Rotary Compressor and Refrigeration Equipment

Abstract

The present invention discloses a rotary compressor and a refrigeration device. The rotary compressor includes a pump body assembly, a motor assembly, a crankshaft, and a bearing body. The pump body assembly includes a cylinder; the motor assembly includes a stator and a rotor, and the stator is arranged around the rotor; the crankshaft passes through the rotor and is connected to the rotor. The crankshaft includes an eccentric portion and a connecting section. The eccentric portion and the connecting section are respectively located at two ends of the motor assembly along the axial direction of the crankshaft. The eccentric portion is rotatably arranged in the cylinder. The crankshaft is provided with a central oil hole, and the connecting section is provided with a first oil outlet hole, and the first oil outlet hole communicates with a central guide hole; the bearing body is provided with a shaft hole, and the bearing body is sleeved on the connecting section through the shaft hole; wherein, the oil outlet end of the first oil outlet hole faces the gap between the outer peripheral wall of the connecting section and the inner wall of the shaft hole. The lubricity between the bearing body and the crankshaft of the rotary compressor of the present invention is good and the wear is small.

Description

Technical Field

[0001] The present invention relates to the technical field of compressors, and particularly to a rotary compressor and a refrigeration device. Background Art

[0002] With the high-speed and high-efficiency development of rotary compressors and the use of high-stack motors in specific environments, it has become particularly important to ensure the coaxiality between the stator and the rotor of the motor during operation and to reduce the shaft-end deformation of the crankshaft for ensuring the reliability of rotary compressors. For this purpose, some rotary compressors achieve the above purposes by installing motor bearings at the ends of the motors. However, when using conventional sliding bearings as motor bearings, the motor bearings themselves are prone to wear and have relatively poor reliability, thus affecting the overall reliability of the rotary compressor. Summary of the Invention

[0003] The present invention aims to solve at least one of the technical problems existing in the prior art. For this reason, the present invention provides a rotary compressor with good lubricity and small wear between the bearing body and the crankshaft.

[0004] The present invention also provides a refrigeration device having the above rotary compressor.

[0005] The rotary compressor according to the first aspect embodiment of the present invention includes: a pump body assembly including a cylinder; a motor assembly including a stator and a rotor, the stator being arranged around the rotor; a crankshaft passing through the rotor and connected to the rotor, the crankshaft including an eccentric portion and a connecting section, the eccentric portion and the connecting section being respectively located at two ends of the motor assembly along the axial direction of the crankshaft, the eccentric portion being rotatably arranged in the cylinder, the crankshaft being provided with a central oil hole, the connecting section being provided with a first oil outlet hole, the first oil outlet hole communicating with the central guide hole; a bearing body provided with a shaft hole, the bearing body being sleeved on the connecting section through the shaft hole; wherein, the oil outlet end of the first oil outlet hole faces the gap between the outer peripheral wall of the connecting section and the inner wall of the shaft hole.

[0006] The rotary compressor according to the first aspect embodiment of the present invention has at least the following beneficial effects: By providing a first oil outlet hole communicating with the central oil hole in the connecting section of the crankshaft, and the first oil outlet hole facing the gap between the outer peripheral wall of the connecting section and the inner wall of the shaft hole of the bearing body, when the rotary compressor operates, the lubricating oil can directly flow between the connecting section and the inner wall of the shaft hole through the central oil hole and the first oil outlet hole, increasing the oil film thickness between the connecting section and the inner wall of the shaft hole, achieving the purpose of lubrication, keeping a good lubrication state between the crankshaft and the bearing body all the time, reducing the wear of the crankshaft and the bearing body, and effectively improving the reliability of the bearing body and the rotary compressor. At the same time, since part of the lubricating oil flows out from the first oil outlet hole, the amount of oil reaching the top space of the crankshaft can be reduced, so as to reduce the oil discharge amount of the rotary compressor and further improve the reliability of the rotary compressor.

[0007] According to some embodiments of the present invention, the first oil outlet hole is arranged along the radial direction of the crankshaft.

[0008] According to some embodiments of the present invention, a groove body is provided on the outer peripheral wall of the connecting section, the groove body communicates with the first oil outlet hole, and an oil groove is defined between the groove body and the inner wall of the shaft hole.

[0009] According to some embodiments of the present invention, the groove body includes a bottom wall and a side wall, the side wall is connected to one end of the bottom wall along the axial direction of the crankshaft, the bottom wall is closer to the central axis of the crankshaft than the side wall, and both ends of the bottom wall along the circumferential direction of the crankshaft respectively extend to the outer peripheral wall of the connecting section.

[0010] According to some embodiments of the present invention, the bottom wall is a straight wall, and the included angle between the reference plane passing through the central axis of the crankshaft and perpendicular to the bottom wall and the deflection direction of the eccentric part is θ, satisfying: 45°≤θ≤135°.

[0011] According to some embodiments of the present invention, the maximum radial dimension of the connecting section is D, and the maximum linear distance between both ends of the groove body in the circumferential direction of the crankshaft is W, satisfying: W / D≤0.7.

[0012] According to some embodiments of the present invention, along the axial direction of the crankshaft, one end of the groove body facing the motor assembly penetrates through the connecting section, and the connecting section includes a first oil retaining part, and the first oil retaining part is located at the other end of the groove body.

[0013] According to some embodiments of the present invention, along the axial direction of the crankshaft, the length of the first oil retaining part is L1, and the maximum length of the groove body is L2, satisfying: L1 / L2≥0.25.

[0014] According to some embodiments of the present invention, the connecting section includes a first oil-blocking portion and a second oil-blocking portion, and the first oil-blocking portion and the second oil-blocking portion are respectively located at two ends of the slot body along the axial direction of the crankshaft.

[0015] According to some embodiments of the present invention, the central oil hole is closed toward one end of the bearing body.

[0016] According to some embodiments of the present invention, a second oil outlet hole is provided at one end of the connecting section away from the motor assembly, the second oil outlet hole is connected to the central oil hole, and the oil outlet end of the second oil outlet hole is located on the upper end wall of the connecting section, and the inner diameter of the second oil outlet hole is smaller than the inner diameter of the first oil outlet hole and the inner diameter of the central oil hole.

[0017] A refrigeration device according to an embodiment of the second aspect of the present invention comprises a rotary compressor according to an embodiment of the first aspect of the present invention.

[0018] According to the refrigeration equipment of the second aspect of the present invention, there are at least the following beneficial effects: since the refrigeration equipment adopts the above-mentioned rotary compressor, a first oil outlet hole connected to the central oil hole is set in the connecting section of the crankshaft, and the first oil outlet hole faces the gap between the outer peripheral wall of the connecting section and the inner wall of the shaft hole of the bearing body. When the rotary compressor is running, the lubricating oil can flow directly to the inner wall between the connecting section and the shaft hole through the central oil hole and the first oil outlet hole, increasing the oil film thickness between the connecting section and the inner wall of the shaft hole, achieving the purpose of lubrication, so that the crankshaft and the bearing body are always kept in a good lubrication state, reducing the wear of the crankshaft and the bearing body, and effectively improving the reliability of the bearing body and the rotary compressor. At the same time, since part of the lubricating oil flows out from the first oil outlet hole, the amount of oil reaching the top space of the crankshaft can be reduced, so as to reduce the oil discharge amount of the rotary compressor, and further improve the reliability of the rotary compressor.

[0019] 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

[0020] The present invention will be further described below with reference to the accompanying drawings and embodiments, wherein:

[0021] Figure 1 is a cross-sectional schematic diagram of the internal structure of a rotary compressor in an embodiment of the present invention;

[0022] Figure 2 yes Figure 1 A in the enlarged view;

[0023] Figure 3 is a front view of a crankshaft in an embodiment of the present invention;

[0024] Figure 4 is Figure 3 The sectional view taken along line B-B in the middle;

[0025] Figure 5 It is a partial schematic view of the crankshaft in another embodiment of the present invention;

[0026] Figure 6 It is a partial sectional view of the crankshaft in another embodiment of the present invention;

[0027] Figure 7 It is a curve graph showing that the oil film thickness changes with the change of the angle θ in the embodiment of the present invention;

[0028] Figure 8 It is a curve graph showing that the oil film thickness changes with the change of the ratio W / D in the embodiment of the present invention;

[0029] Figure 9 It is a curve graph showing that the oil film thickness changes with the change of the ratio L1 / L2 in the embodiment of the present invention.

[0030] Reference numerals:

[0031] Pump body assembly 100; first cylinder 110; first compression cavity 111; first roller 112; second cylinder 120; second compression cavity 121; second roller 122; first bearing 130; second bearing 140; partition 150;

[0032] Motor assembly 200; stator 210; rotor 220; balance weight 221;

[0033] Crankshaft 300; eccentric part 310; connecting section 320; first oil outlet hole 321; second oil outlet hole 322; groove body 323; first oil retaining part 324; second oil retaining part 325; bottom wall 326; central oil hole 330; oil groove 340;

[0034] Bearing body 400; main body part 410; mounting part 420; shaft hole 430. Detailed implementation manners

[0035] The embodiments of the present invention will be described in detail below. Examples of the embodiments are shown in the drawings, where the same or similar reference numerals indicate the same or similar elements or elements with the same or similar functions throughout. The embodiments described below by referring to the drawings are exemplary and are only used to explain the present invention and should not be construed as a limitation of the present invention.

[0036] In the description of the present invention, it should be understood that for the orientation description, such as the orientation or positional relationship indicated by up, down, front, back, left, right, etc., it is based on the orientation or positional relationship shown in the drawings. It is only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation. Therefore, it should not be construed as a limitation to the present invention.

[0037] In the description of the present invention, "several" means one or more, "multiple" means more than two, "greater than", "less than", "exceeding", etc. are understood not to include the present number, and "above", "below", "within", etc. are understood to include the present number. If there is a description of first and second, it is only for the purpose of distinguishing technical features and cannot be understood as indicating or implying relative importance or implicitly indicating the quantity of the indicated technical features or implicitly indicating the sequence relationship of the indicated technical features.

[0038] In the description of the present invention, unless otherwise clearly defined, words such as "set", "installed", "connected", "assembled", "matched", etc. should be understood in a broad sense, and those skilled in the art can reasonably determine the specific meanings of the above words in the present invention in combination with the specific content of the technical solution.

[0039] With the high-speed and high-efficiency development of rotary compressors and the use of high-stack motors in specific environments, it becomes particularly important to ensure the coaxiality between the stator and rotor of the motor during operation and to reduce the shaft-end deformation of the crankshaft for ensuring the reliability of rotary compressors. For this reason, some rotary compressors achieve the above purposes by installing motor bearings at the ends of the motors.

[0040] However, when using a conventional sliding bearing as the motor bearing, on the one hand, the motor bearing itself is prone to wear and has relatively poor reliability; on the other hand, relying on the lubricating oil sprayed into the top space of the crankshaft to flow into the gap between the crankshaft and the motor bearing under the action of gravity, the amount of lubricating oil in the gap is small, the oil film thickness is small, and it is difficult to meet the lubrication performance under high-speed operation conditions, resulting in increased wear of the crankshaft and the motor bearing, affecting the service life and reliability of the motor bearing, and further affecting the overall reliability of the rotary compressor.

[0041] For this reason, referring to Figures 1 to 6 as shown, an embodiment of the first aspect of the present invention provides a rotary compressor, which can be a single-cylinder rotary compressor or a double-cylinder rotary compressor.

[0042] Referring to Figure 1As shown, it is a schematic cross-sectional view of the internal structure of a rotary compressor, with the housing omitted. It can be understood that the rotary compressor includes a pump body assembly 100, a motor assembly 200, a crankshaft 300, and a bearing body 400. Among them, the pump body assembly 100 has a double-cylinder structure. Specifically, the pump body assembly 100 includes a first cylinder 110 and a second cylinder 120. The pump body assembly 100 also includes a first bearing 130, a second bearing 140, and a partition 150. The first cylinder 110 is arranged above the second cylinder 120. The partition 150 is clamped between the first cylinder 110 and the second cylinder 120. The first bearing 130 is arranged above the first cylinder 110. The second bearing 140 is arranged below the second cylinder 120. That is to say, the first cylinder 110 and the second cylinder 120 are arranged between the first bearing 130 and the second bearing 140. The first cylinder 110 is provided with a first compression cavity 111 and a first roller 112 installed in the first compression cavity 111. Similarly, the second cylinder 120 is provided with a second compression cavity 121 and a second roller 122 installed in the second compression cavity 121. The lower part of the crankshaft 300 sequentially passes through the first bearing 130, the first cylinder 110, the partition 150, the second cylinder 120, and the second bearing 140. And two eccentric parts 310 are provided on the lower part of the crankshaft 300. The eccentric directions of the two eccentric parts 310 are different. For example, the deflection directions of the two eccentric parts 310 are opposite. The eccentric direction of the eccentric part 310 is the direction from the central axis of the crankshaft 300 towards the center of the eccentric part 310. The two eccentric parts 310 are arranged at intervals up and down and are respectively rotatably arranged in the first compression cavity 111 and the second compression cavity 121, so as to realize the connection between the crankshaft 300 and the first cylinder 110 and the connection between the crankshaft 300 and the second cylinder 120.

[0043] Referring to Figure 1 As shown, it can be understood that by providing the first bearing 130 and the second bearing 140, the support and positioning of the crankshaft 300 are realized to bear the reaction force of the compressed gas in the first cylinder 110 and the second cylinder 120 during the working process of the rotary compressor, and the working stability of the first cylinder 110 and the second cylinder 120 is improved.

[0044] Referring to Figure 1As shown, it can be understood that the motor assembly 200 is connected to the crankshaft 300 and located above the pump body assembly 100. Specifically, the motor assembly 200 includes a stator 210 and a rotor 220. Generally speaking, the stator 210 is fixedly connected to the housing of the rotary compressor. The stator 210 is annular, and the rotor 220 is arranged within the inner circle of the stator 210, that is, the stator 210 is arranged around the rotating shaft rotor 220, and the crankshaft 300 passes through the rotor 220 and is fixedly connected to the rotor 220. The rotor 220 can rotate relative to the stator 210. Under the action of the magnetic field, the rotor 220 can be driven to rotate relative to the stator 210. Thus, the rotor 220 drives the eccentric part 310 to rotate through the crankshaft 300, realizing the compression of the refrigerant in the first compression cavity 111 and the second compression cavity 121.

[0045] Referring to Figure 1 As shown, it can be understood that in order to balance the centrifugal force of the eccentric part 310 of the crankshaft 300, balance weights 221 are installed at both the upper and lower ends of the rotor 220, and the two balance weights 221 at the upper and lower ends are located at both radial ends of the rotor 220, that is, the two balance weights 221 are arranged on opposite sides. Therefore, the balance during the rotation of the rotor 220 can be improved, the radial offset amplitude of the rotor 220 can be reduced, the coaxiality of the stator 210 and the rotor 220 can be improved, and the dynamic and static balance effect can be improved.

[0046] Referring to Figure 1 As shown, it can be understood that in order to improve the coaxiality of the stator 210 and the rotor 220, prevent the stator 210 from rubbing against the rotor 220, and reduce the flexural deformation at the end of the crankshaft 300, the bearing body 400 is installed at the upper end of the crankshaft 300, that is, the bearing body 400 is located on the side of the rotor 220 away from the pump body assembly 100.

[0047] Referring to Figure 1 As shown, it can be understood that specifically, the bearing body 400 includes a main body part 410 and a mounting part 420. The main body part 410 is cylindrical, and the mounting part 420 is connected to the upper end of the main body part 410 and is annular. The mounting part 420 is arranged around the main body part 410, and the bearing body 400 can be fixedly installed through the mounting part 420. The main body part 410 and the mounting part 420 are of an integrally formed structure, which is easy to produce.

[0048] Referring to Figure 1 and Figure 2As shown, it can be understood that the main body 410 is provided with a shaft hole 430, and the shaft hole 430 penetrates the main body 410 along the axial direction of the bearing body 400. Correspondingly, the crankshaft 300 includes a connecting section 320, and the connecting section 320 is located at the upper end of the crankshaft 300. The connecting section 320 is a cylindrical structure. The bearing body 400 is sleeved on the connecting section 320 through the shaft hole 430, so as to realize the support and positioning of the crankshaft 300. Generally speaking, the connecting section 320 is completely accommodated in the shaft hole 430.

[0049] Referring to Figure 1 and Figure 2 As shown, it can be understood that the crankshaft 300 is provided with a central oil hole 330, and the central oil hole 330 extends upward along the axial direction of the crankshaft 300 to the connecting section 320. Generally speaking, an oil sump is provided in the housing of the rotary compressor, and the oil sump is used to store lubricating oil. The oil sump is located below the pump body assembly 100, and the lower end of the central oil hole 330 is open and communicates with the oil groove 340. When the rotary compressor operates, the crankshaft 300 rotates at a high speed, and a continuous oil supply state will be formed in the central oil hole 330, so that the lubricating oil in the oil sump is transported upward through the central oil hole 330 to lubricate the pump body assembly 100, the crankshaft 300, etc., reduce wear, and can take away part of the heat generated during the rotation of the crankshaft 300 through the lubricating oil, improving the reliability of the rotary compressor.

[0050] Referring to Figure 2 As shown, it can be understood that the connecting section 320 is provided with a first oil outlet hole 321, and the first oil outlet hole 321 is arranged along the radial direction of the connecting section 320, which is convenient for processing. One end of the first oil outlet hole 321 communicates with the central oil hole 330, and the other end (i.e., the oil outlet end of the first oil outlet hole 321) faces the gap between the outer peripheral wall of the connecting section 320 and the inner wall of the shaft hole 430. That is to say, the oil outlet end of the first oil outlet hole 321 communicates with the gap between the outer peripheral wall of the connecting section 320 and the inner wall of the shaft hole 430. Therefore, the lubricating oil can directly flow into the gap between the outer peripheral wall of the connecting section 320 and the inner wall of the shaft hole 430 through the central oil hole 330 and the first oil outlet hole 321, realizing lubrication of the contact area between the crankshaft 300 and the bearing body 400, increasing the amount of lubricating oil in the gap, increasing the minimum oil film thickness in the contact area, enhancing the lubrication effect, and reducing the wear of the crankshaft 300 and the bearing body 400.

[0051] It is easy to understand that under the action of gravity, the lubricating oil in the gap between the outer peripheral wall of the connecting section 320 and the inner wall of the shaft hole 430 will flow downward out of the gap, making the lubricating oil in the gap in a flowing state. Therefore, to a certain extent, the lubricating oil can take away part of the heat generated during the rotation of the crankshaft 300, improving the reliability of the crankshaft 300 and the bearing body 400 and further reducing wear.

[0052] Of course, it can be understood that the first oil outlet hole 321 can also be arranged to incline upward or downward, as long as one end of the first oil outlet hole 321 communicates with the central oil hole 330 and the other end faces the gap between the outer peripheral wall of the connecting section 320 and the inner wall of the shaft hole 430.

[0053] By providing the first oil outlet hole 321 communicating with the central oil hole 330 in the connecting section 320 of the crankshaft 300, and the first oil outlet hole 321 facing the gap between the outer peripheral wall of the connecting section 320 and the inner wall of the shaft hole 430, when the rotary compressor operates, the lubricating oil can directly flow between the connecting section 320 and the inner wall of the shaft hole 430 through the central oil hole 330 and the first oil outlet hole 321, increasing the oil film thickness between the connecting section 320 and the inner wall of the shaft hole 430, achieving the purpose of lubrication, keeping a good lubrication state between the crankshaft 300 and the bearing body 400 all the time, reducing the wear of the crankshaft 300 and the bearing body 400, and effectively improving the reliability of the bearing body 400 and the rotary compressor. At the same time, since part of the lubricating oil flows out from the first oil outlet hole 321, the amount of oil reaching the top space of the crankshaft 300 can be reduced to reduce the oil discharge amount of the rotary compressor, further improving the reliability of the rotary compressor.

[0054] Refer to Figure 2 and Figure 3 As shown, it can be understood that a groove 323 is provided on the outer peripheral wall of the connecting section 320. Specifically, the groove 323 is a groove structure formed by cutting off a part of the structure on the outside of the connecting section 320, and the groove 323 is recessed relative to the outer peripheral wall of the connecting section 320 towards the central axis of the crankshaft 300. The groove 323 is located at the oil outlet end of the first oil outlet hole 321. Therefore, the groove 323 communicates with the first oil outlet hole 321. And, the space defined between the groove 323 and the inner wall of the shaft hole 430 forms an oil sump 340. Therefore, during the rotation of the crankshaft 300, a certain amount of lubricating oil can always be stored in the oil sump 340, so as to further increase the minimum oil film thickness between the connecting section 320 and the inner wall of the shaft hole 430, keep a good lubrication state between the crankshaft 300 and the bearing body 400 all the time, reduce wear, and greatly improve the reliability of the crankshaft 300 and the bearing body 400.

[0055] Refer to Figure 2 and Figure 3As shown, it can be understood that the groove body 323 includes a bottom wall 326 and a side wall. The bottom wall 326 is a straight wall and is parallel to the central axis of the crankshaft 300. Along the circumferential direction of the crankshaft 300, both ends of the bottom wall 326 extend to the outer peripheral wall of the connecting section 320, that is, the bottom wall 326 is connected to the outer peripheral wall of the connecting section 320. An edge is formed at the connection between the bottom wall 326 and the outer peripheral wall of the connecting section 320, and the edge is arranged along the axial direction of the crankshaft 300. Along the axial direction of the crankshaft 300, the lower end of the bottom wall 326 extends to the lower end of the connecting section 320, that is, the lower end of the groove body 323 (i.e., the end facing the motor assembly 200) penetrates through the connecting section 320. The side wall is connected to the upper end of the bottom wall 326 and is perpendicular to the central axis of the crankshaft 300. That is, the bottom wall 326 is closer to the central axis of the crankshaft 300 than the side wall, and the bottom wall 326 is rectangular. Therefore, the connecting section 320 forms a first oil retaining portion 324 at the upper end of the groove body 323. The first oil retaining portion 324 protrudes relative to the bottom wall 326, so that the upper end of the groove body 323 does not penetrate through the connecting section 320. The outer peripheral wall of the connecting section 320 at the first oil retaining portion 324 is a complete cylindrical surface, and the connecting section 320 includes the shaft section where the groove body 323 is located and the shaft section where the first oil retaining portion 324 is located.

[0056] Therefore, in the oil groove 340 defined by the inner wall of the groove body 323 and the shaft hole 430, the lower end is open, and the first oil retaining portion 324 is provided at the upper end. When the lubricating oil flows into the oil groove 340, the first oil retaining portion 324 can block the upward flow of the lubricating oil, thereby reducing the amount of oil reaching the top space of the crankshaft 300 and reducing the oil discharge amount of the rotary compressor. At the same time, the lubricating oil mainly flows downward through the opening. On the one hand, the oil discharge rate of the first oil outlet hole 321 can be increased, the lubrication of the crankshaft 300 and the bearing body 400 can be maintained, the minimum oil film thickness can be increased, and wear can be reduced. On the other hand, the flow rate of the lubricating oil can be increased, so that the lubricating oil can quickly take away the heat generated during the rotation of the crankshaft 300, further reducing wear.

[0057] Referring to Table 1 shown, it is easy to understand that under the same working conditions, in Example 1, both the upper and lower ends of the groove body 323 penetrate through the connecting section 320, that is, both the upper and lower ends of the oil groove 340 are open. At this time, the minimum oil film thickness between the crankshaft 300 and the bearing body 400 is 0.701 μm. In Example 2, the lower end of the groove body 323 penetrates through the connecting section 320, and the first oil retaining portion 324 is provided at the upper end, that is, only the lower end of the oil groove 340 is open. At this time, the minimum oil film thickness between the crankshaft 300 and the bearing body 400 is 0.883 μm, which is larger than that in Example 1. Therefore, by providing the first oil retaining portion 324, the minimum oil film thickness between the crankshaft 300 and the bearing body 400 can be effectively increased.

[0058] Table 1: Comparison of minimum oil film thickness under different schemes

[0059] Example Solution Minimum oil film thickness / μm One Both the upper and lower ends of the tank body penetrate through the connecting section 0.701 Two The lower end of the tank body penetrates through the connecting section, and the upper end is provided with a first oil retaining part 0.883

[0060] It is understandable that when the crankshaft 300 rotates and drives the eccentric part 310 to rotate to compress the refrigerant, in the radial direction of the crankshaft 300, the side of the crankshaft 300 facing the eccentric part 310 is the load-bearing side. In general, since the load-bearing side bears the largest load, the oil film thickness of the crankshaft 300 at the load-bearing side is the smallest. When the slot body 323 is provided, the load-bearing area of the side where the slot body 323 is located on the crankshaft 300 is small. When the slot body 323 is located on the load-bearing side, the load-bearing area of the crankshaft 300 at the load-bearing side is reduced. Under the condition that the load remains unchanged, the surface pressure will increase, and the oil film thickness of the crankshaft 300 at the load-bearing side will be further reduced. The oil film here is ultra-thin, which will cause aggravated wear. When the slot body 323 is closer to the load-bearing side, along the radial direction of the crankshaft 300, the load borne by the side where the slot body 323 is located on the crankshaft 300 is greater, the surface pressure is greater, and the oil film thickness is smaller, that is, the oil film thickness deteriorates.

[0061] Reference Figure 3 and Figure 4 As shown, it can be understood that the crankshaft 300 includes two eccentric parts 310, and the eccentric directions of the two eccentric parts 310 are opposite, and the eccentric direction is the direction from the central axis of the crankshaft 300 toward the center of the eccentric part 310. In actual operation, when the crankshaft 300 rotates, the centrifugal forces acting on the two eccentric parts 310 are generally not equal. Therefore, in the radial direction of the crankshaft 300, the side surfaces of the crankshaft 300 facing the two eccentric parts 310 are all load-bearing sides.

[0062] Reference Figure 3 and Figure 4 As shown, it can be understood that, for this purpose, a reference plane is defined that passes through the central axis of the crankshaft 300 and is perpendicular to the bottom wall 326 of the slot body 323. The angle between the reference plane and the eccentric direction of one of the eccentric parts 310 is θ, which satisfies: 45°≤θ≤135°. Since the eccentric directions of the two eccentric parts 310 are opposite, the angle between the reference plane and the eccentric direction of the other eccentric part 310 also satisfies the range of greater than or equal to 45° and less than or equal to 135°. When θ<45°, the distance between the slot body 323 and the corresponding load-bearing side of the eccentric part 310 is relatively close. Along the radial direction of the crankshaft 300, the side of the crankshaft 300 where the slot body 323 is located is subjected to a larger load, the surface pressure is increased, and the oil film thickness here is reduced, that is, the oil film thickness is deteriorated, especially the oil film thickness at the edge is smaller, which will cause aggravated wear. When θ>135°, the distance between the groove body 323 and the load-bearing side where the other eccentric portion 310 is located is relatively close. Similarly, along the radial direction of the crankshaft 300, the load borne by the side of the crankshaft 300 where the groove body 323 is located is relatively large, and the surface pressure is increased. The oil film thickness here is reduced, that is, the oil film thickness is deteriorated, especially the oil film thickness at the edges is even smaller, which will also cause increased wear.

[0063] Reference Figure 7 As shown, it can be understood that under the same working conditions, as the included angle θ between the reference plane and the eccentricity direction of one of the eccentric parts 310 increases, along the radial direction of the crankshaft 300, the oil film thickness on the side of the crankshaft 300 where the groove 323 is located first increases and then decreases. When 45° ≤ θ ≤ 135°, the oil film thickness on the side of the crankshaft 300 where the groove 323 is located is greater than or equal to 1.7 μm. When θ < 45° or θ > 135°, the oil film thickness on the side of the crankshaft 300 where the groove 323 is located is less than 1.7 μm. Therefore, making 45° ≤ θ ≤ 135°, for example, θ = 60°, θ = 90° or θ = 120°, etc., can avoid the groove 323 being too close to any one of the bearing sides where the two eccentric parts 310 are located, thereby reducing the load borne by the side of the crankshaft 300 where the groove 323 is located, reducing the surface pressure, increasing the oil film thickness here, and keeping the oil film thickness stable. Furthermore, it can keep good lubricity between the crankshaft 300 and the bearing body 400, reduce wear, and improve reliability.

[0064] Reference Figure 4 As shown, it can be understood that when θ = 90°, the distances from the groove 323 to the bearing sides where the two eccentric parts 310 are located are equal and the maximum. At this time, the load borne by the side of the crankshaft 300 where the groove 323 is located is the smallest, and the oil film thickness here can be effectively increased.

[0065] Reference Figure 3 As shown, it can be understood that the maximum radial dimension of the connecting section 320 is defined as D, that is, the maximum outer diameter of the connecting section 320 is D, and the maximum linear distance between the two ends of the groove 323 in the circumferential direction of the crankshaft 300 is W, that is, the linear distance between the two ends of the bottom wall 326 in the circumferential direction of the crankshaft 300 is W. It can also be understood that the width of the groove 323 is W, and it satisfies: W / D ≤ 0.7. When the outer diameter D of the connecting section 320 is certain, when W / D > 0.7, the width W of the groove 323 will increase. On the one hand, the distances from the groove 323 to the bearing sides where the two eccentric parts 310 are located become closer. Especially, the edges at the two circumferential ends of the groove 323 along the crankshaft 300 are closer to the bearing sides, and the load borne by the side of the crankshaft 300 where the groove 323 is located is larger, the surface pressure increases, and the oil film thickness here decreases. On the other hand, the bearing area of the crankshaft 300 decreases, the surface pressure increases, which will also cause the oil film thickness to decrease. At the same time, along the direction perpendicular to the bottom wall 326, the depth t of the groove 323 increases, the structural stiffness of the connecting section 320 decreases, the connecting section 320 is prone to deformation, the supporting force of the bearing body 400 on the connecting section 320 is insufficient, affecting the reliability of the rotary compressor, and abnormal wear will occur.

[0066] Reference Figure 8As shown, it can be understood that under the same working conditions, as the ratio W / D increases, the oil film thickness on the side of the crankshaft 300 where the groove 323 is located decreases. When W / D ≤ 0.7, the oil film thickness remains at 2 μm or more. When W / D > 0.7, the oil film thickness is less than 2 μm. Therefore, by making W / D ≤ 0.7, on the premise of increasing lubricity by setting the groove 323, it can be ensured that the width of the groove 323 will not be too large, so that the oil film thickness on the side of the crankshaft 300 where the groove 323 is located is relatively large, so as to maintain good lubricity between the crankshaft 300 and the bearing body 400 and reduce wear. At the same time, it can ensure that the structural stiffness of the connecting section 320 meets the requirements of support and positioning, effectively ensuring the reliability of the rotary compressor.

[0067] Refer to Figure 3 As shown, it can be understood that along the axial direction of the crankshaft 300, the length of the first oil retaining part 324 is defined as L1, and the maximum length of the groove 323 is L2. Since the side wall is perpendicular to the central axis of the crankshaft 300, the maximum length of the groove 323 is also the minimum length of the groove 323. It satisfies: L1 / L2 ≥ 0.25. It is easy to understand that the bearing surface on the side of the crankshaft 300 where the groove 323 is located is mainly the arc surface where the first oil retaining part 324 is located. Along the axial direction of the crankshaft 300, on the premise that the total length of the bearing part on the connecting section 320 is certain, that is, on the premise that the value of (L1 + L2) is certain, when L1 / L2 < 0.25, the length of the groove 323 increases and the length of the first oil retaining part 324 decreases. On the one hand, the area of the arc surface where the first oil retaining part 324 is located decreases, which will lead to a decrease in the bearing area on the side of the crankshaft 300 where the groove 323 is located, an increase in the surface pressure, and a decrease in the oil film thickness here; on the other hand, the structural stiffness of the connecting section 320 decreases, the connecting section 320 is prone to deformation, the supporting force of the bearing body 400 on the connecting section 320 is insufficient, affecting the reliability of the rotary compressor, and abnormal wear will occur.

[0068] Refer to Figure 9 As shown, it can be understood that under the same working conditions, as the ratio L1 / L2 increases, the oil film thickness on the side of the crankshaft 300 where the groove 323 is located increases. When L1 / L2 ≥ 0.25, the oil film thickness remains at 1.6 μm or more. When L1 / L2 < 0.25, the oil film thickness is less than 1.6 μm. Therefore, by making L1 / L2 ≥ 0.25, on the premise of increasing lubricity by setting the groove 323, it can be ensured that the length of the groove 323 will not be too large, while the length of the first oil retaining part 324 is relatively large, so that the oil film thickness on the side of the crankshaft 300 where the groove 323 is located is relatively large, so as to maintain good lubricity between the crankshaft 300 and the bearing body 400 and reduce wear. At the same time, it can ensure that the structural stiffness of the connecting section 320 meets the requirements of support and positioning, effectively ensuring the reliability of the rotary compressor.

[0069] Refer toFigure 5 As shown, in some other embodiments, it can be understood that the groove body 323 includes a bottom wall 326 and two side walls. The bottom wall 326 is a straight wall and is parallel to the central axis of the crankshaft 300. Along the circumferential direction of the crankshaft 300, both ends of the bottom wall 326 extend to the outer peripheral wall of the connecting section 320, that is, the bottom wall 326 is connected to the outer peripheral wall of the connecting section 320, and an edge is formed at the connection between the bottom wall 326 and the outer peripheral wall of the connecting section 320, and the edge is arranged along the axial direction of the crankshaft 300. Along the axial direction of the crankshaft 300, one side wall is connected to the lower end of the bottom wall 326, and the other side wall is connected to the upper end of the bottom wall 326. Both side walls are perpendicular to the central axis of the crankshaft 300, that is, the bottom wall 326 is closer to the central axis of the crankshaft 300 than the side walls, and the bottom wall 326 is rectangular. Therefore, the connecting section 320 forms a first oil retaining portion 324 at the upper end of the groove body 323 and a second oil retaining portion 325 at the lower end of the groove body 323. The first oil retaining portion 324 and the second oil retaining portion 325 protrude relative to the bottom wall 326, so that neither the upper end nor the lower end of the groove body 323 penetrates the connecting section 320. The outer peripheral walls of the connecting section 320 at the first oil retaining portion 324 and the second oil retaining portion 325 are both complete cylindrical surfaces, and the connecting section 320 includes the shaft section where the groove body 323 is located, the shaft section where the first oil retaining portion 324 is located, and the shaft section where the second oil retaining portion 325 is located.

[0070] On the premise of increasing lubricity by setting the groove body 323, due to the existence of the first oil retaining portion 324 and the second oil retaining portion 325, along the radial direction of the crankshaft 300, the bearing surface on the side of the crankshaft 300 where the groove body 323 is located includes the arc surface where the first oil retaining portion 324 is located and the arc surface where the second oil retaining portion 325 is located. Thus, the bearing area on the side of the crankshaft 300 where the groove body 323 is located can be increased, the surface pressure can be reduced, which is beneficial to increasing the oil film thickness at this place, keeping good lubricity between the crankshaft 300 and the bearing body 400, and reducing wear. At this time, under the action of gravity, the lubricating oil flows downward through the gap between the outer peripheral wall of the connecting section 320 and the inner wall of the shaft hole 430, so that the lubricating oil can flow, and thus part of the heat generated during the rotation of the crankshaft 300 can be taken away by the lubricating oil.

[0071] Refer to Figure 2As shown, it can be understood that one end of the central oil hole 330 facing the bearing body 400 is closed, that is, the upper end of the central oil hole 330 is closed, and only the lower end is open. The central oil hole 330 is a blind hole. Therefore, the lubricating oil can only flow out of the central oil hole 330 through the first oil outlet hole 321, so that the lubricating oil cannot be sprayed into the top space of the crankshaft 300, reducing the amount of oil reaching the top space of the crankshaft 300, achieving the reduction of the oil discharge amount of the rotary compressor to maintain the oil level stability of the oil sump and improving the reliability of the rotary compressor. At the same time, the oil discharge amount of the first oil outlet hole 321 can be increased, thereby increasing the minimum oil film thickness between the crankshaft 300 and the bearing body 400, enhancing the lubrication effect, reducing wear, and further improving the reliability of the rotary compressor.

[0072] Referring to Table 2 shown, it is easy to understand that under the same working conditions, in Example 3, the central oil hole 330 penetrates along the axial direction of the crankshaft 300, and both the upper and lower ends of the groove body 323 penetrate through the connecting section 320. At this time, the oil discharge amount ratio of the rotary compressor is 12%; in Example 4, the upper end of the central oil hole 330 is closed, the lower end of the groove body 323 penetrates through the connecting section 320, and a first oil blocking portion 324 is provided at the upper end. At this time, the oil discharge amount ratio of the rotary compressor is 10%, which is smaller than that in Example 3. Therefore, closing the upper end of the central oil hole 330 and providing a first oil blocking portion 324 at the upper end of the groove body 323 can effectively reduce the oil discharge amount of the rotary compressor and improve the reliability of the rotary compressor.

[0073] Table 2: Comparison of Oil Discharge Amount Ratios under Different Schemes

[0074]

[0075] Referring to Figure 6 As shown, in some other embodiments, it can be understood that a second oil outlet hole 322 is provided in the connecting section 320. The second oil outlet hole 322 is located at one end of the connecting section 320 away from the motor assembly 200. The lower end of the second oil outlet hole 322 communicates with the central oil hole 330, and the upper end (i.e., the oil outlet end) of the second oil outlet hole 322 is located on the upper end wall of the connecting section 320, that is, the oil outlet end of the second oil outlet hole 322 communicates with the top space of the crankshaft 300, and the inner diameter of the second oil outlet hole 322 is smaller than the inner diameter of the first oil outlet hole 321 and the inner diameter of the central oil hole 330. Therefore, compared with the central oil hole 330 penetrating along the axial direction of the crankshaft 300, by providing a second oil outlet hole 322 with a smaller inner diameter, most of the lubricating oil in the central oil hole 330 flows out through the first oil outlet hole 321, which can also increase the oil discharge amount of the first oil outlet hole 321, thereby increasing the minimum oil film thickness between the crankshaft 300 and the bearing body 400, enhancing the lubrication effect, reducing wear, and further improving the reliability of the rotary compressor.

[0076] In a second aspect of the embodiments of the present invention, a refrigeration device is provided. The refrigeration device may be an electrical appliance such as an air conditioner or a refrigerator. The refrigeration device includes the rotary compressor according to any of the above embodiments.

[0077] Since the refrigeration device adopts all the technical solutions of the rotary compressor according to the above embodiments, it at least has all the beneficial effects brought by the technical solutions of the above embodiments.

[0078] The embodiments of the present invention have been described in detail above in conjunction with the accompanying drawings. However, the present invention is not limited to the above embodiments. Various changes can be made without departing from the spirit of the present invention within the scope of knowledge possessed by those of ordinary skill in the relevant art.

Claims

1. Rotary compressor, characterized in that, Comprising: A pump body assembly including a cylinder; A motor assembly including a stator and a rotor, the stator being arranged around the rotor; A crankshaft passing through and connected to the rotor, the crankshaft including two eccentric portions and a connecting section, the eccentric directions of the two eccentric portions being opposite, the eccentric portion and the connecting section being respectively located at two ends of the motor assembly along the axial direction of the crankshaft, the eccentric portion being rotatably arranged in the cylinder, the crankshaft being provided with a central oil hole, the connecting section being provided with a first oil outlet hole, the first oil outlet hole communicating with the central guide hole; A bearing body provided with a shaft hole, the bearing body being sleeved on the connecting section through the shaft hole; Wherein, the oil outlet end of the first oil outlet hole faces the gap between the outer peripheral wall of the connecting section and the inner wall of the shaft hole, a groove body is provided on the outer peripheral wall of the connecting section, the groove body communicating with the first oil outlet hole, an oil groove being defined between the groove body and the inner wall of the shaft hole, the groove body including a bottom wall which is a straight wall, the included angle between a reference plane passing through the central axis of the crankshaft and perpendicular to the bottom wall and the eccentric direction of one of the eccentric portions being θ, satisfying: 45° ≤ θ ≤ 135°.

2. The rotary compressor according to claim 1, characterized in that: The first oil outlet hole is arranged along the radial direction of the crankshaft.

3. The rotary compressor according to claim 1 or 2, characterized in that: The groove body includes side walls, the side walls being connected to one end of the bottom wall along the axial direction of the crankshaft, the bottom wall being closer to the central axis of the crankshaft than the side walls, and both circumferential ends of the bottom wall extending to the outer peripheral wall of the connecting section.

4. The rotary compressor according to claim 3, wherein: The maximum radial dimension of the connecting section is D, and the maximum linear distance between the two circumferential ends of the groove body is W, satisfying: W / D ≤ 0.

7.

5. The rotary compressor according to claim 3, wherein: Along the axial direction of the crankshaft, one end of the groove body facing the motor assembly penetrates through the connecting section, the connecting section including a first oil retaining portion located at the other end of the groove body.

6. The rotary compressor according to claim 5, wherein: Along the axial direction of the crankshaft, the length of the first oil retaining portion is L1, and the maximum length of the groove body is L2, satisfying: L1 / L2 ≥ 0.

25.

7. The rotary compressor according to claim 3, characterized in that: The connecting section includes a first oil retaining portion and a second oil retaining portion, the first oil retaining portion and the second oil retaining portion being respectively located at two ends of the groove body along the axial direction of the crankshaft.

8. The rotary compressor according to claim 1, characterized in that: One end of the central oil hole facing the bearing body is closed.

9. The rotary compressor according to claim 1, characterized in that: A second oil outlet hole is provided at one end of the connecting section facing away from the motor assembly, the second oil outlet hole communicating with the central oil hole, and the oil outlet end of the second oil outlet hole being located on the upper end wall of the connecting section, the inner diameter of the second oil outlet hole being smaller than the inner diameter of the first oil outlet hole and the inner diameter of the central oil hole.

10. Refrigeration equipment, characterized in that, Including a rotary compressor according to any one of claims 1 to 9.

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