disulfide particles are mixed with the resin. While ensuring the lubricating effect of the solid lubricant coating on the crankshaft, the solid lubricant coating can be more stably adhered to the surface of the crankshaft, thereby extending the lubricating effect of the solid lubricant coating on the crankshaft.

[0024] In some technical solutions of the present invention, optionally, the solid lubricant coating includes resin and tungsten disulfide particles, and the tungsten disulfide particles are mixed with the resin.

[0025] In this technical solution, the solid lubricant coating includes resin and tungsten disulfide particles. The tungsten disulfide particles are mixed with the resin. While ensuring the lubricating effect of the solid lubricant coating on the crankshaft, the solid lubricant coating can be more stably adhered to the surface of the crankshaft, thereby extending the lubricating effect of the solid lubricant coating on the crankshaft.

[0026] In some technical solutions of the present invention, optionally, the outer diameter of the body is the first diameter; and the minimum thickness of the solid lubricant coating is greater than or equal to 0.00007 times the first diameter and less than or equal to 0.0004 times the first diameter.

[0027] In this technical solution, the minimum thickness of the solid lubricant coating is greater than or equal to 0.00007 times the first diameter, so that the solid lubricant can provide lubrication effect for the body more permanently. The minimum thickness of the solid lubricant coating is less than or equal to 0.0004 times the first diameter, so that the solid lubricant coating will not occupy too much space between the body and the bearing, the body and the piston, thereby avoiding excessive gaps between the body and the bearing, the body and the piston due to wear of the solid lubricant, and improving the matching accuracy between the body and the bearing, the body and the piston; the minimum thickness of the solid lubricant coating is less than or equal to 0.0004 times the first diameter, which can also avoid excessive adhesion of the solid lubricant coating due to excessive thickness, reduce the probability of the solid lubricant coating falling off, and improve the stability of the solid lubricant coating adhering to the body, thereby improving the lubrication effect of the solid lubricant coating on the crankshaft.

[0028] Specifically, the outer diameter of the body is the outer circumferential diameter of the body.

[0029] In some technical solutions of the present invention, optionally, the maximum thickness of the solid lubricant coating is greater than or equal to 0.0005 times the first diameter, and less than or equal to 0.0008 times the first diameter.

[0030] In this technical solution, the diameter of the body is the first diameter, and the maximum thickness of the solid lubricant coating is greater than or equal to 0.0005 times the first diameter, so that the solid lubricant can provide lubrication effect for the body more permanently. The maximum thickness of the solid lubricant coating is less than or equal to 0.0008 times the first diameter, so that the solid lubricant coating does not occupy too much space between the body and the bearing, and between the body and the piston, thereby avoiding excessive gaps between the body and the bearing, and between the body and the piston due to wear of the solid lubricant, and improving the matching accuracy between the body and the bearing, and between the body and the piston; and the maximum thickness of the solid lubricant coating is less than or equal to 0.0008 times the first diameter, which can also avoid excessive adhesion of the solid lubricant coating due to excessive thickness, reduce the probability of the solid lubricant coating falling off, and improve the stability of the solid lubricant coating attached to the body, thereby improving the lubrication effect of the solid lubricant coating on the crankshaft.

[0031] In some technical solutions of the present invention, optionally, the main body is made of medium carbon steel.

[0032] In this technical solution, the material of the body is medium carbon steel, which further improves the strength of the body. During the operation of the compressor, the body has higher strength, which can reduce the bending of the body due to centrifugal force, thereby reducing the deformation of the body, thereby reducing the local wear of the crankshaft, and extending the service life of the crankshaft. Since the bending of the body due to centrifugal force can be reduced, the friction force on the crankshaft can be reduced, thereby reducing the resistance when the crankshaft rotates, reducing the loss when the compressor is working, and improving the efficiency of the compressor.

[0033] In some technical solutions of the present invention, optionally, the main body is a steel body formed by high-temperature hot forging.

[0034] In this technical solution, the steel body is formed by high-temperature hot forging, which improves the density of the steel crankshaft and the grain size, so that the fiber streamlines inside the body are basically consistent with the outer shape, without distortion, interruption, or eddy current, thereby improving the rigidity of the body and reducing the risk of body deformation.

[0035] In some technical solutions of the present invention, optionally, the ratio of the outer diameter of the main shaft to the outer diameter of the secondary shaft is greater than or equal to 1.1 and less than or equal to 1.5.

[0036] In this technical solution, the ratio of the outer diameter of the main shaft to the outer diameter of the secondary shaft is between 1.1 and 1.5, so that the outer diameter of the main shaft is larger than the outer diameter of the secondary shaft, thereby improving the main strength, reducing the probability of bending of the main shaft during the operation of the compressor, further reducing the eccentric wear of the main shaft, and improving the stability of the crankshaft during the operation of the compressor.

[0037] Specifically, the ratio of the outer diameter of the main shaft to the outer diameter of the secondary shaft may be 1.1.

[0038] The ratio of the outer diameter of the main shaft to the outer diameter of the secondary shaft may be 1.2.

[0039] The ratio of the outer diameter of the main shaft to the outer diameter of the secondary shaft may be 1.3.

[0040] The ratio of the outer diameter of the main shaft to the outer diameter of the secondary shaft may be 1.4.

[0041] The ratio of the outer diameter of the main shaft to the outer diameter of the secondary shaft may be 1.5.

[0042] Specifically, the outer diameter of the main shaft is the outer diameter of the main shaft, and the outer diameter of the secondary shaft is the outer diameter of the secondary shaft.

[0043] In some technical solutions of the present invention, optionally, the ratio of the length of the vane in the radial direction of the crankshaft to the height of the vane in the axial direction of the crankshaft is greater than or equal to 1 and less than or equal to 1.5.

[0044] In this technical solution, the ratio of the length of the vane in the radial direction of the crankshaft to the height of the vane in the axial direction of the crankshaft is greater than or equal to 1 and less than or equal to 1.5, so that the vane can move more stably after being hinged to the piston, thereby improving the working efficiency of the compressor.

[0045] A second aspect of the present invention provides a refrigeration device, comprising a compressor as in any of the above technical solutions, so the refrigeration device has all the beneficial effects of the compressor as in any of the above technical solutions.

[0046] Specifically, the refrigeration equipment is an air conditioner, a refrigerator, a wine cabinet or a freezer.

[0047] Additional aspects and advantages of the present invention will be given in part in the following description and in part will be obvious from the following description, or will be learned through practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0048] The above and / or additional aspects and advantages of the present invention will become apparent and easily understood from the description of the embodiments in conjunction with the following drawings, in which:

[0049] Figure 1 A schematic diagram of the cooperation between a piston and a sliding plate according to an embodiment of the present invention;

[0050] Figure 2 is one of the structural schematic diagrams of a crankshaft according to an embodiment of the present invention;

[0051] Figure 3 A schematic diagram of a partial structure of a crankshaft according to an embodiment of the present invention;

[0052] Figure 4 The second structural schematic diagram of a crankshaft according to an embodiment of the present invention;

[0053] Figure 5 A schematic diagram of a local structure of a crankshaft in a microscopic state according to an embodiment of the present invention;

[0054] Figure 6 is a schematic structural diagram of a piston according to an embodiment of the present invention;

[0055] Figure 7 is a schematic structural diagram of a main bearing according to an embodiment of the present invention;

[0056] Figure 8 is a schematic structural diagram of a secondary bearing according to an embodiment of the present invention;

[0057] Fig. 9 is one of the structural schematic diagrams of a slide according to an embodiment of the present invention;

[0058] Fig.10 The second structural schematic diagram of a sliding piece according to an embodiment of the present invention;

[0059] Fig.11 Schematic diagram of the structure of a piston according to an embodiment of the present invention.

[0060] in, Figures 1 to 11 The corresponding relationship between the reference numerals and component names in the figure is:

[0061] 10 crankshaft, 100 body, 110 mounting surface, 112 first surface, 114 third surface, 116 fifth surface, 120 eccentric portion, 130 main shaft, 140 secondary shaft, 200 phosphate layer, 210 protrusion, 220 groove, 230 first phosphate layer, 240 second phosphate layer, 250 third phosphate layer, 300 solid lubricant coating, 310 first solid lubricant coating, 320 second solid lubricant coating, 330 third solid lubricant coating, 400 piston, 410 second surface, 420 hinge hole, 500 bearing, 510 main bearing, 512 fourth surface, 520 secondary bearing, 522 sixth surface, 600 slide, 610 hinge shaft. DETAILED DESCRIPTION

[0062] In order to more clearly understand the above-mentioned purpose, features and advantages of the present invention, the present invention is further described in detail below in conjunction with the accompanying drawings and specific embodiments. It should be noted that the embodiments of the present application and the features in the embodiments can be combined with each other without conflict.

[0063] In the following description, many specific details are set forth to facilitate a full understanding of the present invention. However, the present invention may also be implemented in other ways different from those described herein. Therefore, the protection scope of the present invention is not limited to the specific embodiments disclosed below.

[0064] Refer to the following Figures 1 to 11 A compressor and a refrigeration device according to some embodiments of the present invention are described.

[0065] In one embodiment of the present invention, Figure 1 , Figure 2 and Figure 3 As shown, a compressor is provided, including a crankshaft 10, a piston 400 and a vane 600; the crankshaft 10 includes a body 100, the body 100 includes a main shaft, a secondary shaft 140 and an eccentric portion 120; the piston 400 is sleeved on the eccentric portion 120, and the piston 400 can rotate relative to the body 100; the vane 600 is hinged to the piston 400; wherein, as Figure 1 and Figure 4 As shown, at least a portion of the surface of the main shaft 130 is arranged with a first phosphating layer 230, and at least a portion of the surface of the first phosphating layer 230 is arranged with a first solid lubricant coating 310; at least a portion of the surface of the secondary shaft 140 is arranged with a second phosphating layer 240, and at least a portion of the surface of the second phosphating layer 240 is arranged with a second solid lubricant coating 320; at least a portion of the surface of the eccentric portion 120 is arranged with a third phosphating layer 250, and at least a portion of the surface of the third phosphating layer 250 is arranged with a third solid lubricant coating 330; the thickness C3 of the third solid lubricant coating 330 is greater than the thickness C1 of the first solid lubricant coating 310; and / or the thickness C3 of the third solid lubricant coating 330 is greater than the thickness C2 of the second solid lubricant coating 320.

[0066] In this embodiment, the compressor includes a crankshaft 10, a piston 400 and a vane 600, the crankshaft 10 includes a body 100; the body 100 includes a main shaft, a secondary shaft 140 and an eccentric part 120, the piston 400 is sleeved on the eccentric part 120, the body 100 realizes the installation and positioning of the piston 400 through the eccentric part 120, and thus improves the stability of the crankshaft 10 during the operation of the compressor; the vane 600 is hinged with the piston 400, and the piston 400 can compress the refrigerant through the cooperation of the vane 600 and the cylinder body of the compressor under the drive of the crankshaft 10. Since the vane 600 is hinged with the piston 400, the compressor can have a higher compression efficiency. Specifically, when the materials and sizes of the crankshaft 10, the piston 400 and the vane 600 of the compressor are the same, the structure in which the vane 600 is hinged with the piston 400 can improve the working efficiency of the compressor by 1.5% compared with the structure in which the vane 600 abuts against the piston 400.

[0067] The crankshaft 10 also includes a phosphating layer 200, which may include a first phosphating layer 230, a second phosphating layer 240 and a third phosphating layer 250. The first phosphating layer 230 is arranged on at least part of the surface of the main shaft, the second phosphating layer 240 is arranged on at least part of the surface of the secondary shaft 140, and the third phosphating layer 250 is arranged on at least part of the surface of the eccentric portion 120. By phosphating the surface of the main body 100, the surface of the main body 100 has higher wear resistance, thereby reducing the wear of the crankshaft 10 during the operation of the compressor and improving the service life of the crankshaft 10.

[0068] The crankshaft 10 further includes a solid lubricant coating 300, which includes a first solid lubricant coating 310, a second solid lubricant coating 320 and a third solid lubricant coating 330. The first solid lubricant coating 310 is disposed on at least part of the surface of the first phosphating layer 230, the second solid lubricant coating 320 is disposed on at least part of the surface of the second phosphating layer 240, and the third solid lubricant coating 330 is disposed on at least part of the surface of the third phosphating layer 250. During the operation of the compressor, the solid lubricant can improve the friction coefficient of the friction pair. , reducing the friction force on the crankshaft 10, further reducing the wear on the crankshaft 10, and thus extending the service life of the crankshaft 10; especially for the crankshaft 10, by arranging the solid lubricant coating 300 on at least part of the surface of the phosphating layer 200, it is possible to reduce the local wear of the crankshaft 10 by the piston 400 and the bearing 500, thereby reducing the probability of eccentric wear of the crankshaft 10, and further improving the matching accuracy of the crankshaft 10 with the piston 400, the main bearing 510 and the secondary bearing 520, thereby improving the operating efficiency of the compressor and reducing the vibration and noise of the compressor during operation.

[0069] Furthermore, the solid lubricant coating 300 allows the lubricant to remain on the surface of the crankshaft 10 for a longer period of time and is less likely to be lost due to factors such as temperature, thereby allowing the solid lubricant coating 300 to cover the surface of the crankshaft 10 for a longer period of time, thereby improving the lubrication effect of the solid lubricant coating 300 on the crankshaft 10.

[0070] The phosphating layer 200 cooperates with the solid lubricant coating 300 to improve the wear resistance of the surface of the crankshaft 10, and can also reduce the friction force on the crankshaft 10 during the rotation process, thereby effectively reducing the wear on the crankshaft 10 during the operation of the compressor, solving the problem of large local wear of the crankshaft 10, extending the service life of the crankshaft 10, and improving the stability of the compressor. In addition, since the wear of the crankshaft 10 is reduced by the cooperation of the phosphating layer 200 and the solid lubricant coating 300, the matching accuracy of the crankshaft 10 and the bearing 500, the piston 400 and other components can also be improved, thereby avoiding the influence of the compressor efficiency on the compressor due to the reduction of the matching accuracy between the crankshaft 10 and the bearing 500, the piston 400 and other components, so that the energy efficiency of the compressor can be maintained in a better range after a period of use, thereby improving the quality of the compressor. Since the phosphating layer 200 and the solid lubricant coating 300 cooperate to reduce the wear of the crankshaft 10 and improve the matching accuracy between the crankshaft 10 and components such as the bearing 500 and the piston 400, it can also reduce the vibration and noise generated by the compressor during operation, thereby reducing the noise pollution of the compressor to the surrounding environment and further improving the quality of the compressor.

[0071] The thickness C3 of the third solid lubricant coating 330 is greater than the thickness C1 of the first solid lubricant coating 310, and / or the thickness C3 of the third solid lubricant coating 330 is greater than the thickness C2 of the second solid lubricant coating 320, so that the eccentric portion 120 with worse working conditions has a thicker solid lubricant coating 300, thereby reducing the wear at the eccentric portion 120 and extending the service life of the eccentric portion 120.

[0072] Furthermore, the compressor also includes a motor, a pump body, a closed casing and a liquid storage tank.

[0073] This embodiment provides a compressor. In addition to the technical features of the above embodiments, this embodiment further includes the following technical features.

[0074] like Figure 3 and Figure 4 As shown, the difference between the thickness C3 of the third solid lubricant coating 330 and the thickness C1 of the first solid lubricant coating 310 is greater than or equal to 1 micron and less than or equal to 10 microns; and / or the difference between the thickness C3 of the third solid lubricant coating 330 and the thickness C2 of the second solid lubricant coating 320 is greater than or equal to 1 micron and less than or equal to 10 microns.

[0075] In this technical solution, the difference between the thickness C3 of the third solid lubricant coating 330 and the thickness C1 of the first solid lubricant coating 310 is greater than or equal to 1 micron and less than or equal to 10 microns; and / or the difference between the thickness C3 of the third solid lubricant coating 330 and the thickness C2 of the second solid lubricant coating 320 is greater than or equal to 1 micron and less than or equal to 10 microns, so that the service life and protection effect of the solid lubricant coating 300 at various positions of the crankshaft 10 are more balanced.

[0076] Specifically, the difference between the thickness C3 of the third solid lubricant coating 330 and the thickness C1 of the first solid lubricant coating 310 is 1 μm, 2 μm, 3 μm, 4 μm, 5 μm, 6 μm, 7 μm, 8 μm, 9 μm or 10 μm.

[0077] The difference between the thickness C3 of the third solid lubricant coating 330 and the thickness C2 of the second solid lubricant coating 320 is 1 μm, 2 μm, 3 μm, 4 μm, 5 μm, 6 μm, 7 μm, 8 μm, 9 μm or 10 μm.

[0078] This embodiment provides a compressor. In addition to the technical features of the above embodiments, this embodiment further includes the following technical features.

[0079] like Figure 1 and Fig.11 As shown, the piston 400 is provided with a hinge hole 420, and the slide 600 is provided with a hinge shaft 610, and the hinge shaft 610 is arranged in the hinge hole 420; the minimum assembly gap E between the hinge shaft 610 and the hinge hole 420 is greater than or equal to 10 microns and less than or equal to 70 microns.

[0080] In this technical solution, the minimum assembly clearance E between the articulated shaft 610 and the articulated hole 420 is greater than or equal to 10 microns and less than or equal to 70 microns. While improving the energy efficiency of the compressor through the articulated structure of the piston 400 and the vane 600, it can also ensure that the solid lubricant coating 300 has sufficient lubrication effect, reduce the wear of the eccentric portion 120 caused by the articulated structure of the piston 400 and the vane 600, and further extend the service life of the crankshaft 10.

[0081] Specifically, the minimum assembly gap E between the hinge shaft 610 and the hinge hole 420 is 10 micrometers, 20 micrometers, 30 micrometers, 40 micrometers, 50 micrometers, 60 micrometers or 70 micrometers.

[0082] This embodiment provides a compressor, and in addition to the technical features of the above embodiment, this embodiment further includes the following technical features: The diameter of the hinge hole 420 is less than or equal to 5 mm.

[0083] In this technical solution, the diameter of the hinge hole 420 is less than or equal to 5 mm, which effectively ensures the rigidity of the piston 400 and improves the stability of the piston 400 and the slide 600 during operation.

[0084] Specifically, the diameters of the hinge holes 420 are 1 mm, 2 mm, 3 mm, 4 mm, and 5 mm.

[0085] This embodiment provides a compressor. In addition to the technical features of the above embodiments, this embodiment further includes the following technical features.

[0086] like Figure 1 and Fig.11 As shown, the diameter D4 of the hinge hole 420 is smaller than 0.6 times the wall thickness C4 of the piston 400 .

[0087] In this technical solution, the diameter D4 of the hinge hole 420 is less than 0.6 times the wall thickness C4 of the piston 400, which effectively ensures the rigidity of the piston 400 and improves the stability of the piston 400 and the slide 600 during operation.

[0088] Specifically, the diameter D4 of the hinge hole 420 is 0.1 times the wall thickness C4 of the piston 400 .

[0089] The diameter D4 of the hinge hole 420 is 0.2 times the wall thickness C4 of the piston 400 .

[0090] The diameter D4 of the hinge hole 420 is 0.3 times the wall thickness C4 of the piston 400 .

[0091] The diameter D4 of the hinge hole 420 is 0.4 times the wall thickness C4 of the piston 400 .

[0092] The diameter D4 of the hinge hole 420 is 0.5 times the wall thickness C4 of the piston 400 .

[0093] The diameter D4 of the hinge hole 420 is 0.6 times the wall thickness C4 of the piston 400 .

[0094] This embodiment provides a compressor. In addition to the technical features of the above embodiments, this embodiment further includes the following technical features.

[0095] The solid lubricant coating 300 includes a resin and molybdenum disulfide particles, and the molybdenum disulfide particles are mixed in the resin.

[0096] In this embodiment, the solid lubricant coating 300 includes resin and molybdenum disulfide particles, and the molybdenum disulfide particles are mixed in the resin. While ensuring the lubricating effect of the solid lubricant coating 300 on the crankshaft 10, the solid lubricant coating 300 can be more stably adhered to the surface of the crankshaft 10, thereby extending the lubricating effect of the solid lubricant coating 300 on the crankshaft 10.

[0097] This embodiment provides a compressor. In addition to the technical features of the above embodiments, this embodiment further includes the following technical features.

[0098] The solid lubricant coating 300 includes a resin and tungsten disulfide particles, and the tungsten disulfide particles are mixed in the resin.

[0099] In this embodiment, the solid lubricant coating 300 includes resin and tungsten disulfide particles, and the tungsten disulfide particles are mixed in the resin. While ensuring the lubricating effect of the solid lubricant coating 300 on the crankshaft 10, the solid lubricant coating 300 can be more stably adhered to the surface of the crankshaft 10, thereby extending the lubricating effect of the solid lubricant coating 300 on the crankshaft 10.

[0100] Specifically, the solid lubricant coating 300 obtained by mixing tungsten disulfide particles and / or molybdenum disulfide particles with resin can extend the life of the solid lubricant coating 300 by 1.5 times compared with the solid lubricant coating 300 using other resins as the base material.

[0101] Furthermore, the resin may be polyimide (PI).

[0102] The resin may also be polyamide-imide (PAI) or waterborne polyamide-imide (WPAI).

[0103] This embodiment provides a compressor. In addition to the technical features of the above embodiments, this embodiment further includes the following technical features.

[0104] like Figure 5 As shown, the phosphate layer 200 is provided with a plurality of grooves 220 recessed toward the body 100 .

[0105] In this embodiment, the phosphating layer 200 is provided with a plurality of grooves 220 sunken into the body 100, and the openings of the grooves 220 face the outside of the body 100, so that the surface of the phosphating layer 200 has a certain surface roughness. When the solid lubricant coating 300 is arranged on the phosphating layer 200, the surface of the phosphating layer 200 with a certain surface roughness enables the solid lubricant to have greater adhesion, so that the solid lubricant coating 300 can be more stably attached to the outer surface of the phosphating layer 200, thereby extending the service life of the solid lubricant coating 300.

[0106] This embodiment provides a compressor. In addition to the technical features of the above embodiments, this embodiment further includes the following technical features.

[0107] like Figure 5As shown, the phosphating layer 200 is provided with a plurality of protrusions 210 protruding toward the solid lubricant coating 300, so that the surface of the phosphating layer 200 has a certain surface roughness. When the solid lubricant coating 300 is arranged on the phosphating layer 200, the surface of the phosphating layer 200 with a certain surface roughness enables the solid lubricant to have greater adhesion, so that the solid lubricant coating 300 can be more stably attached to the outer surface of the phosphating layer 200, thereby extending the service life of the solid lubricant coating 300.

[0108] Specifically, the grooves 220 and / or protrusions 210 disposed on the surface of the phosphating layer 200 are microscopic grooves 220 and / or protrusions 210 and can be observed through a microscope.

[0109] This embodiment provides a compressor. In addition to the technical features of the above embodiments, this embodiment further includes the following technical features.

[0110] The surface roughness of the phosphating layer 200 is greater than or equal to Ra0.5 and less than or equal to Ra5.

[0111] In this embodiment, the surface roughness of the phosphating layer 200 is greater than or equal to Ra0.5, and the surface roughness of the phosphating layer 200 is less than or equal to Ra5, so that after the phosphating layer 200 is matched with the solid lubricant coating 300, the phosphating layer 200 will not be excessively worn due to the surface of the phosphating layer 200 being too rough, nor will the solid lubricant coating 300 fall off due to the surface of the phosphating layer 200 being too smooth, thereby improving the stability of the phosphating layer 200 and the solid lubricant coating 300 of the crankshaft 10 during the operation of the compressor.

[0112] Specifically, the surface roughness of the phosphating layer 200 is Ra0.5.

[0113] The surface roughness of the phosphating layer 200 is Ra0.8.

[0114] The surface roughness of the phosphating layer 200 is Ra1.6.

[0115] The surface roughness of the phosphating layer 200 is Ra3.2.

[0116] The surface roughness of the phosphating layer 200 is Ra5.

[0117] This embodiment provides a compressor. In addition to the technical features of the above embodiments, this embodiment further includes the following technical features.

[0118] The phosphating layer 200 is an iron phosphate film layer, a zinc phosphate film layer or a manganese phosphate film layer.

[0119] In this embodiment, the material of the phosphating layer 200 is iron phosphate, zinc phosphate or manganese phosphate, and the main body 100 and the components cooperating with the main body 100 are isolated by the iron phosphate film layer, the zinc phosphate film layer or the manganese phosphate film layer, so as to avoid the main body 100 and the components cooperating with the main body 100 from direct metal contact and adhesive wear, thereby further improving the stability of the crankshaft 10 during the operation of the compressor and extending the service life of the crankshaft 10.

[0120] This embodiment provides a compressor. In addition to the technical features of the above embodiments, this embodiment further includes the following technical features.

[0121] like Figure 3 As shown, the outer diameter of the body 100 is the first diameter D1; the minimum thickness H of the solid lubricant coating 300 is greater than or equal to 0.00007 times the first diameter D1, and less than or equal to 0.0004 times the first diameter D1.

[0122] In this embodiment, the minimum thickness H of the solid lubricant coating 300 is greater than or equal to 0.00007 times the first diameter D1 , so that the solid lubricant can provide lubrication effect for the body 100 more permanently. The minimum thickness H of the solid lubricant coating 300 is less than or equal to 0.0004 times the first diameter D1, so that the solid lubricant coating 300 does not occupy too much space between the body 100 and the bearing 500, and between the body 100 and the piston 400, thereby avoiding excessive gaps between the body 100 and the bearing 500, and between the body 100 and the piston 400 due to wear of the solid lubricant, thereby improving the matching accuracy between the body 100 and the bearing 500, and between the body 100 and the piston 400; the minimum thickness H of the solid lubricant coating 300 is less than or equal to 0.0004 times the first diameter D1, and it can also avoid that the thickness H of the solid lubricant coating 300 is too large, resulting in excessive adhesion of the solid lubricant coating 300, reduce the probability of the solid lubricant coating 300 falling off, improve the stability of the solid lubricant coating 300 adhering to the body 100, and thereby improve the lubrication effect of the solid lubricant coating 300 on the crankshaft 10.

[0123] Specifically, the outer diameter of the body 100 is the outer circumferential diameter of the body 100 .

[0124] Specifically, the minimum thickness H of the solid lubricant coating 300 may be 0.00007 times the first diameter D1.

[0125] The minimum thickness H of the solid lubricant coating 300 may be 0.0001 times the first diameter D1.

[0126] The minimum thickness H of the solid lubricant coating 300 may be 0.0002 times the first diameter D1.

[0127] The minimum thickness H of the solid lubricant coating 300 may be 0.0003 times the first diameter D1.

[0128] The minimum thickness H of the solid lubricant coating 300 may be 0.0004 times the first diameter D1.

[0129] Specifically, the first diameter D1 is the diameter of the crankshaft 10 corresponding to the position of the solid lubricant coating 300 .

[0130] The solid lubricant coating 300 is located on the eccentric portion 120 , and the first thickness H of the solid lubricant coating 300 on the eccentric portion 120 and the diameter of the eccentric portion 120 satisfy the following conditions: the minimum thickness H of the solid lubricant coating 300 is greater than or equal to 0.00007 times the first diameter D1 and less than or equal to 0.0004 times the first diameter D1.

[0131] The solid lubricant coating 300 is located on the spindle 130 , and the first thickness H of the solid lubricant coating 300 on the spindle 130 and the diameter of the spindle 130 satisfy the following conditions: the minimum thickness H of the solid lubricant coating 300 is greater than or equal to 0.00007 times the first diameter D1 and less than or equal to 0.0004 times the first diameter D1.

[0132] The solid lubricant coating 300 is located on the secondary shaft 140 , and the first thickness H of the solid lubricant coating 300 on the secondary shaft 140 and the diameter of the secondary shaft 140 satisfy the following conditions: the minimum thickness H of the solid lubricant coating 300 is greater than or equal to 0.00007 times the first diameter D1 and less than or equal to 0.0004 times the first diameter D1.

[0133] Specifically, the thickness H of the solid lubricant coating 300 at various positions has certain differences, and the minimum thickness H is the thickness H at the position where the thickness H of the solid lubricant coating 300 is the smallest.

[0134] This embodiment provides a compressor. In addition to the technical features of the above embodiments, this embodiment further includes the following technical features.

[0135] like Figure 3 As shown, the maximum thickness H of the solid lubricant coating 300 is greater than or equal to 0.0005 times the first diameter D1 and less than or equal to 0.0008 times the first diameter D1.

[0136] In this embodiment, the diameter of the body 100 is the first diameter D1 , and the maximum thickness H of the solid lubricant coating 300 is greater than or equal to 0.0005 times the first diameter D1 , so that the solid lubricant can provide lubrication effect for the body 100 more permanently. The maximum thickness H of the solid lubricant coating 300 is less than or equal to 0.0008 times the first diameter D1, so that the solid lubricant coating 300 does not occupy too much space between the body 100 and the bearing 500, and between the body 100 and the piston 400, thereby avoiding excessive gaps between the body 100 and the bearing 500, and between the body 100 and the piston 400 due to wear of the solid lubricant, thereby improving the matching accuracy between the body 100 and the bearing 500, and between the body 100 and the piston 400; and the maximum thickness H of the solid lubricant coating 300 is less than or equal to 0.0008 times the first diameter D1, which can also avoid excessive adhesion of the solid lubricant coating 300 due to excessive thickness H of the solid lubricant coating 300, reduce the probability of the solid lubricant coating 300 falling off, improve the stability of the solid lubricant coating 300 adhering to the body 100, and thereby improve the lubrication effect of the solid lubricant coating 300 on the crankshaft 10.

[0137] Specifically, the maximum thickness H of the solid lubricant coating 300 may be 0.0005 times the first diameter D1.

[0138] The maximum thickness H of the solid lubricant coating 300 may also be 0.0006 times the first diameter D1.

[0139] The maximum thickness H of the solid lubricant coating 300 may also be 0.0007 times the first diameter D1.

[0140] The maximum thickness H of the solid lubricant coating 300 may also be 0.0008 times the first diameter D1.

[0141] Specifically, the first diameter D1 is the diameter of the body 100 corresponding to the position of the solid lubricant coating 300 .

[0142] The solid lubricant coating 300 is located on the eccentric portion 120 , and the thickness H of the solid lubricant coating 300 on the eccentric portion 120 and the diameter of the eccentric portion 120 satisfy the following conditions: the maximum thickness H of the solid lubricant coating 300 is greater than or equal to 0.0005 times the first diameter D1 and less than or equal to 0.0008 times the first diameter D1.

[0143] The solid lubricant coating 300 is located on the spindle 130 , and the thickness H of the solid lubricant coating 300 on the spindle 130 and the diameter of the spindle 130 satisfy the following conditions: the maximum thickness H of the solid lubricant coating 300 is greater than or equal to 0.0005 times the first diameter D1 and less than or equal to 0.0008 times the first diameter D1.

[0144] The solid lubricant coating 300 is located on the secondary shaft 140 , and the thickness H of the solid lubricant coating 300 on the secondary shaft 140 and the diameter of the secondary shaft 140 satisfy the following conditions: the maximum thickness H of the solid lubricant coating 300 is greater than or equal to 0.0005 times the first diameter D1 and less than or equal to 0.0008 times the first diameter D1.

[0145] Specifically, the first diameter D1 may be the diameter of the main shaft 130 , and the first diameter D1 may also be the diameter of the secondary shaft 140 .

[0146] Specifically, the thickness H of the solid lubricant coating 300 at various positions has certain differences, and the maximum thickness H is the thickness H at the position where the thickness H of the solid lubricant coating 300 is the largest.

[0147] This embodiment provides a compressor. In addition to the technical features of the above embodiments, this embodiment further includes the following technical features.

[0148] The main body 100 is made of medium carbon steel.

[0149] In this embodiment, the body 100 is made of medium carbon steel, which further improves the strength of the body 100. During the operation of the compressor, the body 100 has a higher strength, which can reduce the bending of the body 100 due to centrifugal force, thereby reducing the deformation of the body 100, thereby reducing the local wear of the crankshaft 10, and extending the service life of the crankshaft 10. Since the bending of the body 100 due to centrifugal force can be reduced, the friction force on the crankshaft 10 can be reduced, thereby reducing the resistance when the crankshaft 10 rotates, reducing the loss when the compressor is working, and improving the efficiency of the compressor.

[0150] Compared with the body 100 made of ductile iron, the body 100 made of medium carbon steel has higher rigidity. When the power of the compressor remains unchanged, a body 100 with a smaller diameter can be used to achieve power transmission inside the compressor, thereby improving the energy efficiency of the compressor. In addition, the use of a body 100 with higher rigidity and a smaller diameter to achieve power transmission inside the compressor can also reduce the vibration of the compressor during operation, reduce the noise of the compressor during operation, and thus improve the quality of the compressor. The use of a body 100 with a smaller diameter to achieve power transmission inside the compressor can also break through the energy efficiency bottleneck caused by the excessively large diameter of the crankshaft 10, thereby further improving the energy efficiency of the compressor.

[0151] Specifically, compared with the crankshaft 10 made of ductile iron, the main body 100 made of medium carbon steel improves the rigidity of the compressor by 25% at the same shaft diameter, and reduces the noise of the compressor during operation by 3dBA to 4dBA.

[0152] Compared with the crankshaft 10 made of ductile iron, the main body 100 made of medium carbon steel has a smaller shaft diameter under the condition of equal rigidity, thereby improving the energy efficiency of the compressor by 2%.

[0153] Specifically, the crankshaft 10 may be made of medium carbon steel, with a carbon (C) content between 0.25% and 0.60%, and may also contain trace metal elements such as manganese (Mn), silicon (Si), phosphorus (P), sulfur (S), chromium (Cr), nickel (Ni), molybdenum (Mo), vanadium (V), and copper (Cu).

[0154] Specifically, the grade of the steel material used for the crankshaft 10 may be 45#, 40Cr or 20Cr.

[0155] This embodiment provides a compressor. In addition to the technical features of the above embodiments, this embodiment further includes the following technical features.

[0156] The body 100 is a steel body 100 formed by high temperature hot forging.

[0157] In this embodiment, the steel body 100 formed by high-temperature hot forging improves the density of the steel crankshaft 10 and improves the grain size, so that the fiber streamlines inside the body 100 are basically consistent with the outer shape without distortion, interruption, and eddy current, thereby improving the rigidity of the body 100 and reducing the risk of deformation of the body 100.

[0158] This embodiment provides a compressor. In addition to the technical features of the above embodiments, this embodiment further includes the following technical features.

[0159] like Figure 2 As shown, the body 100 includes an eccentric portion 120, a main shaft 130 and a secondary shaft 140; the piston 400 is sleeved on the eccentric portion 120; the main shaft 130 is connected to the eccentric portion 120 and is located at the axial direction ( Figure 2 The secondary shaft 140 is connected to the eccentric portion 120 and is located on the other side of the eccentric portion 120 in the axial direction; wherein the phosphating layer 200 is arranged on the surface of the eccentric portion 120, the surface of the secondary shaft 140 and the surface of the main shaft 130; and / or the solid lubricant coating 300 is arranged on the surface of the eccentric portion 120, the surface of the secondary shaft 140 and a part of the surface of the main shaft 130.

[0160] In this embodiment, the body 100 includes an eccentric portion 120, and the piston 400 of the compressor can be sleeved on the eccentric portion 120, and then the power generated by the motor is transmitted to the piston 400 through the crankshaft 10, thereby improving the stability of the compressor during operation. The body 100 also includes a main shaft 130 and a secondary shaft 140, and the main shaft 130 and the secondary shaft 140 are respectively located on both sides of the eccentric portion 120, and the main shaft 130 cooperates with the main bearing 510 of the compressor, and the secondary shaft 140 cooperates with the secondary bearing 520 of the compressor, thereby achieving support for the crankshaft 10, and further improving the stability of the compressor during operation.

[0161] The phosphating layer 200 is arranged on the surface of the eccentric part 120, the surface of the secondary shaft 140 and the surface of the main shaft 130. The phosphating layer 200 isolates the main shaft 130 from the main bearing 510, the secondary shaft 140 from the secondary bearing 520, and the eccentric part 120 from the piston 400, thereby avoiding direct metal contact between the main shaft 130 and the main bearing 510, the secondary shaft 140 and the secondary bearing 520, and the eccentric part 120 and the piston 400 to prevent adhesive wear from occurring, further improving the stability of the crankshaft 10 during the operation of the compressor and extending the service life of the crankshaft 10.

[0162] The solid lubricant coating 300 is arranged on the surface of the eccentric portion 120, the surface of the secondary shaft 140 and at least part of the surface of the main shaft 130. The solid lubricant can reduce the friction force on the surface of the eccentric portion 120, the surface of the secondary shaft 140 and at least part of the surface of the main shaft 130, further reduce the wear of the crankshaft 10, and thus extend the service life of the crankshaft 10. In particular, for the crankshaft 10 provided with the eccentric portion 120, by arranging the solid lubricant coating 300 on the surface of the eccentric portion 120, the surface of the secondary shaft 140 and at least part of the surface of the main shaft 130, the local wear of the crankshaft 10 by the piston 400, the main bearing 510 and the secondary bearing 520 can be reduced, thereby reducing the probability of eccentric wear of the crankshaft 10, further improving the matching accuracy of the crankshaft 10 with the piston 400, the main bearing 510 and the secondary bearing 520, thereby improving the operating efficiency of the compressor and reducing the vibration and noise of the compressor during operation.

[0163] Specifically, Figure 6 As shown, the mounting surface 110 includes a first surface 112 , which is a circumferential surface of the eccentric portion 120 , and the inner hole of the piston 400 has a second surface 410 , and the first surface 112 matches the second surface 410 .

[0164] like Figure 7 As shown, the mounting surface 110 includes a third surface 114 , which is a circumferential surface of the main shaft 130 , and the inner hole of the main bearing 510 has a fourth surface 512 , and the third surface 114 cooperates with the fourth surface 512 .

[0165] like Figure 8As shown, the mounting surface 110 includes a fifth surface 116 , which is a circumferential surface of the secondary shaft 140 . The inner hole of the secondary bearing 520 has a sixth surface 522 , and the fifth surface 116 matches the sixth surface 522 .

[0166] Specifically, the outer surface of the crankshaft 10 is entirely provided with a phosphate layer 200 , and the first surface 112 , the third surface 114 , and the fifth surface 116 are coated with a solid lubricant coating 300 .

[0167] The second surface 410 , the fourth surface 512 , and the sixth surface 522 are provided with a phosphate layer 200 and coated with a solid lubricant coating 300 .

[0168] This embodiment provides a compressor. In addition to the technical features of the above embodiments, this embodiment further includes the following technical features.

[0169] like Figure 2 As shown, the ratio of the outer diameter D2 of the main shaft 130 to the outer diameter D3 of the secondary shaft 140 is greater than or equal to 1.1 and less than or equal to 1.5.

[0170] In this embodiment, the ratio of the outer diameter D2 of the main shaft 130 to the outer diameter D3 of the secondary shaft 140 is between 1.1 and 1.5, so that the outer diameter D2 of the main shaft 130 is larger than the outer diameter D3 of the secondary shaft 140, thereby improving the main strength, reducing the probability of bending of the main shaft 130 during the operation of the compressor, further reducing the eccentric wear of the main shaft 130, and improving the stability of the crankshaft 10 during the operation of the compressor.

[0171] Specifically, the ratio of the outer diameter D2 of the main shaft 130 to the outer diameter D3 of the secondary shaft 140 may be 1.1.

[0172] The ratio of the outer diameter D2 of the main shaft 130 to the outer diameter D3 of the secondary shaft 140 may be 1.2.

[0173] The ratio of the outer diameter D2 of the main shaft 130 to the outer diameter D3 of the secondary shaft 140 may be 1.3.

[0174] The ratio of the outer diameter D2 of the main shaft 130 to the outer diameter D3 of the secondary shaft 140 may be 1.4.

[0175] The ratio of the outer diameter D2 of the main shaft 130 to the outer diameter D3 of the secondary shaft 140 may be 1.5.

[0176] Specifically, the outer diameter of the main shaft 130 is the outer circumferential diameter of the main shaft 130 , and the outer diameter of the auxiliary shaft 140 is the outer circumferential diameter of the auxiliary shaft 140 .

[0177] This embodiment provides a compressor. In addition to the technical features of the above embodiments, this embodiment further includes the following technical features.

[0178] like Fig. 9 and Fig.10 As shown, the vane 600 is in the radial direction of the crankshaft 10 ( Fig.10 The length L1 in the direction indicated by the arrow B in the middle) is the same as the axial direction of the sliding vane 600 in the crankshaft 10 ( Figure 2 and Fig.10 The ratio of the height L2 in the direction indicated by the arrow A is greater than or equal to 1 and less than or equal to 1.5.

[0179] In this embodiment, the ratio of the radial length L1 of the slide vane 600 in the crankshaft 10 to the axial height L2 of the slide vane 600 in the crankshaft 10 is greater than or equal to 1 and less than or equal to 1.5, so that the slide vane 600 can move more stably after being hinged to the piston 400, thereby improving the working efficiency of the compressor.

[0180] Specifically, a ratio of a length L1 of the sliding vane 600 in the radial direction of the crankshaft 10 to a height L2 of the sliding vane 600 in the axial direction of the crankshaft 10 may be 1.

[0181] A ratio of a length L1 of the vane 600 in the radial direction of the crankshaft 10 to a height L2 of the vane 600 in the axial direction of the crankshaft 10 may be 1.1.

[0182] A ratio of a length L1 of the vane 600 in the radial direction of the crankshaft 10 to a height L2 of the vane 600 in the axial direction of the crankshaft 10 may be 1.2.

[0183] A ratio of a length L1 of the vane 600 in the radial direction of the crankshaft 10 to a height L2 of the vane 600 in the axial direction of the crankshaft 10 may be 1.3.

[0184] A ratio of a length L1 of the vane 600 in the radial direction of the crankshaft 10 to a height L2 of the vane 600 in the axial direction of the crankshaft 10 may be 1.4.

[0185] A ratio of a length L1 of the vane 600 in the radial direction of the crankshaft 10 to a height L2 of the vane 600 in the axial direction of the crankshaft 10 may be 1.5.

[0186] In one embodiment of the present invention, a refrigeration device is provided, comprising a compressor as in any of the above embodiments, so the refrigeration device has all the beneficial effects of the compressor as in any of the above embodiments.

[0187] Specifically, the refrigeration equipment is an air conditioner, a refrigerator, a wine cabinet or a freezer.

[0188] In the claims, specification and drawings of the present invention, the term "multiple" refers to two or more than two. Unless otherwise clearly defined, the orientation or positional relationship indicated by the terms "upper" and "lower" is based on the orientation or positional relationship shown in the drawings, which is only for the purpose of more conveniently describing the present invention and making the description process simpler, rather than indicating or implying that the device or element referred to must have the specific orientation described, be constructed and operated in a specific orientation, so these descriptions cannot be understood as limiting the present invention; the terms "connect", "install", "fix" and the like should be understood in a broad sense. For example, "connection" can be a fixed connection between multiple objects, or a detachable connection between multiple objects, or an integral connection; it can be a direct connection between multiple objects, or an indirect connection between multiple objects through an intermediate medium. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood based on the specific circumstances of the above data.

[0189] In the claims, specification and drawings of the present invention, the description of the terms "one embodiment", "some embodiments", "specific embodiments" and the like means that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the present invention. In the claims, specification and drawings of the present invention, the schematic representations of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described may be combined in any one or more embodiments or examples in a suitable manner.

[0190] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. For those skilled in the art, the present invention may have various modifications and variations. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention shall be included in the protection scope of the present invention.

Claims

1. A compressor, characterized in that: include: A crankshaft, the crankshaft comprising a body, the body comprising a main shaft, a secondary shaft and an eccentric portion; A piston, wherein the piston is sleeved on the eccentric portion and can rotate relative to the body; a slide, the slide being hinged to the piston; Wherein, a first phosphating layer is arranged on at least part of the surface of the spindle, and a first solid lubricant coating is arranged on at least part of the surface of the first phosphating layer; A second phosphate layer is arranged on at least part of the surface of the secondary shaft, and a second solid lubricant coating is arranged on at least part of the surface of the second phosphate layer; A third phosphating layer is arranged on at least part of the surface of the eccentric portion, and a third solid lubricant coating is arranged on at least part of the surface of the third phosphating layer; The thickness of the third solid lubricant coating is greater than the thickness of the first solid lubricant coating; and / or The thickness of the third solid lubricant coating layer is greater than the thickness of the second solid lubricant coating layer.

2. The compressor according to claim 1, characterized in that The difference between the thickness of the third solid lubricant coating and the thickness of the first solid lubricant coating is greater than or equal to 1 micron and less than or equal to 10 microns; and / or A difference between a thickness of the third solid lubricant coating layer and a thickness of the second solid lubricant coating layer is greater than or equal to 1 micrometer and less than or equal to 10 micrometers.

3. The compressor according to claim 1, characterized in that The piston is provided with a hinge hole, the slide is provided with a hinge shaft, and the hinge shaft is arranged in the hinge hole; The minimum assembly clearance between the hinge shaft and the hinge hole is greater than or equal to 10 microns and less than or equal to 70 microns.

4. The compressor according to claim 3, characterized in that The diameter of the hinge hole is less than or equal to 5 mm.

5. The compressor according to claim 3, characterized in that The diameter of the hinge hole is less than 0.6 times the wall thickness of the piston.

6. The compressor according to claim 1, characterized in that The solid lubricant coating comprises a resin and molybdenum disulfide particles, wherein the molybdenum disulfide particles are mixed with the resin; or The solid lubricant coating includes a resin and tungsten disulfide particles, and the tungsten disulfide particles are mixed in the resin.

7. The compressor according to claim 1, characterized in that The outer diameter of the body is a first diameter; The minimum thickness of the solid lubricant coating is greater than or equal to 0.00007 times the first diameter and less than or equal to 0.0004 times the first diameter; and / or The maximum thickness of the solid lubricant coating is greater than or equal to 0.0005 times the first diameter and less than or equal to 0.0008 times the first diameter.

8. The compressor according to claim 1, characterized in that The main body is made of medium carbon steel.

9. The compressor according to claim 1, characterized in that The main body is a steel body formed by high temperature hot forging.

10. The compressor according to claim 1, characterized in that The ratio of the outer diameter of the main shaft to the outer diameter of the secondary shaft is greater than or equal to 1.1 and less than or equal to 1.

5.

11. The compressor according to any one of claims 1 to 10, characterized in that A ratio of a length of the sliding vane in a radial direction of the crankshaft to a height of the sliding vane in an axial direction of the crankshaft is greater than or equal to 1 and less than or equal to 1.

5.

12. A refrigeration device, characterized in that: Comprising the compressor according to any one of claims 1 to 11.

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