Crankshaft, pump body assembly, compressor and refrigeration equipment

Abstract

The utility model provides a crankshaft, pump body assembly, compressor and refrigeration equipment, crankshaft is used for the pump body assembly, the pump body assembly is provided with an accommodating cavity, the crankshaft comprises: a shaft body, the shaft body is provided with an oil supply channel; the eccentric part is arranged on the shaft body and located in the containing cavity, the eccentric part comprises a first eccentric section and a second eccentric section, the first eccentric section and the second eccentric section are arranged in the axial direction of the shaft body, and the diameter of the first eccentric section is smaller than that of the second eccentric section; the pressure relief hole is formed in at least one of the first eccentric section and the second eccentric section, the first end of the pressure relief hole communicates with the oil supply channel, and the second end of the pressure relief hole is used for communicating with the containing cavity. In other words, the containing cavity can be communicated with the oil supply channel through the pressure relief hole, so that due to friction heat generated by the eccentric part and the inner wall of the piston in the containing cavity, refrigerants escaping from the lubricating oil can leak into the oil supply channel through the pressure relief hole, pressure relief is completed, the refrigerants cannot leak into the compression cavity, and the efficiency of the compressor is improved advantageously.

Description

Technical Field

[0001] The utility model relates to the technical field of crankshaft structures, and in particular, to a crankshaft, a pump body assembly, a compressor, and a refrigeration device. Background Art

[0002] Currently, during the operation of a compressor in the related art, frictional heat is generated when a roller and a crankshaft rotate. The heat causes the refrigerant dissolved in the lubricating oil to escape, resulting in local high pressure in the area surrounded by the crankshaft, the roller, and the shaft sleeve. The escaped refrigerant leaks into the compression chamber, affecting the efficiency of the compressor. Summary of the Utility Model

[0003] An embodiment of the utility model aims to solve at least one of the technical problems existing in the prior art.

[0004] To this end, a first aspect of an embodiment of the utility model provides a crankshaft.

[0005] A second aspect of an embodiment of the utility model provides a pump body assembly.

[0006] A third aspect of an embodiment of the utility model provides a compressor.

[0007] A fourth aspect of an embodiment of the utility model provides a refrigeration device.

[0008] In view of this, according to the first aspect of an embodiment of the utility model, there is provided a crankshaft for a pump body assembly having a receiving cavity, the crankshaft including: a shaft body provided with an oil supply passage; an eccentric portion provided on the shaft body and located within the receiving cavity, the eccentric portion including a first eccentric section and a second eccentric section arranged along the axial direction of the shaft body, the diameter of the first eccentric section being smaller than that of the second eccentric section; a pressure relief hole provided on at least one of the first eccentric section and the second eccentric section, a first end of the pressure relief hole communicating with the oil supply passage, and a second end of the pressure relief hole for communicating with the receiving cavity.

[0009] The crankshaft provided by the embodiment of the utility model includes a shaft body, an eccentric portion, and a pressure relief hole. Specifically, the eccentric portion is provided on the shaft body. Optionally, the eccentric portion and the shaft body are of an integral structure, which is beneficial to improving the structural strength of the crankshaft.

[0010] It can be understood that the pump body assembly includes a cylinder, a first bearing, a second bearing, and a piston. The first bearing and the second bearing are respectively provided on both sides of the cylinder in the axial direction. The piston is provided within the cylinder. The outer wall of the piston and the inner wall of the cylinder form a compression chamber. The piston has a receiving cavity, and the cavity wall of the receiving cavity, that is, the inner wall of the piston, the first bearing, and the second bearing enclose a receiving cavity, and the eccentric portion is rotatably located within the receiving cavity.

[0011] The eccentric part includes a first eccentric section and a second eccentric section. Specifically, the first eccentric section and the second eccentric section are arranged along the axial direction of the shaft body. Among them, the diameter of the first eccentric section is smaller than that of the second eccentric section. That is to say, along the radial direction of the shaft body, the distance between the outer wall of the first eccentric section and the central axis of the shaft body is smaller than the distance between the outer wall of the second eccentric section and the central axis of the shaft body.

[0012] Specifically, during the operation of the compressor, the eccentric part rotates in the accommodating cavity to compress the refrigerant in the compression cavity. By making the diameter of the first eccentric section of the eccentric part smaller, it is beneficial to reduce the contact area between the eccentric part and the inner wall of the piston, reduce the friction between the eccentric part and the piston, and improve the reliability of the compressor.

[0013] Since the larger-diameter second eccentric section contacts the inner wall of the piston when the eccentric part rotates in the accommodating cavity, frictional heat will be generated, causing the refrigerant dissolved in the lubricating oil to escape, resulting in high pressure in the accommodating cavity, causing the refrigerant to leak into the compression cavity and reducing the efficiency of the compressor.

[0014] The pressure relief hole is provided on at least one of the first eccentric section and the second eccentric section. Specifically, the pressure relief hole is provided on the first eccentric section. Or, the pressure relief hole is provided on the second eccentric section. Or, the first eccentric section and the second eccentric section are respectively provided with pressure relief holes. It can be specifically set according to actual needs.

[0015] The first end of the pressure relief hole is communicated with the oil supply channel, and the second end of the pressure relief hole is communicated with the accommodating cavity. That is to say, the accommodating cavity can be communicated with the oil supply channel through the pressure relief hole, so that the refrigerant escaping from the lubricating oil due to the frictional heat generated by the eccentric part and the inner wall of the piston can leak into the oil supply channel through the pressure relief hole to complete pressure relief, and will not leak into the compression cavity, which is beneficial to improving the efficiency of the compressor and ensuring the reliability of the compressor.

[0016] Optionally, the oil supply channel penetrates the shaft body axially. That is to say, one end of the oil supply channel is communicated with the oil sump at the bottom of the compressor housing, and the other end of the oil supply channel is communicated with the inner cavity of the housing. That is, the refrigerant leaking into the oil supply channel flows to the inner cavity of the housing through the oil supply channel.

[0017] In addition, the crankshaft provided according to the above technical solution of the present invention further has the following additional technical features:

[0018] In some technical solutions, optionally, the first eccentric section includes a first shaft section and a second shaft section. Along the axial direction of the shaft body, the first shaft section and the second shaft section are respectively located on both sides of the second eccentric section; among them, when the pressure relief hole is provided on the first eccentric section, the pressure relief hole is provided on at least one of the first shaft section and the second shaft section.

[0019] In this technical solution, it is defined that the first eccentric section includes a first shaft section and a second shaft section. Specifically, along the axial direction of the shaft body, the first shaft section and the second shaft section are respectively located on both sides of the second eccentric section. That is to say, along the axial direction of the shaft body, the first shaft section, the second eccentric section, and the second shaft section are arranged in sequence.

[0020] Since the diameter of the first eccentric section is smaller than that of the second eccentric section, that is to say, the diameter of the first shaft section is smaller than that of the second eccentric section, and the diameter of the second shaft section is smaller than that of the second eccentric section.

[0021] The pressure relief hole is provided on the first shaft section. Or, the pressure relief hole is provided on the second shaft section. Or, pressure relief holes are respectively provided on the first shaft section and the second shaft section. Specifically, it can be set according to actual needs.

[0022] Since one end of the pressure relief hole is communicated with the oil supply channel, and the other end of the pressure relief hole is communicated with the accommodation cavity, the refrigerant escaping from the lubricating oil in the accommodation cavity can leak into the oil supply channel through the pressure relief hole to complete pressure relief, and will not leak into the compression cavity, which is beneficial to improving the efficiency of the compressor and ensuring the reliability of the compressor.

[0023] In addition, by setting the pressure relief hole on the first shaft section and / or the second shaft section, compared with setting the pressure relief hole on the second eccentric section, since the diameters of the first shaft section and the second shaft section are relatively small, there is a certain distance between the outer walls of the first shaft section and the second shaft section and the inner wall of the piston. Thus, it can ensure the effective communication between the pressure relief hole and the accommodation cavity. When local high pressure is generated in the accommodation cavity, the refrigerant can enter the oil supply channel through the pressure relief hole for rapid pressure relief, preventing the refrigerant in the accommodation cavity from leaking into the compression cavity and further improving the efficiency of the compressor.

[0024] In some technical solutions, optionally, when the pressure relief hole is provided on the first shaft section, between the diameter D of the pressure relief hole, the diameter Dp1 of the first shaft section, and the inner diameter Do of the oil supply channel, it satisfies 6 < (Dp1 - Do) / D < 15; and / or when the pressure relief hole is provided on the second shaft section, between the diameter D of the pressure relief hole, the diameter Dp2 of the second shaft section, and the inner diameter Do of the oil supply channel, it satisfies 6 < (Dp2 - Do) / D < 15.

[0025] In this technical solution, based on the pressure relief hole being provided on the first shaft section, between the diameter of the first shaft section, the diameter of the pressure relief hole, and the inner diameter of the oil supply channel, it satisfies 6 < (Dp1 - Do) / D < 15, that is, it defines the value range of the ratio of the drilling depth to the hole diameter, that is, the depth-diameter ratio, thus avoiding the problem of insignificant pressure relief effect due to too small a diameter of the pressure relief hole, ensuring effective pressure relief. At the same time, it is also convenient for machining, which is beneficial to improving the machining efficiency and reducing costs.

[0026] Based on the pressure relief hole being provided on the second shaft section, the relationship between the diameter of the second shaft section, the diameter of the pressure relief hole, and the inner diameter of the oil supply passage satisfies 6 < (Dp2 - Do) / D < 15. That is, the value range of the ratio of the drilling depth to the hole diameter is defined, which is also the depth-diameter ratio. This avoids the problem of ineffective pressure relief due to too small a diameter of the pressure relief hole, ensures effective pressure relief, and at the same time, is convenient for machining, which is beneficial to improving machining efficiency and reducing costs.

[0027] In some technical solutions, optionally, when the pressure relief hole is provided on the second eccentric section, between the diameter D of the pressure relief hole, the diameter Dp3 of the second eccentric section, and the inner diameter Do of the oil supply passage, it satisfies 6 <

[0028] (Dp3 - Do) / D < 15.

[0029] In this technical solution, based on the pressure relief hole being provided on the second eccentric section, the relationship between the diameter of the second eccentric section, the diameter of the pressure relief hole, and the inner diameter of the oil supply passage satisfies 6 < (Dp3 - Do) / D < 15. That is, the value range of the ratio of the drilling depth to the hole diameter is defined, which is also the depth-diameter ratio. This avoids the problem of ineffective pressure relief due to too small a diameter of the pressure relief hole, ensures effective pressure relief, and at the same time, is convenient for machining, which is beneficial to improving machining efficiency and reducing costs.

[0030] In some technical solutions, optionally, the first eccentric section has an outer peripheral surface, and at least a part of the outer peripheral surface extends along the axial direction of the shaft body. When the pressure relief hole is provided on the first eccentric section, the second end of the pressure relief hole is provided on the outer peripheral surface.

[0031] In this technical solution, it is defined that the first eccentric section has an outer peripheral surface. Optionally, the first eccentric section includes a first shaft section and a second shaft section. The first shaft section has a first outer peripheral surface, and the second shaft section has a second outer peripheral surface.

[0032] The second end of the pressure relief hole is provided on the outer peripheral surface. Since the diameters of the first shaft section and the second shaft section are relatively small, there is a certain distance between the outer walls of the first shaft section and the second shaft section and the inner wall of the piston. That is, there is a certain distance between the first outer peripheral surface and the second outer peripheral surface and the inner wall of the piston. Thus, it can ensure the effective connection between the pressure relief hole and the accommodation cavity. When local high pressure is generated in the accommodation cavity, the refrigerant can enter the oil supply passage through the pressure relief hole for rapid pressure relief.

[0033] In some technical solutions, optionally, the first eccentric section has a first end face, and at least a part of the first end face extends along the radial direction of the shaft body. When the pressure relief hole is provided on the first eccentric section, the second end of the pressure relief hole is provided on the first end face.

[0034] In this technical solution, it is defined that the first eccentric section further has a first end face. Optionally, the first eccentric section includes a first shaft section and a second shaft section. Among them, the end face of the first shaft section facing away from the second eccentric section is the upper end face, and the end face of the second shaft section facing away from the second eccentric section is the lower end face.

[0035] The second end of the pressure relief hole is provided on the first end face, that is, the second end of the pressure relief hole is provided on the upper end face or the lower end face. It can be understood that after the pump body assembly is completed, there is a gap between the first bearing located above and the upper end face of the first shaft section. At this time, the upper end face of the first shaft section is the first end face, and the second end of the pressure relief hole is provided on the first end face, which is beneficial to ensuring the effective communication between the pressure relief hole and the accommodation cavity.

[0036] Or, there is a gap between the second bearing located below and the lower end face of the second shaft section. At this time, the lower end face of the second shaft section is the first end face, and the second end of the pressure relief hole is provided on the first end face, which is beneficial to ensuring the effective communication between the pressure relief hole and the accommodation cavity.

[0037] In some technical solutions, optionally, the second eccentric section has a second end face, and at least a part of the second end face extends along the radial direction of the shaft body. In the case where the pressure relief hole is provided in the second eccentric section, the second end of the pressure relief hole is provided on the second end face.

[0038] In this technical solution, it is defined that the second eccentric section has a second end face. Optionally, along the axial direction of the shaft body, the second eccentric section includes an upper end face and a lower end face. That is to say, the second end face is the upper end face of the second eccentric section or the lower end face of the second eccentric section. That is, the second end of the pressure relief hole is provided on the upper end face or the lower end face of the second eccentric section.

[0039] It can be understood that the upper end face or the lower end face of the second eccentric section is located in the accommodation cavity, and the second end of the pressure relief hole is provided on the upper end face or the lower end face of the second eccentric section, which is beneficial to ensuring the effective communication between the pressure relief hole and the accommodation cavity.

[0040] In some technical solutions, optionally, the pressure relief hole extends along the radial direction of the shaft body.

[0041] In this technical solution, it is defined that the pressure relief hole extends along the radial direction of the shaft body. That is to say, the pressure relief hole is a radial hole. Thus, when a local high pressure is generated in the accommodation cavity, the refrigerant can enter the oil supply channel through the pressure relief hole for rapid pressure relief, preventing the refrigerant in the accommodation cavity from leaking into the compression cavity, and at the same time, it is beneficial to reducing the processing difficulty of the pressure relief hole, and further beneficial to reducing the production cost of the crankshaft.

[0042] In some technical solutions, optionally, the aperture D of the pressure relief hole satisfies D≥1mm.

[0043] In this technical solution, it is defined that the aperture of the pressure relief hole is greater than or equal to 1 mm. Thus, when a local high pressure is generated in the accommodation cavity, the refrigerant enters the oil supply channel through the pressure relief hole for effective pressure relief, preventing the refrigerant in the accommodation cavity from leaking into the compression cavity. Meanwhile, it is beneficial to reduce the processing difficulty of the pressure relief hole, and further beneficial to reduce the production cost of the crankshaft.

[0044] In some technical solutions, optionally, the crankshaft further includes an oil supply hole, which is provided on the second eccentric section. One end of the oil supply hole communicates with the oil supply channel, and the other end of the oil supply hole penetrates through the outer wall of the second eccentric section.

[0045] In this technical solution, it is defined that the crankshaft further includes an oil supply hole. Specifically, the oil supply hole is provided on the second eccentric section, and one end of the oil supply hole communicates with the oil supply channel, while the other end penetrates through the outer wall of the second eccentric section, thereby supplying oil to the part where the second eccentric section contacts the inner wall of the piston, and improving the reliability of the compressor.

[0046] According to the second aspect of the present utility model, there is provided a pump body assembly, including the crankshaft provided in any of the above technical solutions, and thus having all the beneficial technical effects of this crankshaft, which will not be elaborated herein.

[0047] Furthermore, the pump body assembly further includes a cylinder, a first bearing, a second bearing, a piston and a sliding vane. Among them, along the axial direction of the shaft body, the first bearing and the second bearing are respectively provided on both sides of the cylinder; the piston is provided in the cylinder, the piston is provided with an accommodation cavity, and a part of the cavity wall of the accommodation cavity, the first bearing and the second bearing enclose to form an accommodation cavity, and the eccentric part is located in the accommodation cavity; the sliding vane is provided in the cylinder and abuts against the outer wall of the piston.

[0048] The pump body assembly provided by the embodiment of the present utility model includes a cylinder, a first bearing, a second bearing, a piston, a sliding vane and a crankshaft. Specifically, the first bearing and the second bearing are respectively provided on both sides in the axial direction of the cylinder, the piston is provided in the cylinder, the outer wall of the piston and the inner wall of the cylinder form a compression cavity, the piston has an accommodation cavity, and the cavity wall of the accommodation cavity, that is, the inner wall of the piston, the first bearing and the second bearing enclose to form an accommodation cavity, and the eccentric part is rotatably located in the accommodation cavity.

[0049] The eccentric part includes a first eccentric section and a second eccentric section. Specifically, the first eccentric section and the second eccentric section are arranged along the axial direction of the shaft body. Among them, the diameter of the first eccentric section is smaller than that of the second eccentric section. That is to say, along the radial direction of the shaft body, the distance between the outer wall of the first eccentric section and the central axis of the shaft body is smaller than the distance between the outer wall of the second eccentric section and the central axis of the shaft body.

[0050] Specifically, during the operation of the compressor, the eccentric part rotates within the accommodating cavity to compress the refrigerant in the compression cavity. By making the diameter of the first eccentric section of the eccentric part smaller, it is beneficial to reduce the contact area between the eccentric part and the inner wall of the piston, reduce the friction between the eccentric part and the piston, and improve the reliability of the compressor.

[0051] When the eccentric part rotates within the accommodating cavity, the second eccentric section with a larger diameter contacts the inner wall of the piston. Therefore, frictional heat is generated, causing the refrigerant dissolved in the lubricating oil to escape, resulting in high pressure in the accommodating cavity, causing the refrigerant to leak into the compression cavity and reducing the efficiency of the compressor.

[0052] The pressure relief hole is provided on at least one of the first eccentric section and the second eccentric section. Specifically, the pressure relief hole is provided on the first eccentric section. Alternatively, the pressure relief hole is provided on the second eccentric section. Or, the first eccentric section and the second eccentric section are respectively provided with pressure relief holes. It can be specifically set according to actual needs.

[0053] The first end of the pressure relief hole is communicated with the oil supply channel, and the second end of the pressure relief hole is communicated with the accommodating cavity. That is to say, the accommodating cavity can be communicated with the oil supply channel through the pressure relief hole, so that the refrigerant escaping from the lubricating oil can leak into the oil supply channel through the pressure relief hole to complete pressure relief, and will not leak into the compression cavity, which is beneficial to improving the efficiency of the compressor and ensuring the reliability of the compressor.

[0054] According to the third aspect of the present invention, a compressor is provided, including the crankshaft or the pump body assembly provided in any of the above technical solutions, and thus has all the beneficial technical effects of the crankshaft or the pump body assembly, which will not be elaborated here.

[0055] According to the fourth aspect of the present invention, a refrigeration device is provided, including the crankshaft or the pump body assembly or the compressor provided in any of the above technical solutions, and thus has all the beneficial technical effects of the crankshaft or the pump body assembly or the compressor, which will not be elaborated here.

[0056] The additional aspects and advantages of the present invention will be given in the following description part, some of which will become obvious from the following description, or will be understood through the practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0057] The above and / or additional aspects and advantages of the present invention will become obvious and easy to understand from the description of the embodiments in conjunction with the following drawings, wherein:

[0058] Figure 1 FIG. 1 shows a schematic structural diagram of a crankshaft according to an embodiment of the present invention;

[0059] Figure 2 FIG. 2 shows a schematic structural diagram of a crankshaft according to an embodiment of the present invention;

[0060] Figure 3 Shows the third schematic structural diagram of the crankshaft according to an embodiment of the present invention;

[0061] Figure 4 Shows the fourth schematic structural diagram of the crankshaft according to an embodiment of the present invention;

[0062] Figure 5 Shows the fifth schematic structural diagram of the crankshaft according to an embodiment of the present invention;

[0063] Figure 6 Shows the schematic structural diagram of the pump body assembly according to an embodiment of the present invention.

[0064] Among them, Figures 1 to 6 The corresponding relationship between the reference numerals and the component names in the figure is as follows:

[0065] 100 crankshaft, 110 shaft body, 111 oil supply channel, 120 eccentric part, 121 first eccentric section, 122 second eccentric section, 123 first shaft section, 124 second shaft section, 125 outer peripheral surface, 126 first end face, 127 second end face, 130 pressure relief hole, 140 oil supply hole, 200 pump body assembly, 210 cylinder, 220 first bearing, 230 second bearing, 240 piston, 241 accommodation cavity, 250 sliding vane, 260 accommodation cavity. Detailed implementation manners

[0066] In order to more clearly understand the above objects, features and advantages of the present invention, the present invention will be further described in detail below with reference to the drawings and specific implementation manners. It should be noted that, without conflict, the embodiments of the present application and the features in the embodiments can be combined with each other.

[0067] In the following description, many specific details are set forth in order to fully understand the present invention. However, the present invention can also be implemented in other ways different from those described herein. Therefore, the protection scope of the present invention is not limited by the specific embodiments disclosed below.

[0068] The following will refer to Figures 1 to 6 to describe the crankshaft 100, pump body assembly 200, compressor and refrigeration equipment provided according to some embodiments of the present invention.

[0069] In an embodiment according to the present application, as Figure 1 , Figure 2 , Figure 3 , Figure 4 , Figure 5 and Figure 6As shown, a crankshaft 100 is proposed. The crankshaft 100 is used for a pump body assembly 200 which has a receiving cavity 260. The crankshaft 100 includes: a shaft body 110 provided with an oil supply passage 111; an eccentric portion 120 provided on the shaft body 110 and located within the receiving cavity 260. The eccentric portion 120 includes a first eccentric section 121 and a second eccentric section 122. The first eccentric section 121 and the second eccentric section 122 are arranged along the axial direction of the shaft body 110, and the diameter of the first eccentric section 121 is smaller than that of the second eccentric section 122; a pressure relief hole 130 provided on at least one of the first eccentric section 121 and the second eccentric section 122. The first end of the pressure relief hole 130 is communicated with the oil supply passage 111, and the second end of the pressure relief hole 130 is used for communicating with the receiving cavity 260.

[0070] The crankshaft 100 provided by the embodiment of the present utility model includes a shaft body 110, an eccentric portion 120 and a pressure relief hole 130. Specifically, the eccentric portion 120 is provided on the shaft body 110. Optionally, the eccentric portion 120 and the shaft body 110 are of an integral structure, which is beneficial to improving the structural strength of the crankshaft 100.

[0071] It can be understood that the pump body assembly 200 includes a cylinder 210, a first bearing 220, a second bearing 230 and a piston 240. The first bearing 220 and the second bearing 230 are respectively arranged on both sides of the cylinder 210 in the axial direction. The piston 240 is arranged within the cylinder 210. A compression cavity is formed between the outer wall of the piston 240 and the inner wall of the cylinder 210. The piston 240 has a receiving cavity 241. The cavity wall of the receiving cavity 241, that is, the inner wall of the piston 240, the first bearing 220 and the second bearing 230 enclose to form the receiving cavity 260, and the eccentric portion 120 is rotatably located within the receiving cavity 260.

[0072] The eccentric portion 120 includes a first eccentric section 121 and a second eccentric section 122. Specifically, the first eccentric section 121 and the second eccentric section 122 are arranged along the axial direction of the shaft body 110. Among them, the diameter of the first eccentric section 121 is smaller than that of the second eccentric section 122. That is to say, along the radial direction of the shaft body 110, the distance between the outer wall of the first eccentric section 121 and the central axis of the shaft body 110 is smaller than the distance between the outer wall of the second eccentric section 122 and the central axis of the shaft body 110.

[0073] Specifically, during the operation of the compressor, the eccentric portion 120 rotates within the receiving cavity 260 to compress the refrigerant within the compression cavity. By making the diameter of the first eccentric section 121 of the eccentric portion 120 smaller, it is beneficial to reduce the contact area between the eccentric portion 120 and the inner wall of the piston 240, reduce the friction between the eccentric portion 120 and the piston 240, and improve the reliability of the compressor.

[0074] When the eccentric part 120 rotates in the accommodation cavity 260, the second eccentric section 122 with a larger diameter contacts the inner wall of the piston 240. Therefore, frictional heat is generated, causing the refrigerant dissolved in the lubricating oil to escape, resulting in high pressure in the accommodation cavity 260, causing the refrigerant to leak into the compression cavity and reducing the efficiency of the compressor.

[0075] The pressure relief hole 130 is provided on at least one of the first eccentric section 121 and the second eccentric section 122. Specifically, the pressure relief hole 130 is provided on the first eccentric section 121. Alternatively, the pressure relief hole 130 is provided on the second eccentric section 122. Alternatively, the first eccentric section 121 and the second eccentric section 122 are respectively provided with the pressure relief hole 130. It can be specifically set according to actual needs.

[0076] The first end of the pressure relief hole 130 is communicated with the oil supply channel 111, and the second end of the pressure relief hole 130 is communicated with the accommodation cavity 260. That is to say, the accommodation cavity 260 can be communicated with the oil supply channel 111 through the pressure relief hole 130, so that the refrigerant escaping from the lubricating oil due to the frictional heat generated by the eccentric part 120 and the inner wall of the piston 240 can leak into the oil supply channel 111 through the pressure relief hole 130 to complete pressure relief, and will not leak into the compression cavity, which is beneficial to improving the efficiency of the compressor and ensuring the reliability of the compressor.

[0077] Optionally, the oil supply channel 111 penetrates the shaft body 110 axially. That is to say, one end of the oil supply channel 111 is communicated with the oil sump at the bottom of the compressor housing, and the other end of the oil supply channel 111 is communicated with the inner cavity of the housing. That is, the refrigerant leaking into the oil supply channel 111 flows into the inner cavity of the housing through the oil supply channel 111.

[0078] As Figure 1 、 Figure 2 、 Figure 3 、 Figure 4 、 Figure 5 and Figure 6 shown, in some embodiments, optionally, the first eccentric section 121 includes a first shaft section 123 and a second shaft section 124. Along the axial direction of the shaft body 110, the first shaft section 123 and the second shaft section 124 are respectively located on both sides of the second eccentric section 122; wherein, when the pressure relief hole 130 is provided on the first eccentric section 121, the pressure relief hole 130 is provided on at least one of the first shaft section 123 and the second shaft section 124.

[0079] In this embodiment, it is defined that the first eccentric section 121 includes a first shaft section 123 and a second shaft section 124. Specifically, along the axial direction of the shaft body 110, the first shaft section 123 and the second shaft section 124 are respectively located on both sides of the second eccentric section 122. That is to say, along the axial direction of the shaft body 110, the first shaft section 123, the second eccentric section 122, and the second shaft section 124 are arranged in sequence.

[0080] Since the diameter of the first eccentric section 121 is smaller than that of the second eccentric section 122, that is to say, the diameter of the first shaft section 123 is smaller than that of the second eccentric section 122, and the diameter of the second shaft section 124 is smaller than that of the second eccentric section 122.

[0081] The pressure relief hole 130 is provided on the first shaft section 123. Alternatively, the pressure relief hole 130 is provided on the second shaft section 124. Alternatively, pressure relief holes 130 are respectively provided on the first shaft section 123 and the second shaft section 124. Specifically, it can be set according to actual needs.

[0082] Since one end of the pressure relief hole 130 is communicated with the oil supply passage 111, and the other end of the pressure relief hole 130 is communicated with the accommodation cavity 260, the refrigerant escaping from the lubricating oil in the accommodation cavity 260 can leak into the oil supply passage 111 through the pressure relief hole 130 to complete pressure relief, and will not leak into the compression cavity, which is beneficial to improving the efficiency of the compressor and ensuring the reliability of the compressor.

[0083] In addition, setting the pressure relief hole 130 on the first shaft section 123 and / or the second shaft section 124, compared with setting the pressure relief hole 130 on the second eccentric section 122, since the diameters of the first shaft section 123 and the second shaft section 124 are relatively small, therefore, there is a certain distance between the outer walls of the first shaft section 123 and the second shaft section 124 and the inner wall of the piston 240, so as to ensure the effective communication between the pressure relief hole 130 and the accommodation cavity 260. When local high pressure is generated in the accommodation cavity 260, the refrigerant can enter the oil supply passage 111 through the pressure relief hole 130 for rapid pressure relief, preventing the refrigerant in the accommodation cavity 260 from leaking into the compression cavity and further improving the efficiency of the compressor.

[0084] As Figure 3 shown, in some embodiments, optionally, when the pressure relief hole 130 is provided on the first shaft section 123, between the aperture D of the pressure relief hole 130, the diameter Dp1 of the first shaft section 123, and the inner diameter Do of the oil supply passage 111, it satisfies 6 < (Dp1 - Do) / D < 15; and / or when the pressure relief hole 130 is provided on the second shaft section 124, between the aperture D of the pressure relief hole 130, the diameter Dp2 of the second shaft section 124, and the inner diameter Do of the oil supply passage 111, it satisfies 6 < (Dp2 - Do) / D < 15.

[0085] In this embodiment, based on the pressure relief hole 130 being provided on the first shaft section 123, the diameter of the first shaft section 123, the diameter of the pressure relief hole 130, and the inner diameter of the oil supply passage 111 satisfy 6 < (Dp1 - Do) / D < 15, that is, the value range of the ratio of the drilling depth to the hole diameter is defined, which is also the depth-diameter ratio. Thus, the problem of insignificant pressure relief effect due to too small a diameter of the pressure relief hole 130 is avoided, ensuring effective pressure relief. At the same time, it is also convenient for machining, which is beneficial to improving machining efficiency and reducing costs.

[0086] Based on the pressure relief hole 130 being provided on the second shaft section 124, the diameter of the second shaft section 124, the diameter of the pressure relief hole 130, and the inner diameter of the oil supply passage 111 satisfy 6 < (Dp2 - Do) / D < 15, that is, the value range of the ratio of the drilling depth to the hole diameter is defined, which is also the depth-diameter ratio. Thus, the problem of insignificant pressure relief effect due to too small a diameter of the pressure relief hole 130 is avoided, ensuring effective pressure relief. At the same time, it is also convenient for machining, which is beneficial to improving machining efficiency and reducing costs.

[0087] As Figure 3 shown, in some embodiments, optionally, when the pressure relief hole 130 is provided in the second eccentric section 122, between the diameter D of the pressure relief hole 130, the diameter Dp3 of the second eccentric section 122, and the inner diameter Do of the oil supply passage 111, 6 < (Dp3 - Do) / D < 15 is satisfied.

[0088] In this embodiment, based on the pressure relief hole 130 being provided on the second eccentric section 122, the diameter of the second eccentric section 122, the diameter of the pressure relief hole 130, and the inner diameter of the oil supply passage 111 satisfy 6 < (Dp3 - Do) / D < 15, that is, the value range of the ratio of the drilling depth to the hole diameter is defined, which is also the depth-diameter ratio. Thus, the problem of insignificant pressure relief effect due to too small a diameter of the pressure relief hole 130 is avoided, ensuring effective pressure relief. At the same time, it is also convenient for machining, which is beneficial to improving machining efficiency and reducing costs.

[0089] As Figure 1 、 Figure 2 、 Figure 3 、 Figure 4 、 Figure 5 and Figure 6 shown, in some embodiments, optionally, the first eccentric section 121 has an outer peripheral surface 125, at least a part of the outer peripheral surface 125 extends along the axial direction of the shaft body 110, and when the pressure relief hole 130 is provided in the first eccentric section 121, the second end of the pressure relief hole 130 is provided on the outer peripheral surface 125.

[0090] In this embodiment, it is defined that the first eccentric section 121 has an outer peripheral surface 125. Optionally, the first eccentric section 121 includes a first shaft section 123 and a second shaft section 124, the first shaft section 123 has a first outer peripheral surface, and the second shaft section 124 has a second outer peripheral surface.

[0091] The second end of the pressure relief hole 130 is disposed on the outer peripheral surface 125. Since the diameters of the first shaft segment 123 and the second shaft segment 124 are relatively small, there is a certain distance between the outer walls of the first shaft segment 123 and the second shaft segment 124 and the inner wall of the piston 240. That is, there is a certain distance between the first outer peripheral surface and the second outer peripheral surface and the inner wall of the piston 240, so as to ensure the effective communication between the pressure relief hole 130 and the accommodating cavity 260. When local high pressure is generated in the accommodating cavity 260, the refrigerant can enter the oil supply passage 111 through the pressure relief hole 130 for rapid pressure relief.

[0092] Such as Figure 1 and Figure 2 As shown, in some embodiments, optionally, the first eccentric segment 121 has a first end face 126, and at least a part of the first end face 126 extends along the radial direction of the shaft body 110. When the pressure relief hole 130 is disposed on the first eccentric segment 121, the second end of the pressure relief hole 130 is disposed on the first end face 126.

[0093] In this embodiment, it is defined that the first eccentric segment 121 further has a first end face 126. Optionally, the first eccentric segment 121 includes a first shaft segment 123 and a second shaft segment 124. Among them, the end face of the first shaft segment 123 facing away from the second eccentric segment 122 is the upper end face, and the end face of the second shaft segment 124 facing away from the second eccentric segment 122 is the lower end face.

[0094] The second end of the pressure relief hole 130 is disposed on the first end face 126, that is, the second end of the pressure relief hole 130 is disposed on the upper end face or the lower end face. It can be understood that after the pump body assembly 200 is assembled, there is a gap between the first bearing 220 located above and the upper end face of the first shaft segment 123. At this time, the upper end face of the first shaft segment 123 is the first end face 126, and the second end of the pressure relief hole 130 is disposed on the first end face 126, which is beneficial to ensuring the effective communication between the pressure relief hole 130 and the accommodating cavity 260.

[0095] Or, there is a gap between the second bearing 230 located below and the lower end face of the second shaft segment 124. At this time, the lower end face of the second shaft segment 124 is the first end face 126, and the second end of the pressure relief hole 130 is disposed on the first end face 126, which is beneficial to ensuring the effective communication between the pressure relief hole 130 and the accommodating cavity 260.

[0096] Such as Figure 1 As shown, in some embodiments, optionally, the second eccentric segment 122 has a second end face 127, and at least a part of the second end face 127 extends along the radial direction of the shaft body 110. When the pressure relief hole 130 is disposed on the second eccentric segment 122, the second end of the pressure relief hole 130 is disposed on the second end face 127.

[0097] In this embodiment, it is defined that the second eccentric section 122 has a second end face 127. Optionally, along the axial direction of the shaft body 110, the second eccentric section 122 includes an upper end face and a lower end face. That is to say, the second end face 127 is the upper end face or the lower end face of the second eccentric section 122. Namely, the second end of the pressure relief hole 130 is provided on the upper end face or the lower end face of the second eccentric section 122.

[0098] It can be understood that the upper end face or the lower end face of the second eccentric section 122 is located in the accommodation cavity 260, and the second end of the pressure relief hole 130 is provided on the upper end face or the lower end face of the second eccentric section 122, which is beneficial to ensuring the effective connection between the pressure relief hole 130 and the accommodation cavity 260.

[0099] Such as Figure 1 、 Figure 3 and Figure 6 As shown, in some embodiments, optionally, the pressure relief hole 130 extends radially along the shaft body 110.

[0100] In this embodiment, it is defined that the pressure relief hole 130 extends along the radial direction of the shaft body 110. That is to say, the pressure relief hole 130 is a radial hole. Thus, when a local high pressure is generated in the accommodation cavity 260, the refrigerant can enter the oil supply channel 111 through the pressure relief hole 130 for rapid pressure relief, preventing the refrigerant in the accommodation cavity 260 from leaking into the compression cavity. At the same time, it is beneficial to reducing the processing difficulty of the pressure relief hole 130, and further beneficial to reducing the production cost of the crankshaft 100.

[0101] Such as Figure 3 As shown, in some embodiments, optionally, the aperture D of the pressure relief hole 130 satisfies D≥1 mm.

[0102] In this embodiment, it is defined that the aperture of the pressure relief hole 130 is greater than or equal to 1 mm. Thus, when a local high pressure is generated in the accommodation cavity 260, the refrigerant can enter the oil supply channel 111 through the pressure relief hole 130 for effective pressure relief, preventing the refrigerant in the accommodation cavity 260 from leaking into the compression cavity. At the same time, it is beneficial to reducing the processing difficulty of the pressure relief hole 130, and further beneficial to reducing the production cost of the crankshaft 100.

[0103] Such as Figure 5 As shown, in some embodiments, optionally, the crankshaft 100 further includes an oil supply hole 140. The oil supply hole 140 is provided on the second eccentric section 122. One end of the oil supply hole 140 is communicated with the oil supply channel 111, and the other end of the oil supply hole 140 penetrates through the outer wall of the second eccentric section 122.

[0104] In this embodiment, it is defined that the crankshaft 100 further includes an oil supply hole 140. Specifically, the oil supply hole 140 is provided on the second eccentric section 122, and one end of the oil supply hole 140 is communicated with the oil supply passage 111, and the other end penetrates through the outer wall of the second eccentric section 122, so as to supply oil to the part where the second eccentric section 122 contacts the inner wall of the piston 240, thereby improving the reliability of the compressor.

[0105] According to the second aspect of the present invention, a pump body assembly 200 is provided, which includes the crankshaft 100 provided in any of the above embodiments, and thus has all the beneficial technical effects of the crankshaft 100, which will not be elaborated herein.

[0106] As Figure 6 shown, further, the pump body assembly 200 further includes a cylinder 210, a first bearing 220, a second bearing 230, a piston 240 and a sliding vane 250. Among them, along the axial direction of the shaft body 110, the first bearing 220 and the second bearing 230 are respectively arranged on both sides of the cylinder 210; the piston 240 is arranged in the cylinder 210, the piston 240 is provided with a receiving cavity 241, and a part of the cavity wall of the receiving cavity 241, the first bearing 220 and the second bearing 230 enclose to form a receiving cavity 260, and the eccentric part 120 is located in the receiving cavity 260; the sliding vane 250 is arranged in the cylinder 210 and abuts against the outer wall of the piston 240.

[0107] The pump body assembly 200 provided by the embodiment of the present invention includes a cylinder 210, a first bearing 220, a second bearing 230, a piston 240, a sliding vane 250 and a crankshaft 100. Specifically, the first bearing 220 and the second bearing 230 are respectively arranged on both sides in the axial direction of the cylinder 210, the piston 240 is arranged in the cylinder 210, the outer wall of the piston 240 and the inner wall of the cylinder 210 form a compression cavity, the piston 240 has a receiving cavity 241, and the cavity wall of the receiving cavity 241, that is, the inner wall of the piston 240, the first bearing 220 and the second bearing 230 enclose to form a receiving cavity 260, and the eccentric part 120 is rotatably located in the receiving cavity 260.

[0108] The eccentric part 120 includes a first eccentric section 121 and a second eccentric section 122. Specifically, the first eccentric section 121 and the second eccentric section 122 are arranged along the axial direction of the shaft body 110. Among them, the diameter of the first eccentric section 121 is smaller than that of the second eccentric section 122. That is to say, along the radial direction of the shaft body 110, the distance between the outer wall of the first eccentric section 121 and the central axis of the shaft body 110 is smaller than the distance between the outer wall of the second eccentric section 122 and the central axis of the shaft body 110.

[0109] Specifically, during the operation of the compressor, the eccentric part 120 rotates within the accommodation cavity 260 to compress the refrigerant within the compression cavity. By making the diameter of the first eccentric section 121 of the eccentric part 120 smaller, it is beneficial to reduce the contact area between the eccentric part 120 and the inner wall of the piston 240, decrease the friction between the eccentric part 120 and the piston 240, and improve the reliability of the compressor.

[0110] When the eccentric part 120 rotates within the accommodation cavity 260, the second eccentric section 122 with a larger diameter contacts the inner wall of the piston 240. Therefore, frictional heat is generated, causing the refrigerant dissolved in the lubricating oil to escape, resulting in high pressure within the accommodation cavity 260, causing the refrigerant to leak into the compression cavity and reducing the efficiency of the compressor.

[0111] The pressure relief hole 130 is provided on at least one of the first eccentric section 121 and the second eccentric section 122. Specifically, the pressure relief hole 130 is provided on the first eccentric section 121. Alternatively, the pressure relief hole 130 is provided on the second eccentric section 122. Or, the first eccentric section 121 and the second eccentric section 122 are respectively provided with the pressure relief hole 130. It can be specifically set according to actual needs.

[0112] The first end of the pressure relief hole 130 is communicated with the oil supply passage 111, and the second end of the pressure relief hole 130 is communicated with the accommodation cavity 260. That is to say, the accommodation cavity 260 can be communicated with the oil supply passage 111 through the pressure relief hole 130, so that the refrigerant escaping from the lubricating oil can leak into the oil supply passage 111 through the pressure relief hole 130 to complete pressure relief, and will not leak into the compression cavity, which is beneficial to improving the working efficiency of the compressor and ensuring the reliability of the compressor.

[0113] According to the third aspect of the present invention, a compressor is provided, including the crankshaft 100 or the pump body assembly 200 provided in any of the above embodiments, and thus has all the beneficial technical effects of the crankshaft 100 or the pump body assembly 200, which will not be elaborated herein.

[0114] According to the fourth aspect of the present invention, a refrigeration device is provided, including the crankshaft 100 or the pump body assembly 200 or the compressor provided in any of the above embodiments, and thus has all the beneficial technical effects of the crankshaft 100 or the pump body assembly 200 or the compressor, which will not be elaborated herein.

[0115] In the description of this specification, terms such as "connection", "installation", "fixation", etc. should all be understood in a broad sense. For example, "connection" can be a fixed connection, a detachable connection, or an integral connection; it can be directly connected or indirectly connected through an intermediate medium. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0116] In the description of this specification, the descriptions of the terms "one embodiment", "some embodiments", "specific embodiments", etc. mean that the specific features, structures, materials or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present utility model. In this specification, the schematic representations of the above terms do not necessarily refer to the same embodiment or instance. Moreover, the specific features, structures, materials or characteristics described may be combined in any one or more embodiments or examples in a suitable manner.

[0117] The above are only the preferred embodiments of the present utility model and are not intended to limit the present utility model. For those skilled in the art, various modifications and variations can be made to the present utility model. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present utility model shall be included within the protection scope of the present utility model.

Claims

1. A crankshaft, characterized in that: The crankshaft is used for a pump body assembly, the pump body assembly has an accommodating cavity, and the crankshaft comprises: A shaft body, wherein the shaft body is provided with an oil supply passage; an eccentric portion, provided on the shaft body and located in the accommodating cavity, the eccentric portion comprising a first eccentric segment and a second eccentric segment, the first eccentric segment and the second eccentric segment are arranged along the axial direction of the shaft body, and the diameter of the first eccentric segment is smaller than the diameter of the second eccentric segment; A pressure relief hole is provided on at least one of the first eccentric segment and the second eccentric segment, a first end of the pressure relief hole is communicated with the oil supply passage, and a second end of the pressure relief hole is used to communicate with the accommodating chamber.

2. The crankshaft according to claim 1, characterized in that The first eccentric segment includes a first shaft segment and a second shaft segment, and along the axial direction of the shaft body, the first shaft segment and the second shaft segment are respectively located on both sides of the second eccentric segment; Wherein, in the case where the pressure relief hole is provided in the first eccentric segment, the pressure relief hole is provided in at least one of the first shaft segment and the second shaft segment.

3. The crankshaft according to claim 2, characterized in that When the pressure relief hole is provided in the first shaft segment, the diameter D of the pressure relief hole, the diameter Dp1 of the first shaft segment and the inner diameter Do of the oil supply passage satisfy 6<(Dp1-Do) / D<15; and / or When the pressure relief hole is provided in the second shaft segment, the hole diameter D of the pressure relief hole, the diameter Dp2 of the second shaft segment and the inner diameter Do of the oil supply passage satisfy 6<(Dp2-Do) / D<15.

4. The crankshaft according to any one of claims 1 to 3, characterized in that When the pressure relief hole is provided in the second eccentric section, the hole diameter D of the pressure relief hole, the diameter Dp3 of the second eccentric section and the inner diameter Do of the oil supply passage satisfy 6<(Dp3-Do) / D<15.

5. The crankshaft according to any one of claims 1 to 3, characterized in that The first eccentric segment has an outer circumferential surface, at least a portion of which extends along the axial direction of the shaft body. When the pressure relief hole is provided in the first eccentric segment, the second end of the pressure relief hole is provided on the outer circumferential surface.

6. The crankshaft according to any one of claims 1 to 3, characterized in that The first eccentric segment has a first end face, at least a portion of which extends radially along the shaft body. When the pressure relief hole is provided in the first eccentric segment, the second end of the pressure relief hole is provided on the first end face.

7. The crankshaft according to any one of claims 1 to 3, characterized in that The second eccentric segment has a second end face, at least a portion of which extends radially along the shaft body. When the pressure relief hole is provided in the second eccentric segment, the second end of the pressure relief hole is provided on the second end face.

8. The crankshaft according to any one of claims 1 to 3, characterized in that The pressure relief hole extends in a radial direction of the shaft body.

9. The crankshaft according to any one of claims 1 to 3, characterized in that Also includes: An oil supply hole is provided on the second eccentric segment, one end of the oil supply hole is communicated with the oil supply passage, and the other end of the oil supply hole passes through the outer wall of the second eccentric segment.

10. A pump assembly, characterized in that: include: A crankshaft as claimed in any one of claims 1 to 9; cylinder; A first bearing and a second bearing, along the axial direction of the shaft body, the first bearing and the second bearing are respectively arranged on both sides of the cylinder; A piston is disposed in the cylinder, the piston is provided with an accommodating cavity, a part of the cavity wall of the accommodating cavity, the first bearing and the second bearing together form an accommodating cavity, and the eccentric portion is located in the accommodating cavity; The sliding plate is arranged on the cylinder and abuts against the outer wall of the piston.

11. A compressor, characterized in that: include: A crankshaft as claimed in any one of claims 1 to 9; or The pump assembly of claim 10.

12. A refrigeration device, characterized in that: include: A crankshaft as claimed in any one of claims 1 to 9; or The pump assembly according to claim 10; or the compressor according to claim 11.

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