Scroll compressor, air conditioning apparatus, and vehicle

Abstract

The application discloses a scroll compressor, air conditioning equipment and a vehicle. The scroll compressor comprises a high-pressure side, a support, a bearing mounted on the support, and a crankshaft with one end mounted on the bearing; characterized in that a groove is formed on the support, a sealing element abutting against an inner ring end surface of the bearing is arranged in the groove, a communication passage of medium is arranged between the groove and the high-pressure side, and the medium makes the sealing element thrust against the inner ring end surface of the bearing. After long-term use, when the surface of the sealing element in contact with the bearing is worn, the sealing element can continuously float to be close to the inner ring of the bearing due to the effect of the buoyancy provided by the medium (such as high-pressure lubricating oil), and is not easy to affect the sealing performance due to the decrease of the height caused by the wear of the sealing element, so that the stable work of the scroll compressor for a long time can be ensured, and the reliability of the scroll compressor is improved.

Description

Technical Field

[0001] This application relates to the field of air conditioning equipment, and more particularly to a scroll compressor, air conditioning equipment, and vehicle. Background Technology

[0002] In existing scroll compressors, a sealing assembly is typically used to seal the crankshaft and bearing housing, and lubricating oil is stored in the bearing housing to lubricate the bearing (not shown in the figure) located in the bearing housing. Figure 1 This is a partial cross-sectional view of the crankshaft and bearing housing assembly of a scroll compressor in the prior art, such as... Figure 1 As shown, the sealing assembly 500 is composed of an elastic part 500a, a rigid part 500b, and an elastic sealing part 500c. The elastic part 500a is interference-fitted with the bearing housing bore 100d to achieve the positioning of the sealing assembly. The elastic sealing part 500c is interference-fitted with the crankshaft 300 to form a seal, thereby preventing the lubricating oil stored in the bearing housing from leaking through the gap between the crankshaft 100 and the bearing housing.

[0003] However, due to the influence of the high temperature and high pressure lubricating oil in the bearing housing, the aforementioned elastic seal 500c will gradually age and wear after working for a certain period of time, resulting in a gap between the crankshaft 300 and the elastic seal 500c. This causes the seal between the crankshaft 300 and the elastic seal 500c to fail, and the lubricating oil in the bearing housing will leak through the gap between the crankshaft 100 and the bearing housing. As a result, the bearing in the bearing housing will not be effectively lubricated due to lack of oil, which will lead to increased power consumption of the scroll compressor, reduced cooling efficiency, and even serious functional failure. Summary of the Invention

[0004] The purpose of this application is to provide a scroll compressor, air conditioning equipment and vehicle, which aims to solve the technical problem in the prior art that the sealing structure between the crankshaft and the bearing housing is prone to failure, which leads to the leakage of lubricating oil in the bearing housing through the gap between the crankshaft and the bearing housing.

[0005] To achieve this objective, the embodiments of this application adopt the following technical solutions:

[0006] A scroll compressor includes a high-pressure side, a bracket, a bearing mounted on the bracket, and a crankshaft with one end mounted on the bearing; characterized in that the bracket has a groove, and a seal is provided in the groove to abut against the inner ring end face of the bearing; a medium communication channel is provided between the groove and the high-pressure side, and the medium causes the seal to resist the inner ring end face of the bearing.

[0007] In one embodiment, the groove is provided with an elastic support; one side of the elastic support is in abutment with the groove bottom, and the other side of the elastic support is in abutment with the sealing element. The elastic support can be deformed along the groove depth direction; when the pressure difference between the lubricating oil in the mounting groove and the low-pressure cavity is small, the elastic thrust of the elastic support can push the sealing element to abut against the inner ring of the bearing, so that the sealing performance of the sealing element is maintained well during the change of the pressure of the lubricating oil. Meanwhile, in the case that the surface of the sealing element in contact with the inner ring of the bearing is worn, the deformation capacity of the elastic support can cooperate with the buoyancy of the lubricating oil to push the sealing element to tightly abut against the inner ring of the bearing.

[0008] In one embodiment, the groove bottom of the mounting groove has a first table surface and a second table surface, the second table surface is more protruded from the groove bottom of the mounting groove than the first table surface; the groove is provided in the first table surface; the outer ring of the bearing is in abutment with the second table surface; and a communication gap is formed between the first table surface and the end surface of the inner ring of the bearing. Since the communication gap d is formed between the first table surface and the end surface of the inner ring of the bearing, the sealing element can be floated to partially protrude from the groove and abut against the inner ring of the bearing, at this time, a certain gap is formed between the end of the sealing element away from the inner ring of the bearing and the groove bottom, at this time, a certain amount of lubricating oil can be accommodated in the gap between the sealing element and the groove bottom, and the part of the lubricating oil can continuously provide the buoyancy of the sealing element along the axial direction of the crankshaft, so that the sealing element continuously abuts against the inner ring of the bearing.

[0009] In one embodiment, the width d of the communication gap satisfies: 0 mm < d ≤ 5 mm.

[0010] In one embodiment, the height h of the sealing element is greater than or equal to the communication gap d.

[0011] In one embodiment, the width W1 of the sealing element is less than the width W2 of the groove.

[0012] In one embodiment, the groove is a circular ring groove, the inner diameter D1 of the groove is greater than or equal to the inner diameter D2 of the inner ring of the bearing, and the inner diameter D1 of the groove is less than or equal to the outer diameter D3 of the inner ring of the bearing, so that the sealing element has sufficient overlap area between the radial direction of the crankshaft and the inner ring of the bearing, and the contact area between the sealing element and the inner ring of the bearing is large enough to ensure that the sealing element applies good sealing to the inner ring of the bearing.

[0013] In one embodiment, the inner diameter D1 of the groove and the inner diameter D2 of the inner ring of the bearing satisfy: D2 + 0.2 ≤ D1.

[0014] In one embodiment, the surface of the sealing element is provided with a wear-resistant layer.

[0015] In one embodiment, the outer ring of the bearing is fixedly installed on the inner side wall of the installation groove.

[0016] In one embodiment, the scroll compressor further comprises a low-pressure shell, a moving scroll connected with the crankshaft, a stationary scroll matched with the moving scroll, and an oil-gas separation assembly installed on the stationary scroll; the low-pressure shell has a low-pressure cavity, the bracket is installed on the low-pressure shell, and the pressure of the hydraulic oil in the installation groove is greater than the pressure in the low-pressure cavity.

[0017] The scroll compressor provided by the embodiments of the present application has at least the following beneficial effects relative to the prior art: when the surface of the sealing element in contact with the bearing is worn after long-term use, the medium (e.g., lubricating oil) with a certain pressure at the high-pressure side can smoothly flow into the groove and exert a buoyancy on the sealing element, and the sealing element can be continuously floated to tightly adhere to the inner ring of the bearing due to the buoyancy provided by the medium, so that the sealing performance is not easily affected by the decrease in height caused by the wear of the sealing element. Therefore, the sealing element provided by the embodiments of the present application is not prone to sealing failure in the case of long-term use, and the scroll compressor can be stably operated for a long time, thereby improving the reliability of the scroll compressor.

[0018] Another object of the present application is to provide an air conditioning device comprising the scroll compressor in any of the above embodiments.

[0019] The air conditioning device provided by the embodiments of the present application has at least the following technical effects compared with the prior art by adopting the scroll compressor described above: in the scroll compressor of the air conditioning device, the medium with a certain pressure at the high-pressure side can smoothly flow into the groove and exert a buoyancy on the sealing element, and the sealing element can be continuously floated to tightly adhere to the inner ring of the bearing due to the buoyancy provided by the high-pressure medium, so that the sealing performance is not easily affected by the decrease in height caused by the wear of the sealing element. The scroll compressor can be stably operated for a long time, thereby improving the reliability of the air conditioning device.

[0020] Another object of the present application is to provide a vehicle comprising the air conditioning device in the above embodiments.

[0021] The vehicle provided by the embodiments of the present application has at least the following technical effects compared with the prior art by adopting the air conditioning device described above: in the air conditioning device in the vehicle, the sealing element of the bearing in the scroll compressor is not prone to sealing failure, and the air conditioning device can be stably operated for a long time, thereby improving the reliability of the air conditioning device of the vehicle. BRIEF DESCRIPTION OF DRAWINGS

[0022] In order to more clearly illustrate the technical solutions in the embodiments of the present application, the drawings needed to be used in the embodiments or prior art description will be briefly introduced. Obviously, the drawings in the following description only constitute some embodiments of the present application, and for those skilled in the art, other drawings can also be obtained from these drawings without creative labor.

[0023] Figure 1 Figure 2 is a partial sectional view of the matching position of the crankshaft and the bearing seat of the scroll compressor in the prior art;

[0024] Figure 2 Figure 3 is a partial sectional view of the scroll compressor in the embodiments of the present application;

[0025] Figure 3 Figure 4 is an enlarged view of B in Figure 3; Figure 2

[0026] Figure 4 Figure 5 is a sectional view of the bracket in Figure 4; Figure 2

[0027] Figure 5 Figure 6 is an enlarged view of C in Figure 5; Figure 4

[0028] Figure 6 Figure 7 is a partial sectional view along the line A-A in Figure 6; Figure 2

[0029] Figure 7 Figure 8 is a sectional view of the seal in Figure 7; Figure 2

[0030] Figure 9 is a sectional view of the bearing in Figure 8; Figure 8 Figure 2 Figure 10 is a structural schematic view of the elastic member support in Figure 9;

[0031] Figure 9 Figure 3 Figure 11 is a structural schematic view of the elastic member support in Figure 10;

[0032] In the drawings:

[0033] 1, bracket; 101, mounting groove; 1011, first table surface; 1012, second table surface; 102, let-out hole; 103, groove; 2, bearing; 201, inner ring; 202, outer ring; 3, crankshaft; 4, seal; 5, elastic support; 6, low-pressure shell; 601, low-pressure cavity; 7, moving scroll; 8, stationary scroll; 9, oil-gas separation assembly; 10, oil storage cavity. DETAILED DESCRIPTION

[0034] ​​​​​​In order to make the purposes, technical solutions and advantages of the present application clearer, the present application will be further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present application and not intended to limit the present application.

[0035] It should be noted that when an element is referred to as being "fixed" or "disposed" on another element, it can be directly on the other element or indirectly on the other element. When an element is referred to as being "connected" to another element, it can be directly connected to the other element or indirectly connected to the other element.

[0036] It should be understood that the terms "length", "width", "upper", "lower", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer" and the like indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, and are only used to facilitate the description of the present application and simplify the description, and therefore cannot be understood as indicating or implying that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore cannot be understood as limiting the present application.

[0037] In addition, the terms "first", "second" are only used for descriptive purposes and cannot be understood as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Therefore, the features defined with "first", "second" can explicitly or implicitly include one or more of the features. In the description of the present application, the meaning of "multiple" is two or more, unless otherwise specifically limited.

[0038] The implementation of the present application will be described in detail below in combination with specific embodiments.

[0039] As Figures 2-4As shown, the embodiment of the present application provides a scroll compressor, which comprises a high-pressure side, a bracket 1, a bearing 2, a crankshaft 3, and a sealing element 4. The crankshaft 3 is installed on the bearing 2, and the sealing element 4 is arranged between the bearing 2 and the bracket 1. The bracket 1 is provided with a groove 103 which is in communication with the high-pressure side of the scroll compressor (for example, an oil-gas separation assembly 9 of the scroll compressor, and lubricating oil flows from the oil-gas separation assembly 9 to the groove 103); the crankshaft 3 penetrates through the bracket 1 and is in interference fit with an inner ring 201 of the bearing 2; the sealing element 4 is movably installed in the groove 103 and abuts against an end surface of the inner ring 201 of the bearing 2, and the medium (for example, high-pressure lubricating oil) of the high-pressure side of the scroll compressor enters the groove 103 and applies a thrust force to the sealing element 4, thereby thrusting the sealing element 4 against the end surface of the inner ring 201 of the bearing 2. The scroll compressor further comprises a low-pressure shell 6 in the prior art and a movable scroll 7 connected with the crankshaft 3, and the bracket 1 is installed on the low-pressure shell 6, and the low-pressure shell 6 has a low-pressure cavity 601 (the low-pressure cavity 601 can be a low-pressure side of the scroll compressor, and the pressure of the low-pressure side is lower than that of the high-pressure side. The low-pressure side of the scroll compressor is in communication with a suction port of the scroll compressor, and the high-pressure side of the scroll compressor is in communication with a discharge port of the scroll compressor), and the low-pressure cavity 601 is located on a side of the bracket 1 away from the movable scroll 7.

[0040] In the embodiment of the present application, the sealing element 4 is movably installed in the groove 103, so that the sealing element 4 can move along the axial direction of the crankshaft 3 relative to the bracket 1. Since the high-pressure lubricating oil of the high-pressure side of the scroll compressor has sufficient pressure and can apply a certain buoyancy to the sealing element 4. Therefore, the lubricating oil reaching the groove 103 from the high-pressure side can apply a thrust force to the sealing element 4, which is directed to the inner ring 201 of the bearing 2, and make the sealing element 4 float up (move towards the inner ring 201 of the bearing 2), so that the sealing element 4 continuously abuts against the end surface (the side surface of the inner ring 201 of the bearing 2) of the inner ring 201 of the bearing 2; in combination with the fact that Figure 6 the high-pressure lubricating oil tightly abuts the inner circumferential surface (the surface closer to the crankshaft 3) of the sealing element 4 against the inner circumferential surface (the surface closer to the crankshaft 3) of the groove 103. Since the crankshaft 3 is in interference fit with the inner ring 201 of the bearing 2, there is almost no gap between the crankshaft 3 and the inner surface of the inner ring 201 of the bearing 2. In combination with the fact that the sealing element 4 seals the side surface of the inner ring 201 of the bearing 2 and the inner circumferential surface of the groove 103, the lubricating oil in the installation groove 101 is not easy to leak through the gap between the bearing 2 and the crankshaft 3 or the gap between the bearing 2 and the bracket 1, thereby completing the sealing of the crankshaft 3, the bracket 1, and the bearing 2.

[0041] Since the bearing 2 is a rotating part, the surface of the sealing member 4 in contact with the bearing 2 is prone to wear and the height (thickness in the direction of the groove depth of the groove 103) is reduced after long-term use; but the sealing member 4 can continuously float to be in close contact with the inner ring 201 of the bearing 2 due to the effect of high-pressure lubricating oil, and is not prone to affecting the sealing performance due to the reduction of the height caused by its own wear. Therefore, the sealing member 4 provided in the embodiment of the application is not prone to sealing failure in the case of long-term use, and can ensure the stable operation of the scroll compressor for a long time, thereby improving the reliability of the scroll compressor.

[0042] Optionally, the sealing member 4 has a smaller density and a smaller self weight, for example, less than the density of the lubricating oil, so that the lubricating oil can float the sealing member 4 in the direction of the groove depth of the groove 103.

[0043] Please refer to Figures 2-4 , as another specific embodiment of the scroll compressor provided in the application, the bracket 1 is provided with a mounting groove 101, and the bearing 2 is mounted in the mounting groove 101. The groove bottom of the mounting groove 101 is provided with a clearance hole 102 and the above-mentioned groove 103. The crankshaft 3 penetrates through the clearance hole 102 and cooperates with the bearing 2.

[0044] Please refer to Figure 3 , as another specific embodiment of the scroll compressor provided in the application, the groove 103 is provided with an elastic support member 5; one side of the elastic support member 5 abuts against the groove bottom of the groove 103, and the other side of the elastic support member 5 abuts against the sealing member 4. The elastic support member 5 can be deformed in the direction of the groove depth of the groove 103 (i.e. the axial direction of the crankshaft 3); when the pressure difference between the lubricating oil in the mounting groove 101 and the low-pressure cavity 601 is small, the elastic pushing force of the elastic support member 5 can push the sealing member 4 to abut against the inner ring 201 of the bearing 2, so as to ensure that the sealing performance of the sealing member 4 remains good in the process of changing the pressure of the lubricating oil. At the same time, in the case that the surface of the sealing member 4 in contact with the inner ring 201 of the bearing 2 is worn, the deformation ability of the elastic support member 5 can cooperate with the buoyancy of the lubricating oil to push the sealing member 4 to be in close contact with the inner ring 201 of the bearing 2. For example, as shown in Figure 9 , the elastic support member 5 can be a wave-shaped gasket.

[0045] For example, the elastic support member 5 and the sealing member 4 can be an integral part, for example, the elastic support member 5 and the sealing member 4 are fixedly connected in one body. When the sealing member 4 and the elastic support member 5 are integrally installed in the groove 103, the installation step can be completed at one time, thereby simplifying the assembly process of the scroll compressor.

[0046] Optionally, the sealing member 4 can also be a part with certain elasticity. The sealing member 4 abuts between the groove bottom of the installation groove 101 and the inner ring 201 of the bearing 2. Since the sealing member 4 itself has certain deformation ability, when the pressure difference between the lubricating oil in the installation groove 101 and the low-pressure cavity 601 is small, the sealing member 4 itself is in a relaxed state and abuts against the inner ring 201 of the bearing 2, so as to ensure that the sealing performance of the sealing member 4 remains good during the change of the pressure of the lubricating oil.

[0047] Please refer to Figures 3-4 As another specific embodiment of the scroll compressor provided in the present application, the bearing 2 is installed in the installation groove 101. The groove bottom of the installation groove 101 has a first table surface 1011 and a second table surface 1012, the second table surface 1012 is more protruding from the groove bottom of the installation groove 101 than the first table surface 1011; the groove 103 is opened in the first table surface 1011; the outer ring 202 of the bearing 2 abuts against the second table surface 1012; and the first table surface 1011 and the end surface of the inner ring 201 of the bearing 2 form a communication gap d. Without the action of the buoyancy of the lubricating oil, the sealing member 4 is located in the groove 103 and is not easy to abut against (close to) the inner ring 201 of the bearing 2, at this time the sealing member 4 is easy to abut against the groove bottom of the groove 103. Under the action of the buoyancy of the lubricating oil, the sealing member 4 floats and abuts against the inner ring 201 of the bearing 2. Since the first table surface 1011 and the end surface of the inner ring 201 of the bearing 2 form the communication gap d, the sealing member 4 can float to protrude from the groove 103 and abut against the inner ring 201 of the bearing 2, at this time a certain gap is formed between the end of the sealing member 4 away from the inner ring 201 of the bearing 2 and the groove bottom of the groove 103, at this time a certain amount of lubricating oil can be accommodated in the gap between the sealing member 4 and the groove bottom of the groove 103, the part of the lubricating oil can continuously provide the buoyancy of the sealing member 4 along the axial direction of the crankshaft 3, so that the sealing member 4 continuously abuts against the inner ring 201 of the bearing 2. And since the communication gap d exists, part of the structure of the sealing member 4 can protrude from the groove 103 after floating, at this time the lubricating oil exerts a pressure on the sealing member 4 along the radial direction of the crankshaft 3, so that the inner circumferential surface of the sealing member 4 closely abuts against the inner circumferential surface of the groove 103, so that the lubricating oil is not easy to pass through the gap between the sealing member 4 and the inner circumferential surface of the groove 103.

[0048] The orbiting scroll 7 and the installation groove 101 of the support 1 enclose the oil storage cavity 10, and the lubricating oil in the oil storage cavity 10 comes from the high-pressure side of the scroll compressor (for example, the oil-gas separation assembly 9 of the scroll compressor), so the pressure of the lubricating oil in the oil storage cavity 10 is greater than the pressure in the low-pressure cavity 601.

[0049] Since the pressure of the lubricating oil in the installation groove 101 (the oil storage cavity 10) is greater than the external pressure (the low pressure cavity 601 communicated with the let-in hole 102), under the action of the pressure difference, the high pressure lubricating oil in the installation groove 101 smoothly enters the bottom of the groove 103 from the gap between the sealing member 4 and the groove 103, and the high pressure lubricating oil at the bottom of the groove 103 exerts a buoyancy on the sealing member 4, which is directed to the inner ring 201 of the bearing 2, and makes the sealing member 4 float (move towards the inner ring 201 of the bearing 2), so that the sealing member 4 is tightly attached to the end surface (the side surface of the inner ring 201 of the bearing 2) of the inner ring 201 of the bearing 2; in combination with Figure 6 , and the inner circumferential surface (the surface closer to the crankshaft 3) of the floating sealing ring is tightly attached to the inner circumferential surface (the surface closer to the crankshaft 3) of the groove 103 due to the pressure difference. Since the crankshaft 3 is in interference fit with the inner ring 201 of the bearing 2, there is almost no gap between the crankshaft 3 and the inner surface of the inner ring 201 of the bearing 2, and the sealing of the sealing member 4 to the side surface of the inner ring 201 of the bearing 2 and the sealing of the sealing member 4 to the inner circumferential surface of the groove 103 make the lubricating oil in the installation groove 101 not easy to leak through the gap between the bearing 2 and the crankshaft 3 or the gap between the bearing 2 and the bracket 1, thereby completing the sealing of the crankshaft 3, the bracket 1 and the bearing 2.

[0050] Please refer to Figures 3-5 As another specific embodiment of the scroll compressor provided in the present application, the width d of the communication gap (the vertical distance between the first mesa 1011 and the second mesa 1012) satisfies: 0 mm < d ≤ 5 mm; the example d can also be 1 mm, 2 mm, …, 8 mm. After the floating of the sealing member 4, the gap between the sealing member 4 and the groove bottom of the groove 103 is large enough to accommodate a certain amount of lubricating oil, which continuously exerts a thrust on the sealing member 4 along the axial direction of the crankshaft 3 and towards the end surface of the inner ring 201 of the bearing 2, so that the sealing member 4 is tightly attached to the inner ring 201 of the bearing 2. At the same time, since the communication gap d is within a certain width range, the length of the part of the sealing member 4 protruding from the structure of the groove 103 after the floating is not too large, and the lubricating oil is not easy to press the sealing member 4 to deform (for example, deflect) along the radial direction of the crankshaft 3, so that the sealing member 4 can better attach to the inner ring 201 of the bearing 2, and the sealing performance is guaranteed.

[0051] Please refer to Figures 3-4As another embodiment of the scroll compressor provided in the present application, the height (height in the direction of the groove depth of the groove 103) of the seal 4 is h, h is greater than or equal to the communication gap d, and thus after the seal 4 floats, at least part of the structure of the seal 4 can still be located inside the groove 103, and the seal 4 does not completely separate from the groove 103, so that at least part of the structure of the seal 4 is located inside the groove 103, and the seal 4 can be limited in the radial direction of the crankshaft 3 by the groove 103. Thus, the seal 4 is not prone to moving in the radial direction of the crankshaft 3 relative to the inner ring 201 of the bearing 2, so that the seal 4 can continuously abut against the inner ring 201 of the bearing 2.

[0052] Referring to Figures 7-8 As another embodiment of the scroll compressor provided in the present application, the width W1 (width in the radial direction of the crankshaft 3) of the seal 4 is less than the width W2 (width in the radial direction of the crankshaft 3) of the groove 103, so that the seal 4 can move in the groove 103 when the seal 4 is installed in the groove 103. For example, a gap can be formed between the seal 4 and the inner wall of the groove 103, and lubricating oil can smoothly enter the groove 103 through the gap and reach the groove bottom of the groove 103, so as to exert a floating force on the seal 4 in the axial direction of the crankshaft 3, so that the seal 4 abuts against the inner ring 201 of the bearing 2. In addition, the lubricating oil can exert a pressure on the seal 4 in the radial direction of the crankshaft 3, so that the seal 4 moves in the radial direction of the crankshaft 3 relative to the support 1 in the groove 103 and abuts against the inner circumferential surface of the groove 103.

[0053] Referring to Figure 4 and Figure 8 As another embodiment of the scroll compressor provided in the present application, the groove 103 is a circular annular groove (cross section is circular annular), the inner diameter D1 of the groove 103 is greater than or equal to the inner diameter D2 of the inner ring 201 of the bearing 2, and the inner diameter D1 of the groove 103 is less than or equal to the outer diameter D3 of the inner ring 201 of the bearing 2, so that there is enough overlap between the seal 4 in the radial direction of the crankshaft 3 and the inner ring 201 of the bearing 2, and the area of contact between the seal 4 and the inner ring 201 of the bearing 2 is large enough to ensure that the seal 4 exerts a good seal on the inner ring 201 of the bearing 2. Even if the scroll compressor is subjected to external impact and the seal 4 moves slightly in the radial direction of the crankshaft 3, the seal 4 and the inner ring 201 of the bearing 2 can still be in good contact, and it is not easy for a gap to exist due to misalignment, and lubricating oil is not prone to leakage.

[0054] Referring to Figure 4 and Figure 8As another specific embodiment of the scroll compressor provided in the present application, the inner diameter D1 of the groove 103 and the inner diameter D2 of the inner ring 201 of the bearing 2 satisfy the following relationship: D2 + 0.2 ≤ D1. The inner diameter of the floating seal ring is set to be slightly larger than the inner diameter of the inner ring 201 of the bearing 2. For certain installation errors or slight movement of the bearing 2 during rotation, the seal 4 can be relatively stable within the boundary range of the inner ring 201 of the bearing 2, and the seal 4 can be in contact with the inner ring 201 of the bearing 2 everywhere, so that the seal 4 is not prone to be locally misaligned with the inner ring 201 of the bearing 2, and the floating seal ring is not prone to be damaged.

[0055] Please refer to Figures 2-3 As another specific embodiment of the scroll compressor provided in the present application, the surface of the seal 4 is provided with a wear-resistant layer to improve the wear resistance of the seal 4 and prolong the service life of the seal 4. The seal 4 is subjected to heat treatment such as nitriding, chromium plating, and carburizing to improve hardness, or is coated with a material such as polytetrafluoroethylene having wear-resistant properties. When the inner ring 201 of the bearing 2 rotates with the crankshaft 3, the inner ring 201 rotates relative to the seal 4 and exerts a sliding friction force on the seal 4. The surface of the seal 4 is prone to wear after being subjected to the sliding friction force, and the sealing effect of the inner ring 201 of the bearing 2 is prone to decrease. The provision of the wear-resistant layer makes the surface of the seal 4 not prone to wear, and the surface flatness and the length of the seal 4 are not prone to change, so that the sealing performance of the seal 4 relative to the inner ring 201 of the bearing 2 is relatively stable.

[0056] Please refer to Figures 2-3 As another specific embodiment of the scroll compressor provided in the present application, the outer ring 202 of the bearing 2 is fixedly installed on the inner side wall of the installation groove 101, which can be in interference fit to achieve fixed installation. The outer ring 202 of the bearing 2 is fixed to the inner wall of the installation groove 101, so that the bearing 2 is relatively stably installed on the bracket 1, and the position of the bearing 2 as a whole is not prone to move. Therefore, the bearing 2 is not prone to move relative to the axial direction of the crankshaft 3, and is not prone to move away from the seal 4 along the axial direction of the crankshaft 3. When the scroll compressor is in operation, the bearing 2 is not prone to actively separate from the seal 4, and the seal 4 can be relatively stably in contact with the inner ring 201 of the bearing 2.

[0057] Please refer to Figure 1As another embodiment of the scroll compressor provided by the present application, the scroll compressor further comprises a low-pressure shell 6, a moving scroll 7 connected to the crankshaft 3, a stationary scroll 8 adapted to the moving scroll 7, and an oil-gas separation assembly 9 installed on the stationary scroll 8. The low-pressure shell 6 has a low-pressure cavity 601, and the bracket 1 is installed on the low-pressure shell 6. The pressure of the hydraulic oil in the installation groove 101 is greater than the pressure in the low-pressure cavity 601. The working process of the scroll compressor is as follows: the low-pressure refrigerant in the low-pressure cavity 601 enters the compression cavity between the moving scroll 7 and the stationary scroll 8, the refrigerant is compressed into high-pressure refrigerant in the compression cavity, and then the high-pressure refrigerant leaves the stationary scroll 8 and reaches the oil-gas separation assembly 9. The oil-gas separation assembly 9 separates the high-pressure refrigerant and the lubricating oil. The refrigerant leaving the oil-gas separation assembly 9 is depressurized through a pipeline and then enters the low-pressure cavity 601 of the low-pressure shell 6. The lubricating oil leaving the oil-gas separation assembly 9 enters the installation groove 101 (the oil storage cavity 10), so the pressure of the lubricating oil in the installation groove 101 is greater than the pressure of the refrigerant in the low-pressure cavity 601.

[0058] The bracket 1 is installed on one end surface of the low-pressure shell 6 and seals the opening of the end surface of the low-pressure shell 6. The main body of the crankshaft 3 is located inside the low-pressure shell 6, and one end of the crankshaft 3 penetrates the accommodation hole 102 and enters the installation groove 101 and is connected to the inner ring 201 of the bearing 2. The inner surface of the installation groove and the partial surface of the moving scroll 7 form an oil cavity (filled with lubricating oil). The sealing member 4 is movably installed in the groove 103 formed in the bottom of the installation groove 101. The sealing member 4 is floated (moves towards the inner ring 201 of the bearing 2) under the buoyancy of the lubricating oil, so that the sealing member 4 is tightly attached to the end surface (the side surface of the inner ring 201 of the bearing 2) of the inner ring 201 of the bearing 2. In combination with Figure 6 , and the inner circumferential surface (the surface closer to the crankshaft 3) of the floating sealing ring is tightly attached to the inner circumferential surface (the surface closer to the crankshaft 3) of the groove 103 due to the pressure difference. Since the crankshaft 3 and the inner ring 201 of the bearing 2 are in interference fit, there is almost no gap between the inner surface of the crankshaft 3 and the inner surface of the inner ring 201 of the bearing 2. The sealing of the sealing member 4 to the side surface of the inner ring 201 of the bearing 2 and the sealing of the sealing member 4 to the inner circumferential surface of the groove 103 prevent the lubricating oil in the installation groove 101 from leaking through the gap between the bearing 2 and the crankshaft 3 or the gap between the bearing 2 and the bracket 1, thereby achieving the sealing of the crankshaft 3, the bracket 1, and the bearing 2.

[0059] Optionally, a corresponding channel can be provided on the bracket 1 or the crankshaft 3 and communicated with the installation groove 101. A switch can be provided on the channel. When the refrigeration oil separated by the oil-gas separation assembly 9 is replenished into the installation groove 101, a certain amount of refrigeration oil can flow into the low-pressure cavity of the low-pressure shell 6 through the channel and mix with the refrigerant in the low-pressure cavity, and then re-enter the compression cavity between the moving scroll 7 and the stationary scroll 8.

[0060] The bracket 1 has a protruding portion away from the side of the orbiting scroll 7, and the mounting groove 101 and the clearance hole 102 are located on the protruding portion. The protruding portion extends into the interior of the low-pressure shell 6, so that the internal structure of the scroll compressor is more compact. A wear-resistant sheet is arranged between the orbiting scroll 7 and the bracket 1. On the one hand, the wear-resistant sheet can seal the gap between the bracket 1 and the orbiting scroll 7, so that the mounting groove 101 and the partial surface of the orbiting scroll 7 form an oil cavity, and the refrigerant oil can be stably located in the oil cavity to lubricate the bearing 2. On the other hand, the bracket 1 and the orbiting scroll 7 are mainly made of metal, and there is a large friction force between the orbiting scroll 7 and the bracket 1 when the orbiting scroll 7 moves. Direct contact between the bracket 1 and the orbiting scroll 7 can cause wear of the orbiting scroll 7 and the bracket 1. The wear-resistant sheet can isolate the bracket 1 and the orbiting scroll 7 to avoid direct contact between the bracket 1 and the orbiting scroll 7 and friction, thereby avoiding wear of the bracket 1 and the orbiting scroll 7 and noise caused by friction. Therefore, the arrangement of the wear-resistant sheet can improve the service life of the scroll compressor and reduce the noise during use. The wear-resistant sheet can be selected as a sheet-shaped material with a certain deformation capacity. When the bracket 1 and the orbiting scroll 7 are installed in the low-pressure shell 6, within a certain error range, the wear-resistant sheet can still fill the gap between the bracket 1 and the orbiting scroll 7. This reduces the precision requirements of the parts of the orbiting scroll 7 and the bracket 1, and also reduces the assembly precision requirements, and can improve the yield of the scroll compressor.

[0061] The low-pressure shell 6 has a low-pressure cavity for containing refrigerant and refrigerant oil. The refrigerant and refrigerant oil in the low-pressure cavity can enter the compression cavity formed by the stationary scroll 8 and the orbiting scroll 7 for compression. When the scroll compressor is working, the driving assembly drives the crankshaft 3 installed on the bearing 2 to rotate, and the crankshaft 3 drives the orbiting scroll 7 connected thereto to rotate. For example, the crankshaft 3 can drive the orbiting scroll 7 to revolve and translate through the eccentric sleeve, so as to compress the refrigerant oil and refrigerant in the compression cavity. The compressed and mixed refrigerant oil and refrigerant enter the oil-gas separation assembly 9 through the gas outlet of the stationary scroll 8. The oil-gas separation assembly 9 separates the mixture of refrigerant oil and refrigerant, and the separated refrigerant oil flows out of the oil-gas separation assembly 9 through the oil return port and flows to each rotating friction pair of the scroll compressor (for example, a corresponding oil return channel is arranged to reach each friction pair). Therefore, the refrigerant oil separated by the oil-gas separation assembly 9 can be reused.

[0062] In the embodiments of the present application, the bracket 1 and the stationary scroll 8 can be fixedly installed on the low-pressure shell 6 through the positioning of the pin, and the orbiting scroll 7 is compressed between the bracket 1 and the stationary scroll 8 and cooperates with the stationary scroll 8 to form a compression cavity. The crankshaft 3 can be rotationally connected with the orbiting scroll 7 through components such as an eccentric sleeve, so as to drive the orbiting scroll 7 to revolve and translate when the crankshaft 3 rotates.

[0063] In the embodiment of the present application, the oil-gas separation assembly 9 comprises a high-pressure shell mounted on the static scroll 8 and an oil separation pipe located in the high-pressure shell; the high-pressure shell is provided with an exhaust port; and the oil return port is provided on the high-pressure shell. The high-pressure shell is mounted on the static scroll 8, and a through hole is formed on the static scroll 8. The refrigerant and the refrigeration oil compressed by the passive scroll 7 and the static scroll 8 enter the high-pressure shell through the through hole. Meanwhile, a buffer groove corresponding to the through hole can be arranged on the high-pressure shell. The high-pressure refrigerant and refrigeration oil mixture first enters the buffer groove for buffering, so as to reduce the speed of the refrigerant and refrigeration oil mixture, so that the oil separation pipe is not easily impacted by the high-speed fluid, the normal work of the oil separation pipe in the high-pressure shell is not easily affected by the refrigerant and refrigeration oil mixture, and the oil separation pipe can rotate normally and stably to separate the refrigerant and the refrigeration oil.

[0064] The mixture of the refrigeration oil and the refrigerant in the high-pressure shell is centrifugally separated by the oil separation pipe. The refrigerant is discharged through the exhaust port and flows to the gas inlet in the low-pressure shell 6 through the pipeline to enter the low-pressure cavity. The refrigeration oil flows out from the oil return port and flows to the friction pair of the scroll compressor. Specifically, after the refrigeration oil flows out from the oil return port, it can enter the channel on the static scroll 8 and then enter the channel on the support 1 to flow to the oil storage cavity 10 (formed by the inner surface of the mounting groove 101 and the partial surface of the dynamic scroll 7).

[0065] The embodiment of the present application also provides a vehicle comprising the scroll compressor in any of the above embodiments. The scroll compressor is a component of the vehicle-mounted air conditioner, and the vehicle further comprises other necessary components of the vehicle-mounted air conditioner in the prior art. The vehicle with the scroll compressor in the above embodiment has sufficient lubricating oil in the oil storage cavity 10 to lubricate the bearing 2 and the friction pair in the oil storage cavity 10, and the lubricating oil in the oil storage cavity 10 is not easily leaked during use. The internal structure of the scroll compressor is not easily damaged, and the scroll compressor is not easily abnormally noisy, and the service life of the scroll compressor is long enough.

[0066] In the present application, the specific type of the vehicle is not limited. For example, the vehicle can be a traditional fuel vehicle or a new energy vehicle. The new energy vehicle includes but is not limited to a pure electric vehicle, a range-extended electric vehicle, a hybrid electric vehicle, a fuel cell electric vehicle, a hydrogen engine vehicle, etc. The present embodiment does not particularly limit this.

[0067] Obviously, the above embodiments of the present application are only examples for clearly illustrating the present application, and are not intended to limit the implementation modes of the present application. Based on the above description, other different forms of changes or modifications can be made by those skilled in the art. Here, it is not necessary or possible to exhaust all the implementation modes. Any modification, equivalent replacement and improvement made within the spirit and principle of the present application shall be included in the protection scope of the claims of the present application.

Claims

1. A scroll compressor comprising a high pressure side, a bracket, a bearing mounted to the bracket, and a crankshaft mounted to the bearing at one end; characterized in that, The bracket is provided with a groove, and a sealing element abutting against an end surface of an inner ring of the bearing is arranged in the groove; a communication passage of a medium is arranged between the groove and the high-pressure side, the medium thrusts the sealing element against the end surface of the inner ring of the bearing, the crankshaft is in interference fit with the inner ring of the bearing, the inner circumferential surface of the groove is arranged in spaced relationship with the crankshaft, and the sealing element seals the inner circumferential surface of the groove; and the cross section of the sealing element is rectangular.

2. The scroll compressor of claim 1, wherein An elastic supporting element is arranged in the groove; one side of the elastic supporting element abuts against the groove bottom, and the other side of the elastic supporting element abuts against the sealing element.

3. The scroll compressor of claim 1, wherein The bracket is provided with a mounting groove in communication with the high-pressure side, the groove bottom of the mounting groove is provided with a first platform and a second platform, the bearing is mounted in the mounting groove; the groove is arranged in the first platform; the outer ring of the bearing abuts against the second platform; and the first platform and the end surface of the inner ring of the bearing form a communication gap in communication with the mounting groove and the groove.

4. The scroll compressor of claim 3, wherein The width d of the communication gap satisfies: 0 mm < d ≤ 5 mm.

5. The scroll compressor of claim 4, wherein, The height h of the sealing element is greater than the width d of the communication gap.

6. The scroll compressor of any one of claims 1-4, wherein, The width W1 of the sealing element in the radial direction of the crankshaft is less than the width W2 of the groove in the radial direction of the crankshaft.

7. The scroll compressor of claim 1, wherein The groove is a circular ring groove, the inner diameter D1 of the groove is greater than or equal to the inner diameter D2 of the inner ring of the bearing, and the inner diameter D1 of the groove is less than or equal to the outer diameter D3 of the inner ring of the bearing.

8. The scroll compressor of claim 7, wherein, The inner diameter D1 of the groove and the inner diameter D2 of the inner ring of the bearing satisfy: D2 + 0.2 ≤ D1.

9. The scroll compressor of claim 1, wherein, The surface of the sealing element is provided with a wear-resistant layer.

10. Air conditioning apparatus, characterized by A scroll compressor comprising any one of the brackets as claimed in claims 1-9.

11. Vehicle, characterized in that An air conditioning device comprising the scroll compressor as claimed in claim 10.

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