Compressor

Abstract

The compressor comprises a crankshaft, an auxiliary bearing, a main bearing and an air cylinder, the crankshaft is provided with a main shaft section, an eccentric section and an auxiliary shaft section, and the end face of the auxiliary shaft section is provided with a first thrust face. The auxiliary bearing is provided with a matching hole, the matching hole is used for installing the auxiliary shaft section, a second thrust face is arranged at the inner bottom of the matching hole, and the second thrust face abuts against the first thrust face. The main bearing is provided with a mounting hole for mounting the main shaft section; the air cylinder is arranged on the outer side of the eccentric section and located between the main bearing and the auxiliary bearing. Wherein the crankshaft is provided with a first oil hole and a central oil hole arranged along the central axis, and the auxiliary bearing is provided with a second oil hole. According to the compressor provided by the embodiment of the invention, the interior of the compressor with the crankshaft and the auxiliary bearing adopting an end part abutting structure is convenient to lubricate.

Description

Technical Field

[0001] The present invention relates to the technical field of thermal management, and particularly relates to a compressor. Background Art

[0002] A rotary compressor generally includes a compression mechanism and a motor disposed in a housing. The compression mechanism includes a cylinder, a main bearing, a sub-bearing, a muffler, etc. The main bearing and the sub-bearing are respectively disposed on both sides of the cylinder. The bearing close to the motor side is defined as the main bearing, and the bearing far from the motor side is defined as the sub-bearing. The crankshaft includes a main shaft section, an eccentric section, and a sub-shaft section. The section close to the motor side is defined as the main shaft section. The crankshaft axially penetrates through the sub-bearing, the cylinder, and the main bearing, and the rotor drives the crankshaft to rotate.

[0003] In the related art, the end face of the sub-bearing close to the cylinder is usually used to abut against the crankshaft to facilitate the stable rotation of the crankshaft in the compressor. Due to the existence of the eccentric section of the crankshaft, when the crankshaft rotates, the center of gravity of the moving parts is not on the rotation axis, so a rotational inertial force pointing in the eccentric direction is generated. The eccentric inertial force will increase the vibration and noise of the compressor during operation, affecting the reliability of the refrigeration system and the user's comfort. Summary of the Invention

[0004] An object of the present invention is to provide a compressor, which facilitates lubrication in a compressor having an end abutting structure for a crankshaft and a sub-bearing.

[0005] The compressor according to an embodiment of the present invention includes: a crankshaft, a sub-bearing, a main bearing, and a cylinder. The crankshaft has a main shaft section, an eccentric section, and a sub-shaft section. A first thrust surface is provided on the end face of the sub-shaft section. The sub-bearing has a mating hole for installing the sub-shaft section. A second thrust surface is provided at the inner bottom of the mating hole, and the second thrust surface abuts against the first thrust surface. The main bearing has an installation hole for installing the main shaft section. The cylinder is disposed outside the eccentric section and is located between the main bearing and the sub-bearing. Wherein, the crankshaft is provided with a first oil hole and a central oil hole arranged along the central axis, and the second thrust surface is provided with a second oil hole.

[0006] The compressor according to an embodiment of the present invention facilitates lubrication in a compressor having an end abutting structure for a crankshaft and a sub-bearing.

[0007] In addition, the compressor according to the above embodiment of the present invention may further have the following additional technical features:

[0008] In some embodiments, the first oil hole is provided on the first thrust surface. And / or, the first oil hole is arranged along the central axis, and the axis of the first oil hole coincides with the central axis.

[0009] In some embodiments, the diameter D1 of the central oil hole and the diameter D2 of the first oil hole satisfy: D2 < D1.

[0010] In some embodiments, the second oil hole is provided on the second thrust surface. And / or, the second oil hole is arranged along the central axis.

[0011] In some embodiments, the first oil hole and the second oil hole are arranged along the same center line, and the center line coincides with or is parallel to the central axis of the crankshaft. The diameter D2 of the first oil hole and the diameter D3 of the second oil hole satisfy: D3 = D2; or, D3 < D2; or, D3 > D2.

[0012] In some embodiments, a fourth oil hole and a fifth oil hole are provided on the side wall of the crankshaft. The fourth oil hole and the fifth oil hole are distributed along the central axis, and the fourth oil hole and the fifth oil hole communicate with the central oil hole. The fourth oil hole is farther from the first thrust surface than the fifth oil hole.

[0013] In some embodiments, the fourth oil hole is provided inside the sub-bearing, and the fifth oil hole is provided inside the main bearing.

[0014] In some embodiments, the diameter D4 of the fourth oil hole and the diameter D5 of the fifth oil hole satisfy: D4 = D5.

[0015] In some embodiments, the diameter D5 of the fifth oil hole, the height dimension H2 of the fifth oil hole relative to the end face of the sub-shaft section, and the height dimension H3 of the mating hole satisfy: 0 < H3 - H2; or, 1 / 2 * D5 < H3 - H2.

[0016] In some embodiments, the cylinder height dimension H, the height dimension H1 of the fourth oil hole relative to the end face of the sub-shaft section, the diameter D4 of the fourth oil hole, and the height dimension H3 of the mating hole satisfy: 0 < H1 - H - H3; or, 1 / 2 * D4 < H1 - H - H3.

[0017] In some embodiments, the first oil hole is configured to supply oil to the central oil hole along the radial direction of the sub-shaft section.

[0018] In some embodiments, the sub-bearing includes a shaft portion and balls. The balls are connected to the end of the shaft portion. The first thrust surface is provided on the balls. An oil groove is provided on the end face of the shaft portion. The balls have a mating surface that mates with the end face of the shaft portion, and the first oil hole is formed between the mating surface and the oil groove.

[0019] In some embodiments, a second oil hole that can communicate with the first oil hole is provided on the side wall of the sub-bearing.

[0020] In some embodiments, a first helical groove is provided on the inner wall surface of the mounting hole, and a second helical groove is provided on the inner wall surface of the mating hole. In a cross-section perpendicular to the central axis, the cross-sectional area S1 of the first helical groove and the cross-sectional area S2 of the second helical groove satisfy: π*(1 / 2*D1)^2 > π*(1 / 2*D2)^2 > S1 + S2, where D1 is the diameter dimension of the central oil hole, and D2 is the diameter dimension of the first oil hole.

[0021] In some embodiments, a first helical groove is provided on the inner wall surface of the mounting hole, and a second helical groove is provided on the inner wall surface of the mating hole. In a cross-section perpendicular to the central axis, the cross-sectional area S1 of the first helical groove and the cross-sectional area S2 of the second helical groove satisfy: π*(1 / 2*D1)^2 > π*(1 / 2*D3)^2 > S1 + S2, where D1 is the diameter dimension of the central oil hole, and D3 is the diameter dimension of the second oil hole. Description of the Drawings

[0022] Figure 1 It is a cross-sectional view of a partial structure of a compressor according to an embodiment of the present invention.

[0023] Figure 2 It is a cross-sectional view of the cooperation between a crankshaft and a sub-bearing according to an embodiment of the present invention.

[0024] Figure 3 It is a cross-sectional view of a crankshaft according to an embodiment of the present invention.

[0025] Figure 4 It is a cross-sectional view of a sub-bearing according to an embodiment of the present invention.

[0026] Figure 5 It is a cross-sectional view of a main bearing according to an embodiment of the present invention.

[0027] Figure 6 It is a cross-sectional view of the cooperation between a crankshaft and a sub-bearing according to another embodiment of the present invention.

[0028] Figure 7 It is a schematic diagram of a ball according to another embodiment of the present invention.

[0029] Figure 8 It is a cross-sectional view of the cooperation between a crankshaft and a sub-bearing according to still another embodiment of the present invention.

[0030] Reference Signs:

[0031] 100, Compressor; 10, Crankshaft; 11, Main shaft section; 12, Auxiliary shaft section; 1201, Central oil hole; 1202, First thrust surface; 1203, First oil hole; 1204, Fourth oil hole; 1205, Fifth oil hole; 121, Shaft portion; 122, Ball; 1221, Cylindrical portion; 1222, Spherical portion; 13, Eccentric section; 20, Auxiliary bearing; 201, Fitting hole; 202, Second thrust surface; 203, Second oil hole; 204, Second spiral groove; 21, Bearing body; 20A, Central axis; 22, Thrust seat; 30, Main bearing; 301, Mounting hole; 302, First spiral groove. Detailed implementation manners

[0032] 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 denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below by referring to the drawings are exemplary and are intended to explain the present invention and should not be construed as limiting the present invention.

[0033] Combined with Figure 1 And Figure 2 , the compressor 100 according to an embodiment of the present invention includes: a crankshaft 10, an auxiliary bearing 20, a main bearing 30, and a cylinder. The auxiliary bearing 20 and the main bearing 30 are used to support the crankshaft 10 so that the eccentric section 13 of the crankshaft 10 can rotate stably in the cylinder, so as to drive the piston to reciprocate in the cylinder to compress the fluid.

[0034] Specifically, the crankshaft 10 has a main shaft section 11, an eccentric section 13, and an auxiliary shaft section 12. The end face of the auxiliary shaft section 12 is provided with a first thrust surface 1202. The auxiliary bearing 20 has a fitting hole 201 for installing the auxiliary shaft section 12. The inner bottom of the fitting hole 201 is provided with a second thrust surface 202, and the second thrust surface 202 abuts against the first thrust surface 1202. Among them, Figure 2The crankshaft 10 and the auxiliary bearing 20 are separated in the [description] to facilitate the display of the first thrust surface 1202 and the second thrust surface 202. The crankshaft 10 assembly can utilize the cooperation between the first thrust surface 1202 provided at the end face of the auxiliary shaft section 12 and the second thrust surface 202 of the auxiliary bearing 20 to achieve the thrust function, that is, the thrust is realized at the end of the crankshaft 10. In this way, there is no need to provide a thrust structure at the end face of the eccentric part, or the thrust area of the thrust structure provided at the end face of the eccentric part can be designed to be very small. In addition, the thrust area is not affected by whether the auxiliary bearing 20 has a ring groove, so the thrust surface can be further reduced, and the influence of the crankshaft 10 thrust surface structure on the size of the weight reduction balance hole can be eliminated or reduced. As a result, the weight reduction balance hole provided on the eccentric part of the crankshaft 10 can be made correspondingly larger, so that the eccentric mass of the crankshaft 10 can be minimized while keeping the eccentricity of the crankshaft 10 unchanged. This is beneficial to reducing the weight of the balance block in the compressor 100, and further reducing the vibration and noise during the operation of the compressor 100 while reducing the material cost of the balance block, improving the energy efficiency of the compressor 100, reducing the eccentric wear between the crankshaft 10 and the bearing, and achieving low cost, high energy efficiency and high reliability of the compressor 100.

[0035] In addition, in combination Figure 1 with Figure 5 , the main bearing 30 has a mounting hole 301 for mounting the main shaft section 11, and the cylinder is provided outside the eccentric section 13 and is located between the main bearing 30 and the auxiliary bearing 20; wherein, the crankshaft 10 is provided with a first oil hole 1203 and a central oil hole 1201 arranged along the central axis 20A, and the second oil hole 203 is provided on the second thrust surface 202. The second oil hole 203 can facilitate the lubricating oil to enter between the first thrust surface 1202 and the second thrust surface 202 to achieve lubrication between the first thrust surface 1202 and the second thrust surface 202. The second oil hole 203 can facilitate the lubricating oil to enter the central oil hole 1201, and the central oil hole 1201 can facilitate the lubricating oil to enter other positions in the compressor 100. By providing the first oil hole 1203, the second oil hole 203 and the central oil hole 1201, the circulation of the lubricating oil can be realized, which can facilitate the rotation of the crankshaft 10 and improve the stability of the rotation process of the crankshaft 10.

[0036] According to the compressor 100 of the embodiment of the present invention, the thrust effect between the first thrust surface 1202 and the second thrust surface 202 can be improved, and the stable support of the auxiliary bearing 20 for the auxiliary shaft section 12 can be realized, so as to improve the stability during the rotation of the crankshaft 10 and reduce the influence of the eccentric inertial force of the crankshaft 10, and the stability during the operation of the compressor 100 can be improved. In addition, by providing the first oil hole 1203, the second oil hole 203 and the central oil hole 1201, the circulation of the lubricating oil is facilitated, so as to facilitate the lubrication between the internal components of the compressor 100.

[0037] In addition, at least a part of the first thrust surface 1202 is an arc surface, which may include but is not limited to: the entire surface of the first thrust surface 1202 is an arc surface; a part of the first thrust surface 1202 is set as an arc surface, and the other part is a non-arc surface, etc. During the relative movement of the first thrust surface 1202 and the second thrust surface 202, the arc surface can be used to make the auxiliary shaft section 12 easier to be centered, reduce the influence of the eccentric inertia force of the crankshaft 10, and improve the stability of the relative movement between the crankshaft 10 and the auxiliary bearing 20.

[0038] In order to achieve the stability of the mutual thrust between the first thrust surface 1202 and the second thrust surface 202, the first thrust surface 1202 can be set as an arc surface with a convex middle part, that is, the arc surface is convex in the direction away from the mating hole 201 along the axis A of the auxiliary shaft section 12 in the middle; the first thrust surface 1202 can also be set as an arc surface with a concave middle part, that is, the arc surface is convex in the direction towards the inside of the mating hole 201 along the axis A of the auxiliary shaft section 12 in the middle. In addition, the first thrust surface 1202 can also be set as a flat surface or a wavy surface, etc., and the second thrust surface 202 can be set as a surface adapted to the first thrust surface 1202.

[0039] Such as Figure 1 and Figure 2 , in some embodiments, the first thrust surface 1202 is set as an arc surface with a convex middle part. In this way, the thrust fit between the first thrust surface 1202 and the second thrust surface 202 can further improve the fit stability between the crankshaft 10 and the auxiliary bearing 20. In addition, the second thrust surface 202 is set as an arc adapted to the first thrust surface 1202. Among them, the radian of the second thrust surface 202 can be different or the same as that of the first thrust surface 1202. For example, if the first thrust surface 1202 is set as an arc surface with a convex middle part, the second thrust surface 202 can also be set as an arc surface with a convex middle part. Of course, the second thrust surface 202 can also be set as a flat surface.

[0040] Optionally, in some embodiments, the first thrust surface 1202 is set as a rotating surface centered on the axis A of the crankshaft 10, and at least a part of the generatrix of the rotating surface forms an angle less than 90° with the axis A. When the first thrust surface 1202 cooperates with the second thrust surface 202, during the rotation of the auxiliary shaft section 12 relative to the auxiliary bearing 20, the rotating surface is beneficial to the centering of the crankshaft 10 and improves the stability of the cooperation between the first thrust surface 1202 and the second thrust surface 202. Among them, the generatrix of the rotating surface can be a straight line segment, an arc segment, or a combination of a straight line segment and an arc segment, etc.

[0041] The first oil hole 1203 in the present invention can be arranged at positions such as the side wall and end face of the crankshaft 10. In some embodiments, the first oil hole 1203 is arranged on the first thrust surface 1202. This can simplify the structure of the crankshaft 10 and facilitate the lubricating oil to enter the central oil hole 1201 through the first oil hole 1203. In addition, it can also facilitate the lubricating oil to enter between the first thrust surface 1202 and the second thrust surface 202, realize the lubrication of the relative movement between the first thrust surface 1202 and the second thrust surface 202, effectively improve the operation stability of the compressor 100, realize the rapid heat dissipation of the internal components of the compressor 100, and improve the energy efficiency of the compressor 100.

[0042] In addition, as Figure 1 , the first oil hole 1203 can be arranged along the central axis 20A. The axis of the first oil hole 1203 can also coincide with the central axis 20A. In this way, it can further facilitate the lubricating oil to enter the central oil hole 1201 from the first oil hole 1203, improve the fluidity of the lubricating oil, realize the rapid circulation of the lubricating oil, and rapidly lubricate and dissipate heat from the components in a short time.

[0043] In some embodiments, as Figure 3 , the diameter dimension D1 of the central oil hole 1201 and the diameter dimension D2 of the first oil hole 1203 satisfy: D2 < D1. This can improve the suction force of the oil at the first oil hole 1203, so that the oil can quickly enter the central oil hole 1201 through the first oil hole 1203, realizing the rapid circulation of the lubricating oil.

[0044] In addition, combining the foregoing embodiments, combining Figures 1 to 3 , when the first oil hole 1203 is arranged on the first thrust surface 1202, the crankshaft 10 can be divided into a main shaft portion 121 and a ball 122. The ball 122 can be installed at the end of the main shaft portion 121. The diameter dimension of the first oil hole 1203 is smaller than the diameter dimension of the central oil hole 1201, which can conveniently improve the installation stability of the ball 122 on the main shaft portion 121 and the strength of the connection structure.

[0045] In some embodiments, combining Figure 1 、 Figure 2 and Figure 4 , the second oil hole 203 is arranged on the second thrust surface 202. This can simplify the structure of the auxiliary bearing 20 and facilitate the lubricating oil to enter between the first thrust surface 1202 and the second thrust surface 202 through the second oil hole 203, realize the lubrication of the relative movement between the first thrust surface 1202 and the second thrust surface 202, effectively improve the operation stability of the compressor 100, realize the rapid heat dissipation of the internal components of the compressor 100, and improve the energy efficiency of the compressor 100.

[0046] In addition, the second oil hole 203 can be arranged along the central axis 20A. The axis of the second oil hole 203 can also coincide with the central axis 20A. In this way, it is further convenient for lubricating oil to enter between the first thrust surface 1202 and the second thrust surface 202 through the second oil hole 203, improving the fluidity of the lubricating oil, realizing the rapid circulation of the lubricating oil, and quickly lubricating and dissipating heat from the components in a short time.

[0047] In some embodiments, such as Figure 1 , the first oil hole 1203 and the second oil hole 203 are arranged along the same center line, the center line coincides with or is parallel to the central axis 20A of the crankshaft 10, and the diameter dimension D2 of the first oil hole 1203 and the diameter dimension D3 of the second oil hole 203 satisfy: D3 = D2. It is convenient for lubricating oil to enter the central oil hole 1201 through the first oil hole 1203 and the second oil hole 203, realizing the rapid circulation of the lubricating oil. Moreover, the first oil hole 1203 and the second oil hole 203 can have good suction force to improve the circulation efficiency of the lubricating oil and reduce the flow resistance during the flow of the lubricating oil.

[0048] In addition, the diameter dimension D2 of the first oil hole 1203 and the diameter dimension D3 of the second oil hole 203 can also be set as D3 < D2; or D3 > D2. In this way, the suction force of the first oil hole 1203 and the second oil hole 203 can be further improved, and the flow rate of the lubricating oil after entering the central oil hole 1201 can be simplified, so as to facilitate the lubricating oil to enter from the central oil hole 1201 between the crankshaft 10 and the main bearing 30, as well as between the crankshaft 10 and the auxiliary bearing 20, improving the lubrication and heat dissipation effects.

[0049] Such as Figure 1 and Figure 3 , in some embodiments, the side wall of the crankshaft 10 is provided with a fourth oil hole 1204 and a fifth oil hole 1205. The fourth oil hole 1204 and the fifth oil hole 1205 are distributed along the central axis 20A, and the fourth oil hole 1204 and the fifth oil hole 1205 communicate with the central oil hole 1201. The fourth oil hole 1204 is farther from the first thrust surface 1202 than the fifth oil hole 1205. By providing the fourth oil hole 1204 and the second oil hole 203, it is convenient for the lubricating oil in the central oil hole 1201 to be discharged, so as to provide lubrication for the outer peripheral surface of the crankshaft 10, facilitate the rotation of the crankshaft 10, improve the stability of the crankshaft 10 during rotation, and thus improve the energy efficiency of the compressor 100. In addition, it is also convenient for the lubricating oil to form a stable circulation channel, facilitating the use of the lubricating oil to lubricate the inside of the compressor 100.

[0050] Among them, the fourth oil hole 1204 is provided inside the auxiliary bearing 20, and the fifth oil hole 1205 is provided inside the main bearing 30. The lubricating oil in the central oil hole 1201 can be introduced between the auxiliary bearing 20 and the crankshaft 10 through the fourth oil hole 1204, and the lubricating oil in the central oil hole 1201 can enter between the main bearing 30 and the crankshaft 10 through the fifth oil hole 1205, so as to effectively lubricate the crankshaft 10, the main bearing 30 and the auxiliary bearing 20, facilitate the rotation of the crankshaft 10, and improve the performance of the compressor 100.

[0051] In addition, in combination with Figure 4 and Figure 5 , in other embodiments of the present invention, a first spiral groove 302 is provided. The first spiral groove 302 can be provided on the inner wall surface of the mounting hole 301. At this time, after the lubricating oil enters the fifth oil hole 1205 from the central oil hole 1201, it will be discharged between the main bearing 30 and the crankshaft 10 through the fifth oil hole 1205. When the crankshaft 10 rotates relative to the main bearing 30 to make the fifth oil hole 1205 opposite to the first spiral groove 302, the lubricating oil can enter the first spiral groove 302 and cover between the crankshaft 10 and the main bearing 30 after being discharged from the first spiral groove 302, thereby improving the lubrication effect between the main bearing 30 and the crankshaft 10. In other embodiments of the present invention, a second spiral groove 204 is provided. The second spiral groove 204 can be provided on the inner wall surface of the mating hole 201. At this time, after the lubricating oil enters the fourth oil hole 1204 from the central oil hole 1201, it will be discharged between the auxiliary bearing 20 and the crankshaft 10 through the fourth oil hole 1204. When the crankshaft 10 rotates relative to the auxiliary bearing 20 to make the fourth oil hole 1204 opposite to the second spiral groove 204, the lubricating oil can enter the second spiral groove 204 and cover between the crankshaft 10 and the auxiliary bearing 20 after being discharged from the second spiral groove 204, thereby improving the lubrication effect between the auxiliary bearing 20 and the crankshaft 10.

[0052] Such as Figure 3 , the diameter dimension D4 of the fourth oil hole 1204 and the diameter dimension D5 of the fifth oil hole 1205 satisfy: D4 = D5. It can facilitate the lubricating oil in the central oil hole 1201 to be sent out relatively evenly from the fourth oil hole 1204 and the fifth oil hole 1205, so as to improve the lubrication effect between the crankshaft 10, the auxiliary bearing 20 and the main bearing 30. In addition, the eccentric inertial forces between the crankshaft 10 and the auxiliary bearing 20 and between the crankshaft 10 and the main bearing 30 are balanced, effectively improving the operating stability of the compressor 100.

[0053] Among them, the diameter dimension D5 of the fifth oil hole 1205, the height dimension H2 of the fifth oil hole 1205 relative to the end face of the secondary shaft section 12, and the height dimension H3 of the mating hole 201 can satisfy: 0 < H3 - H2; or, 1 / 2 * D5 < H3 - H2. This can improve the lubrication effect of the lubricating oil between the crankshaft 10 and the secondary bearing 20, thereby facilitating the stable rotation of the crankshaft 10 within the mating hole 201 and improving the stability and energy efficiency of the compressor 100.

[0054] Among them, the cylinder height dimension H of the cylinder, the height dimension H1 of the fourth oil hole 1204 relative to the end face of the secondary shaft section 12, the diameter dimension D4 of the fourth oil hole 1204, and the height dimension H3 of the mating hole 201 satisfy: 0 < H1 - H - H3; or, 1 / 2 * D4 < H1 - H - H3. This can improve the lubrication effect of the lubricating oil between the crankshaft 10 and the main bearing 30, thereby facilitating the stable rotation of the crankshaft 10 within the mounting hole 301 and improving the stability and energy efficiency of the compressor 100.

[0055] In addition, the first oil hole 1203 in the present invention may not be provided on the first thrust surface 1202.

[0056] Such as Figures 6 to 8 , in some embodiments, the first oil hole 1203 is configured to supply oil to the central oil hole 1201 along the radial direction of the secondary shaft section 12. This facilitates the lubricating oil circulation, so as to facilitate the lubrication and heat dissipation between the internal components of the compressor 100.

[0057] Such as Figure 3 , in some embodiments, the secondary bearing 20 includes a shaft portion 121 and a ball 122. The ball 122 is connected to the end of the shaft portion 121, and the first thrust surface 1202 is provided on the ball 122. This can simplify the production process of the crankshaft 10, improve the production efficiency of the secondary shaft section 12. In addition, it can also reduce the processing cost of the crankshaft 10.

[0058] Among them, in some examples, the ball 122 may include a cylindrical portion 1221 and a spherical portion 1222. The shaft portion 121 may have a central oil hole. The cylindrical portion 1221 may pass through the central oil hole. The spherical portion 1222 is connected to the cylindrical portion 1221 and is provided outside the end face of the shaft portion 121. The first thrust surface 1202 is provided on the side of the spherical portion 1222 facing away from the shaft portion 121. The cooperation between the cylindrical portion 1221 and the central oil hole can be utilized to achieve the stable connection between the ball 122 and the shaft portion 121, and improve the connection efficiency and stability between the ball 122 and the shaft portion 121.

[0059] In some other examples, the ball 122 is a sphere, and the ball 122 is installed at the end of the shaft portion 121. The spherical surface of the ball 122 is configured as the first thrust surface 1202. When the secondary shaft segment 12 is engaged with the secondary bearing 20, the shaft portion 121 passes through the mating hole 201. The ball 122 is disposed at the end of the shaft portion 121, and the ball 122 is located between the shaft portion 121 and the secondary bearing 20 along the axis A of the shaft portion 121. The ball 122 can be slidably engaged with the end of the secondary shaft segment 12; alternatively, the ball 122 can be slidably engaged with the second thrust surface 202 housing. Additionally, the ball 122 can be fixedly connected to the end of the secondary shaft segment 12.

[0060] In still some other examples, the crankshaft 10 and the first thrust surface 1202 are integrally machined. Integrally forming the first thrust surface 1202 on the crankshaft 10 can simplify the production efficiency and stability of the crankshaft 10. Additionally, it can also simplify the structure of the crankshaft 10, facilitating the centering of the crankshaft 10 when the first thrust surface 1202 and the second thrust surface 202 are in thrust engagement.

[0061] In addition, as Figure 6 shown, an oil groove is provided on the end face of the shaft portion 121. The ball 122 has a mating surface that mates with the end face of the shaft portion 121. A first oil hole 1203 is formed between the mating surface and the oil groove. Different from the aforementioned arrangement of the first oil hole in the first thrust surface 1202, the first oil hole 1203 can be constructed using the oil groove on the end face of the shaft portion 121 and connected to the central oil hole 1201 to achieve the introduction of lubricating oil into the central oil hole 1201. Among them, the oil groove can be arranged to supply oil to the central oil hole 1201 along the radial direction of the shaft portion 121 (or the radial direction of the crankshaft).

[0062] Optionally, as Figure 8 shown, a second oil hole 203 that can communicate with the first oil hole 1203 is provided on the side wall of the secondary bearing 20. Thus, it is convenient for the lubricating oil in the oil sump to be introduced into the central oil hole 1201. Among them, the second oil hole 203 provided on the side wall of the secondary bearing 20 can be arranged to: always communicate with the first oil hole 1203; or communicate with the first oil hole 1203 when the crankshaft rotates to a predetermined position, etc.

[0063] Combining the foregoing embodiments, the first oil hole 1203 in the present invention can be arranged to supply oil to the central oil hole along the radial direction or the axis of the crankshaft; the second oil hole 203 can also be arranged to supply oil into the mating hole along the radial direction or the axial direction of the secondary bearing.

[0064] For example, a first oil hole 1203 for radial oil inlet is provided at the end of the secondary shaft segment, and a second oil hole 203 for axial oil inlet is provided on the second thrust surface 202;

[0065] Alternatively, a first oil hole 1203 for axial oil inlet is provided on the first thrust surface 1202, and a second oil hole 203 for radial oil inlet is provided on the side wall of the auxiliary bearing 20;

[0066] Alternatively, a first oil hole 1203 for radial oil inlet is provided at the end of the auxiliary shaft section, a first oil hole 1203 for axial oil inlet is provided on the first thrust surface 1202, a second oil hole 203 for axial oil inlet is provided on the second thrust surface 202, and a second oil hole 203 for radial oil inlet is provided on the side wall of the auxiliary bearing 20.

[0067] Of course, the above description is only some embodiments of the present invention and does not limit the protection scope of the present invention. There may be other embodiments in the present invention, which will not be elaborated herein.

[0068] Such as Figure 7 , wherein the ball 122 may include a cylindrical portion and a spherical portion. The cylindrical portion is inserted into the shaft portion 121, and the cylindrical portion has a notch corresponding to the oil groove to facilitate the communication between the oil groove and the central oil hole.

[0069] Optionally, the auxiliary bearing 20 may include a bearing body 21 and a thrust seat 22. The mating hole 201 is provided in the bearing body 21, the thrust seat 22 is connected to the bearing body 21, and the second thrust surface 202 is provided on the thrust seat 22 and is opposite to the mating hole 201. It is convenient to construct the second thrust surface 202 on the thrust seat 22, which can simplify the structure of the auxiliary bearing 20.

[0070] In some embodiments, the hardness HR of the first thrust surface 1202 and / or the second thrust surface 202 satisfies: HR > 20 HRC. It can achieve the stable cooperation between the first thrust surface 1202 and the second thrust surface 202, and reduce the wear of the first thrust surface 1202 and the second thrust surface 202 during the rotation of the crankshaft 10 relative to the auxiliary bearing 20, thereby prolonging the service life of the crankshaft 10 assembly.

[0071] Such as Figure 4 and Figure 5, in some embodiments, a first helical groove 302 is provided on the inner wall surface of the mounting hole 301, and a second helical groove 204 is provided on the inner wall surface of the mating hole 201. In a cross-section perpendicular to the central axis 20A, the cross-sectional area S1 of the first helical groove 302 and the cross-sectional area S2 of the second helical groove 204 satisfy: π*(1 / 2*D1)^2 > π*(1 / 2*D2)^2 > S1 + S2, where D1 is the diameter dimension of the central oil hole 1201, and D2 is the diameter dimension of the first oil hole 1203. This can facilitate the suction of lubricating oil from the first oil hole 1203 into the central oil hole 1201. After the lubricating oil enters the central oil hole 1201, due to the change in the flow area, the flow rate of the lubricating oil slows down, which can facilitate the relatively uniform introduction of the lubricating oil into the first helical groove 302 and the second helical groove 204. Moreover, the sum of the cross-sectional areas of the first helical groove 302 and the second helical groove 204 is relatively small, which can facilitate the lubricating oil to fill the first helical groove 302 and the second helical groove 204, so that the lubricating oil in the first helical groove 302 can cover the surface between the main bearing 30 and the crankshaft 10, and the lubricating oil in the second helical groove 204 can cover the surface between the sub-bearing 20 and the crankshaft 10.

[0072] Such as Figure 4 and Figure 5 , in some embodiments, a first helical groove 302 is provided on the inner wall surface of the mounting hole 301, and a second helical groove 204 is provided on the inner wall surface of the mating hole 201. In a cross-section perpendicular to the central axis 20A, the cross-sectional area S1 of the first helical groove 302 and the cross-sectional area S2 of the second helical groove 204 satisfy: π*(1 / 2*D1)^2 > π*(1 / 2*D3)^2 > S1 + S2, where D1 is the diameter dimension of the central oil hole 1201, and D3 is the diameter dimension of the second oil hole 203. This can facilitate the suction of lubricating oil from the second oil hole 203 into the central oil hole 1201. After the lubricating oil enters the central oil hole 1201, due to the change in the flow area, the flow rate of the lubricating oil slows down, which can facilitate the relatively uniform introduction of the lubricating oil into the first helical groove 302 and the second helical groove 204. Moreover, the sum of the cross-sectional areas of the first helical groove 302 and the second helical groove 204 is relatively small, which can facilitate the lubricating oil to fill the first helical groove 302 and the second helical groove 204, so that the lubricating oil in the first helical groove 302 can cover the surface between the main bearing 30 and the crankshaft 10, and the lubricating oil in the second helical groove 204 can cover the surface between the sub-bearing 20 and the crankshaft 10.

[0073] The above-mentioned compressor 100 of the present invention can not only ensure the stiffness of the crankshaft 10, but also maximize the size of the weight-reducing balance holes. Of course, the above-mentioned values are not limited to the above specific ranges and can be reasonably designed and adjusted according to parameters such as the size of the compressor 100. In addition, the compressor 100 can have counterweight balance holes, and the weight-reducing balance holes can be arranged on the end face of the eccentric part of the crankshaft 10, and the cross-section of the weight-reducing balance holes is formed by one or more non-connected circles with the same or different radii.

[0074] On the premise of ensuring the stiffness of the eccentric part of the crankshaft 10, the weight-reducing balance holes can be composed of one or more round holes with equal or different diameters. Preferably, the weight-reducing balance holes are composed of multiple round holes with different diameters to destroy the structural symmetry of the eccentric part, so as to better reduce the eccentric inertial force and make the structural stiffness of the eccentric part better.

[0075] Preferably, the weight-reducing balance holes are arranged on the end face of the eccentric part, and the cross-section of the weight-reducing balance holes is crescent-shaped. The center of the first arc of the crescent shape coincides with the central axis 20AA of the eccentric part, and the center of the second arc of the crescent shape coincides with the central axis 20AA of the main shaft section 11. It is possible to further increase the size of the weight-reducing balance holes on the premise of ensuring the stiffness of the eccentric part of the crankshaft 10, thereby further reducing the eccentric mass of the crankshaft 10, better reducing the eccentric inertial force, and being more conducive to reducing the weight of the balance block in the compressor 100.

[0076] The radius of the second arc of the crescent shape is equal to the radius of the secondary shaft section 12 to maximize the size of the weight-reducing balance holes, thereby maximizing the reduction of the eccentric mass of the crankshaft 10.

[0077] Preferably, the eccentric part has a second end face facing the main shaft section 11, and the weight-reducing balance hole is a through hole penetrating the first end face and the second end face. The weight-reducing balance hole is designed as a through hole penetrating the eccentric part along the axial direction to better reduce the eccentric mass of the crankshaft 10 along the entire axial direction, thereby better reducing the eccentric inertial force.

[0078] According to the heat management system of the embodiment of the present invention, it includes the aforementioned compressor 100. Among them, the heat management system can also include a condenser, an evaporator, a throttle valve, etc. The exhaust cavity of the compressor 100, the condenser, the throttle valve, the evaporator and the suction cavity of the compressor 100 are connected to form a refrigerant circuit to facilitate temperature adjustment by using the phase change of the refrigerant.

[0079] In addition, the evaporator can have a first flow channel, and a heat exchange medium can be introduced into the first flow channel to facilitate refrigerating the heat exchange medium in the first flow channel by using the evaporator; the condenser can have a second flow channel, and a heat exchange medium can be introduced into the second flow channel to facilitate heating the heat exchange medium in the second flow channel by using the condenser.

[0080] In addition, the present invention further provides a vehicle, which may include the aforementioned thermal management system. Among them, the thermal management system may be in heat exchange flow paths with a battery heat exchange flow path, an electronic control heat exchange flow path, a heat exchanger flow path, an air conditioner flow path, etc. in the vehicle, so as to utilize a heat exchange medium to exchange heat in the flow paths between the thermal management system and the vehicle.

[0081] In the description of the present invention, it should be understood that the orientation or positional relationship indicated by the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc. 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, and thus should not be construed as a limitation of the present invention.

[0082] In addition, the terms "first" and "second" are only used for descriptive purposes and cannot be understood as indicating or implying relative importance or implicitly specifying the quantity of the indicated technical features. Thus, the features defined with "first" and "second" may explicitly or implicitly include at least one of such features. In the description of the present invention, "a plurality of" means at least two, such as two, three, etc., unless otherwise specifically and clearly defined.

[0083] In the present invention, unless otherwise clearly specified and limited, the terms "mounted", "connected", "connected to", "fixed", etc. should be understood in a broad sense. For example, it may be a fixed connection, a detachable connection, or integrated; it may be a mechanical connection or an electrical connection; it may be directly connected or indirectly connected through an intermediate medium, and it may be the internal communication of two elements or the interaction relationship between two elements, unless otherwise clearly limited. 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.

[0084] In the present invention, unless otherwise clearly specified and limited, the first feature being "on" or "under" the second feature may be that the first and second features are in direct contact, or the first and second features are indirectly in contact through an intermediate medium. Moreover, the first feature being "above", "over" and "on" the second feature may be that the first feature is directly above or obliquely above the second feature, or merely indicates that the first feature has a higher horizontal height than the second feature. The first feature being "under", "below" and "beneath" the second feature may be that the first feature is directly below or obliquely below the second feature, or merely indicates that the first feature has a lower horizontal height than the second feature.

[0085] In the description of this specification, the descriptions referring to terms such as "one embodiment", "some embodiments", "examples", "specific examples", or "some examples", 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 invention. In this specification, the schematic expressions of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials, or characteristics described can be combined in a suitable manner in any one or more embodiments or examples. In addition, without contradiction, those skilled in the art can combine and combine the different embodiments or examples described in this specification and the features of different embodiments or examples.

[0086] Although the embodiments of the present invention have been shown and described above, it can be understood that the above embodiments are exemplary and should not be construed as limiting the present invention. Those of ordinary skill in the art can make changes, modifications, substitutions, and variations to the above embodiments within the scope of the present invention.

Claims

1. A compressor (100), characterized in that, Comprising: A crankshaft (10), the crankshaft (10) having a main shaft section (11), an eccentric section (13), and a secondary shaft section (12), and a first thrust surface (1202) being provided on an end face of the secondary shaft section (12); A secondary bearing (20), the secondary bearing (20) having a mating hole (201) for mounting the secondary shaft section (12), a second thrust surface (202) being provided at an inner bottom of the mating hole (201), and the second thrust surface (202) abutting against the first thrust surface (1202); A main bearing (30), the main bearing (30) having a mounting hole (301) for mounting the main shaft section (11); A cylinder, the cylinder being provided outside the eccentric section (13) and located between the main bearing (30) and the secondary bearing (20); Wherein, the crankshaft (10) is provided with a first oil hole (1203) and a central oil hole (1201) arranged along a central axis (20A), and the secondary bearing (20) is provided with a second oil hole (203).

2. The compressor (100) according to claim 1, characterized in that, The first oil hole (1203) is provided on the first thrust surface (1202); and / or, the first oil hole (1203) is arranged along the central axis (20A), and an axis of the first oil hole (1203) coincides with the central axis (20A).

3. The compressor (100) according to claim 1 or 2, characterized in that, A diameter dimension D1 of the central oil hole (1201) and a diameter dimension D2 of the first oil hole (1203) satisfy: D2 < D1.

4. The compressor (100) according to claim 1, characterized in that, The second oil hole (203) is provided on the second thrust surface (202); and / or, the second oil hole (203) is arranged along the central axis (20A).

5. The compressor (100) according to claim 1 or 4, characterized in that, The first oil hole (1203) and the second oil hole (203) are arranged along the same center line, the center line coincides with or is parallel to the central axis (20A) of the crankshaft (10), and a diameter dimension D2 of the first oil hole (1203) and a diameter dimension D3 of the second oil hole (203) satisfy: D3 = D2; or, D3 < D2; or, D3 > D2.

6. The compressor (100) according to claim 1, characterized in that, A side wall of the crankshaft (10) is provided with a fourth oil hole (1204) and a fifth oil hole (1205), the fourth oil hole (1204) and the fifth oil hole (1205) are distributed along the central axis (20A), the fourth oil hole (1204) and the fifth oil hole (1205) communicate with the central oil hole (1201), and the fourth oil hole (1204) is farther from the first thrust surface (1202) than the fifth oil hole (1205).

7. The compressor (100) according to claim 6, characterized in that, The fourth oil hole (1204) is provided inside the secondary bearing (20), and the fifth oil hole (1205) is provided inside the main bearing (30); and / or, a diameter dimension D4 of the fourth oil hole (1204) and a diameter dimension D5 of the fifth oil hole (1205) satisfy: D4 = D5.

8. The compressor (100) according to claim 6, characterized in that, The diameter dimension D5 of the fifth oil hole (1205), the height dimension H2 of the fifth oil hole (1205) relative to the end face of the secondary shaft section (12), and the height dimension H3 of the mating hole (201) satisfy: 0 < H3 - H2; or, 1 / 2 * D5 < H3 - H2; And / or, the cylinder height dimension H of the cylinder, the height dimension H1 of the fourth oil hole (1204) relative to the end face of the secondary shaft section (12), the diameter dimension D4 of the fourth oil hole (1204), and the height dimension H3 of the mating hole (201) satisfy: 0 < H1 - H - H3; or, 1 / 2 * D4 < H1 - H - H3.

9. The compressor (100) according to claim 1, wherein, The first oil hole (1203) is configured to supply oil to the central oil hole (1201) along the radial direction of the secondary shaft section (12).

10. The compressor (100) according to claim 9, characterized in that, The auxiliary bearing (20) includes a shaft portion (121) and a ball (122). The ball (122) is connected to the end of the shaft portion (121). The first thrust surface (1202) is provided on the ball (122). An oil groove is provided on the end face of the shaft portion (121). The ball (122) has a mating surface that mates with the end face of the shaft portion (121). The first oil hole (1203) is formed between the mating surface and the oil groove.

11. The compressor (100) according to claim 9, wherein a second oil hole (203) that can communicate with the first oil hole (1203) is provided on the side wall of the auxiliary bearing (20).

12. The compressor (100) according to claim 1, wherein, A first spiral groove (302) is provided on the inner wall surface of the mounting hole (301), and a second spiral groove (204) is provided on the inner wall surface of the mating hole (201). In a cross-section perpendicular to the central axis (20A), the cross-sectional area S1 of the first spiral groove (302) and the cross-sectional area S2 of the second spiral groove (204) satisfy: π * (1 / 2 * D1)^2 > π * (1 / 2 * D2)^2 > S1 + S2, where D1 is the diameter dimension of the central oil hole (1201), and D2 is the diameter dimension of the first oil hole (1203).

13. The compressor (100) according to claim 1, characterized in that, A first spiral groove (302) is provided on the inner wall surface of the mounting hole (301), and a second spiral groove (204) is provided on the inner wall surface of the mating hole (201). In a cross-section perpendicular to the central axis (20A), the cross-sectional area S1 of the first spiral groove (302) and the cross-sectional area S2 of the second spiral groove (204) satisfy: π * (1 / 2 * D1)^2 > π * (1 / 2 * D3)^2 > S1 + S2, where D1 is the diameter dimension of the central oil hole (1201), and D3 is the diameter dimension of the second oil hole (203).

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