Bearing cooling structure, compressor and electrical equipment

Abstract

The utility model provides a bearing cooling structure, a compressor and electrical equipment, the bearing cooling structure comprises a refrigerant flow channel and a bearing cavity, the bearing cavity is used for accommodating a bearing body and allowing a rotating shaft matched with the bearing body to pass through, and the bearing cavity is communicated with the refrigerant flow channel; a circulation path for circulation of a refrigerant is formed in the bearing cavity, and the flowing direction of the refrigerant in the circulation path is the radial outward direction of the rotating shaft. Based on the technical scheme of the utility model, the circulation path for the refrigerant to circulate is constructed in the bearing cavity, and the circulation path is constructed to enable the overall flowing direction of the refrigerant in the circulation path to be outward along the radial direction, and the refrigerant is subjected to the action of the centrifugal force outward along the radial direction in the bearing cavity, so that the refrigerant is prevented from flowing out. Therefore, the overall flowing direction of the refrigerant along the flowing path is consistent with the direction of the centrifugal force, so that the refrigerant can flow along the flowing path in an accelerated manner under the action of the centrifugal force, the flowability of the refrigerant in the bearing cavity can be improved, and heat dissipation of the bearing cavity and the bearing body is accelerated.

Description

Technical Field

[0001] The utility model relates to the technical field of compressors, in particular to a bearing cooling structure, a compressor and electrical equipment. Background Art

[0002] As a general power source, compressors are widely used in machinery, automobiles, medical treatment, food, electricity, building materials, petroleum, chemical industry, military industry and other industries. According to the different working principles of compressors, they can be divided into centrifugal compressors, screw compressors, scroll compressors, etc. Centrifugal compressors are widely used in large public buildings, comfort air conditioning, data centers, regional energy and heat pumps, and their energy efficiency has a significant impact on the energy consumption of public buildings.

[0003] Among them, for centrifugal compressors, the bearing body is the core component that determines whether it can operate safely and stably. The stability and reliability of the bearing body directly affect the performance of the centrifugal compressor. The bearing body will generate a certain amount of heat during the load-bearing operation. As the heat accumulates, the temperature of the bearing body will rise sharply. When the temperature is high, the performance and reliability of the bearing body will be significantly reduced, and even the shaft will get stuck and the motor will burn out. Therefore, effective cooling of the bearing body is a key consideration in the structural design of the centrifugal compressor. Utility Model Content

[0004] In order to solve the problem of heating of a compressor bearing body and improve the cooling effect thereof, the utility model proposes a bearing cooling structure, a compressor and an electrical device.

[0005] In a first aspect, the utility model provides a bearing cooling structure, which comprises a refrigerant flow channel and a bearing cavity, wherein the bearing cavity is used to accommodate a bearing body and a rotating shaft matched with the bearing body to pass through, and the bearing cavity is communicated with the refrigerant flow channel;

[0006] A flow path for circulating the refrigerant is constructed in the bearing cavity, and the flow path is constructed so that the refrigerant flows in a radially outward direction of the rotating shaft.

[0007] In one embodiment, the bearing cavity is configured with a refrigerant inlet connected to the refrigerant flow channel, the bearing cavity has an annular gap between the cavity wall on one side of the shaft in the axial direction and the outer circumferential surface of the shaft, and the refrigerant inlet is configured in the annular gap.

[0008] In one embodiment, the bearing cavity is configured with a refrigerant outlet for discharging refrigerant, and the refrigerant outlet is located radially at the periphery of the bearing body and staggered from the bearing body.

[0009] In one embodiment, the refrigerant outlet includes a plurality of first outlets and a plurality of second outlets, and the plurality of first outlets and the plurality of second outlets are respectively constructed on two side walls of the bearing cavity that are opposite to each other in the axial direction of the rotating shaft.

[0010] In one embodiment, the plurality of first outlets and the plurality of second outlets are arranged circumferentially on the corresponding cavity wall, and the positions of the first outlets and the second outlets are staggered from each other in the circumferential direction.

[0011] In one embodiment, the first outlet is configured such that the axis thereof is in a positional relationship between parallel and perpendicular to the axis of the rotating shaft, and the first outlet gradually deviates from the rotating shaft in a direction from the inside of the bearing cavity along the axis of the first outlet toward the outside.

[0012] In one embodiment, the bearing cavity is configured with an inner chamfer at the radially outermost cavity wall corner, the inner chamfer continuously extends along the circumference of the rotating shaft to form an annular structure, and one end of each of the plurality of first outlets connected to the bearing cavity is configured on the surface of the inner chamfer.

[0013] In one embodiment, the second outlet is configured such that its axis is parallel to the axis of the rotating shaft, and the position of one end of the second outlet communicating with the bearing cavity in the radial direction of the rotating shaft corresponds to the inner chamfer.

[0014] In one embodiment, the plurality of first outlets are arranged circumferentially on the corresponding cavity wall, and the central angle corresponding to the distribution area of ​​the plurality of first outlets on the corresponding cavity wall is not greater than 180°;

[0015] Wherein, when the rotating shaft is in a horizontal use state, the height of the center of the first outlet is not lower than the axis of the rotating shaft.

[0016] In one embodiment, the refrigerant flow channel and the bearing cavity are both constructed in a supporting component corresponding to the bearing body, and the supporting component includes an outer cylinder, a bearing support, and a main thrust plate and an auxiliary thrust plate sleeved on the rotating shaft; the main thrust plate and the auxiliary thrust plate surround the bearing cavity, and an annular gap connecting the main thrust plate and the outer peripheral surface of the rotating shaft is provided, which connects to the bearing cavity, and the refrigerant flow channel is connected to the annular gap.

[0017] In one embodiment, the refrigerant flow channel includes:

[0018] A first flow channel section extending from the outer cylinder to the bearing support;

[0019] A second flow channel section extending from the bearing support to the main thrust plate; and

[0020] A third flow channel section extending from the main thrust plate to communicate with the bearing cavity, the third flow channel section being constructed as a groove structure on the side surface of the main thrust plate, and the third flow channel section extending radially and communicating with the annular gap;

[0021] The refrigerant flow channel is constructed to have direction changes between the first flow channel section and the second flow channel section and between the second flow channel section and the third flow channel section, and the radial dimensions of the first flow channel section, the second flow channel section and the third flow channel section are the same or different.

[0022] In a second aspect, the utility model proposes a compressor, which includes the above-mentioned bearing cooling structure and thus has all the technical effects possessed by it.

[0023] In a third aspect, the utility model proposes an electrical device, which includes the above-mentioned compressor and thus has all the technical effects possessed by it.

[0024] The above technical features can be combined in various suitable ways or replaced by equivalent technical features as long as the purpose of the utility model can be achieved.

[0025] The bearing cooling structure, compressor and electrical equipment provided by the utility model have at least the following beneficial effects compared with the prior art:

[0026] The utility model provides a bearing cooling structure, a compressor and an electrical device, in which a flow path for circulating refrigerant is constructed in a bearing cavity, and the flow path is constructed so that the overall flow direction of the refrigerant therein is radially outward, and the bearing body rotating with the rotating shaft in the bearing cavity will drive the refrigerant entering the bearing cavity to be deflected in the circumferential direction under the action of friction, and then the refrigerant will be subjected to the action of centrifugal force in the radial outward direction. Therefore, the overall flow direction of the refrigerant along the flow path is consistent with the direction of the centrifugal force, so that the refrigerant can be accelerated along the flow path under the action of the centrifugal force, thereby improving the fluidity of the refrigerant in the bearing cavity and accelerating the heat dissipation of the bearing cavity and the bearing body. BRIEF DESCRIPTION OF THE DRAWINGS

[0027] The present invention will be described in more detail below based on embodiments and with reference to the accompanying drawings.

[0028] Figure 1 A cross-sectional view of the bearing cooling structure of the utility model is shown in one viewing angle;

[0029] Figure 2 A cross-sectional view of the bearing cooling structure of the utility model from another perspective is shown;

[0030] Figure 3The schematic diagram of the structure of the auxiliary thrust plate of the bearing cooling structure of the utility model is shown.

[0031] In the drawings, like reference numerals are used for like parts. The drawings are not necessarily to scale.

[0032] Reference numerals:

[0033] 1-refrigerant flow channel, 11-first flow channel section, 111-stop valve, 12-second flow channel section, 13-third flow channel section, 2-bearing cavity, 21-inner chamfer, 3-refrigerant inlet, 4-refrigerant outlet, 41-first outlet, 42-second outlet, 5-support component, 51-outer cylinder, 52-bearing support, 53-main thrust plate, 54-auxiliary thrust plate, 6-bearing body, 7-rotating shaft. DETAILED DESCRIPTION

[0034] The utility model will be further described below in conjunction with the accompanying drawings.

[0035] Example 1

[0036] An embodiment of the utility model provides a bearing cooling structure, which includes a refrigerant flow channel 1 and a bearing cavity 2. The bearing cavity 2 is used to accommodate a bearing body 6 and a rotating shaft 7 matched with the bearing body 6 to pass through, and the bearing cavity 2 is connected to the refrigerant flow channel 1; a flow path for the circulation of refrigerant is constructed in the bearing cavity 2, and the flow path is constructed so that the flow direction of the refrigerant therein is radially outward of the rotating shaft 7.

[0037] Specifically, in this embodiment, an air suspension axial bearing (that is, an air suspension thrust bearing) is used as an example to illustrate the technical solution of the utility model, as shown in the accompanying drawings. Figure 1 As shown, a coolant flow channel 1 and a bearing cavity 2 are constructed in the support component 5 corresponding to the air suspension axial bearing, and the bearing body 6 (that is, the thrust plate of the air suspension thrust bearing) is accommodated in the bearing cavity 2, and the rotating shaft 7 matched with the bearing body 6 passes through the bearing cavity 2. One end of the coolant flow channel 1 is connected to the coolant source through a pipeline, and the other end is connected to the bearing cavity 2, and then the coolant can be introduced into the bearing cavity 2, so as to realize the cooling of the bearing cavity 2 and the bearing body 6. A circulation path for the coolant to flow is constructed inside the bearing cavity 2, and the coolant circulation is realized in cooperation with the coolant flow channel 1.

[0038] In this embodiment, the direction of the flow path inside the bearing cavity 2 is specially designed, that is, the overall flow direction of the coolant along the flow path in the bearing cavity 2 is radially outward, and the technical effect that can be finally achieved is to enhance the fluidity of the coolant in the bearing cavity 2, thereby accelerating the heat dissipation of the bearing cavity 2 and the bearing body 6. The principle for achieving this technical effect is: in the air suspension thrust bearing structure, the bearing body 6 and the rotating shaft 7 are fixedly connected, and then the bearing body 6 will rotate with the rotating shaft 7. When the coolant enters the bearing cavity 2, it will contact the surface of the bearing body 6 and be affected by the friction force, so the coolant will flow along the circumferential direction of the rotating shaft 7 (equivalent to rotation) on the basis of maintaining the original overall flow direction, so the coolant will be affected by the centrifugal force, and the centrifugal force will cause the coolant to deviate from the rotating shaft 7 radially outward, so the direction of the centrifugal force on the coolant is consistent with the direction of the original flow path in the bearing cavity 2, so the coolant can be accelerated along the flow path under the action of the centrifugal force, thereby improving the fluidity of the coolant in the bearing cavity 2 and accelerating the heat dissipation of the bearing cavity 2 and the bearing body 6. In addition, based on the action of centrifugal force, the overall flow of the refrigerant can be decomposed into radial outward flow along the rotating shaft 7 and circumferential flow along the rotating shaft 7. Such multi-directional flow can make the refrigerant quickly and evenly distributed in the bearing cavity 2, ensuring the uniformity of heat dissipation at various positions of the bearing cavity 2 and the bearing body 6.

[0039] Furthermore, the bearing cavity 2 is configured with a refrigerant inlet 3 connected to the refrigerant flow channel 1 , and an annular gap is provided between the cavity wall of the bearing cavity 2 on one side of the axial direction of the rotating shaft 7 and the outer peripheral surface of the rotating shaft 7 , and the refrigerant inlet 3 is configured in the annular gap.

[0040] Specifically, the bearing cavity 2 has a first cavity wall and a second cavity wall opposite to each other in the axial direction of the rotating shaft 7, and an annular gap is formed between the innermost side of one of the first cavity wall and the outer peripheral surface of the rotating shaft 7 in the radial direction of the rotating shaft 7, as shown in the attached Figure 1 and Figure 2 As shown; that is, the center of the cavity wall has a central hole for the shaft 7 to pass through, the diameter of the central hole is larger than the diameter of the shaft 7, and the difference between the two diameters needs to be large enough to allow the refrigerant to flow normally. In this embodiment, the diameter of the central hole is 4 to 10 mm larger than the diameter of the shaft 7, so that an annular gap with a ring width of 2 to 5 mm can be formed. According to the attached drawings Figure 1 and Figure 2It can be seen that the annular gap is at the innermost side of the bearing cavity 2 in the radial direction. Therefore, using the annular gap as the refrigerant inlet 3 can ensure that the refrigerant in the bearing cavity 2 flows radially outward, ensuring that there will be no reverse flow in any part. At the same time, the refrigerant is input into the bearing cavity 2 through the annular gap, so that it can first cover any position of the bearing cavity 2 in the circumferential direction of the rotating shaft 7. Combined with the subsequent radial flow, the refrigerant can cover any position of the bearing cavity 2, ensuring the uniformity of heat dissipation at various positions of the bearing cavity 2 and the bearing body 6.

[0041] It should be noted that whether the annular gap is constructed on the first cavity wall or the second cavity wall mainly depends on which cavity wall is closer to the refrigerant flow channel 1 , that is, which cavity wall is closer to the inner center of the support component 5 .

[0042] Furthermore, the bearing cavity 2 is configured with a refrigerant outlet 4 for discharging refrigerant, and the refrigerant outlet 4 is radially located outside the bearing body 6 and offset from the bearing body 6 ; preferably, the refrigerant outlet 4 is located at the radially outermost position of the bearing cavity 2 .

[0043] Specifically, as shown in the attached figure Figure 1 As shown, the size of the inner space of the bearing cavity 2 in the radial direction of the rotating shaft 7 is larger than the bearing body 6. Therefore, the inner space of the bearing cavity 2 also has an annular space located outside the bearing body 6, and the position of the refrigerant outlet 4 corresponds to the annular space, so it is staggered with the bearing body 6. The purpose of this design is to ensure the bearing capacity of the bearing. Because in this embodiment, the bearing type is an air-suspended thrust bearing, the two cavity walls of the bearing cavity 2 need to cooperate with the bearing body 6 to achieve the axial thrust of the rotating shaft 7. Therefore, if the position of the refrigerant outlet 4 corresponds to the bearing body 6 in the radial direction, the notch formed at the refrigerant outlet 4 cannot contact the bearing body 6 to achieve thrust, that is, the area of ​​the part of the cavity wall of the bearing cavity 2 that can originally contact the bearing body 6 is reduced, which will lead to a decrease in the bearing capacity. Setting the refrigerant outlet 4 to be completely staggered with the bearing body 6 can avoid the occurrence of this problem. In terms of size, the position of the refrigerant outlet 4 cannot fall into the center of the axis position of the rotating shaft 7 and the center of the attached figure. Figure 2 The d5 in the figure is the inner diameter of the circle, and d5 is the outer diameter of the bearing body 6.

[0044] In addition, the refrigerant outlet 4 is preferably arranged at the radially outermost position of the bearing cavity 2. Combined with the previous description of using the innermost annular gap as the refrigerant inlet 3, the refrigerant inlet 3 and the refrigerant outlet 4 are respectively located at the radially innermost and outermost sides of the bearing cavity 2, thereby further ensuring that the flow path of the refrigerant in the bearing cavity 2 is radially outward.

[0045] Example 2

[0046] An embodiment of the utility model provides a bearing cooling structure, which includes a refrigerant flow channel 1 and a bearing cavity 2. The bearing cavity 2 is used to accommodate a bearing body 6 and a rotating shaft 7 matched with the bearing body 6 to pass through, and the bearing cavity 2 is connected to the refrigerant flow channel 1; a flow path for the circulation of refrigerant is constructed in the bearing cavity 2, and the flow path is constructed so that the flow direction of the refrigerant therein is radially outward of the rotating shaft 7.

[0047] Specifically, in this embodiment, an air suspension axial bearing (that is, an air suspension thrust bearing) is used as an example to illustrate the technical solution of the utility model, as shown in the accompanying drawings. Figure 1 As shown, a coolant flow channel 1 and a bearing cavity 2 are constructed in the support component 5 corresponding to the air suspension axial bearing, and the bearing body 6 (that is, the thrust plate of the air suspension thrust bearing) is accommodated in the bearing cavity 2, and the rotating shaft 7 matched with the bearing body 6 passes through the bearing cavity 2. One end of the coolant flow channel 1 is connected to the coolant source through a pipeline, and the other end is connected to the bearing cavity 2, and then the coolant can be introduced into the bearing cavity 2, so as to realize the cooling of the bearing cavity 2 and the bearing body 6. A circulation path for the coolant to flow is constructed inside the bearing cavity 2, and the coolant circulation is realized in cooperation with the coolant flow channel 1.

[0048] In this embodiment, the direction of the flow path inside the bearing cavity 2 is specially designed, that is, the overall flow direction of the coolant along the flow path in the bearing cavity 2 is radially outward, and the technical effect that can be finally achieved is to enhance the fluidity of the coolant in the bearing cavity 2, thereby accelerating the heat dissipation of the bearing cavity 2 and the bearing body 6. The principle for achieving this technical effect is: in the air suspension thrust bearing structure, the bearing body 6 and the rotating shaft 7 are fixedly connected, and then the bearing body 6 will rotate with the rotating shaft 7. When the coolant enters the bearing cavity 2, it will contact the surface of the bearing body 6 and be affected by the friction force, so the coolant will flow along the circumferential direction of the rotating shaft 7 (equivalent to rotation) on the basis of maintaining the original overall flow direction, so the coolant will be affected by the centrifugal force, and the centrifugal force will cause the coolant to deviate from the rotating shaft 7 radially outward, so the direction of the centrifugal force on the coolant is consistent with the direction of the original flow path in the bearing cavity 2, so the coolant can be accelerated along the flow path under the action of the centrifugal force, thereby improving the fluidity of the coolant in the bearing cavity 2 and accelerating the heat dissipation of the bearing cavity 2 and the bearing body 6. In addition, based on the action of centrifugal force, the overall flow of the refrigerant can be decomposed into radial outward flow along the rotating shaft 7 and circumferential flow along the rotating shaft 7. Such multi-directional flow can make the refrigerant quickly and evenly distributed in the bearing cavity 2, ensuring the uniformity of heat dissipation at various positions of the bearing cavity 2 and the bearing body 6.

[0049] Furthermore, the bearing cavity 2 is configured with a refrigerant inlet 3 connected to the refrigerant flow channel 1 , and an annular gap is provided between the cavity wall of the bearing cavity 2 on one side of the axial direction of the rotating shaft 7 and the outer peripheral surface of the rotating shaft 7 , and the refrigerant inlet 3 is configured in the annular gap.

[0050] Specifically, the bearing cavity 2 has a first cavity wall and a second cavity wall opposite to each other in the axial direction of the rotating shaft 7, and an annular gap is formed between the innermost side of one of the first cavity wall and the outer peripheral surface of the rotating shaft 7 in the radial direction of the rotating shaft 7, as shown in the attached Figure 1 and Figure 2 As shown; that is, the center of the cavity wall has a central hole for the shaft 7 to pass through, the diameter of the central hole is larger than the diameter of the shaft 7, and the difference between the two diameters needs to be large enough to allow the refrigerant to flow normally. In this embodiment, the diameter of the central hole is 4 to 10 mm larger than the diameter of the shaft 7, so that an annular gap with a ring width of 2 to 5 mm can be formed. According to the attached drawings Figure 1 and Figure 2 It can be seen that the annular gap is at the innermost side of the bearing cavity 2 in the radial direction. Therefore, using the annular gap as the refrigerant inlet 3 can ensure that the refrigerant in the bearing cavity 2 flows radially outward, ensuring that there will be no reverse flow in any part. At the same time, the refrigerant is input into the bearing cavity 2 through the annular gap, so that it can first cover any position of the bearing cavity 2 in the circumferential direction of the rotating shaft 7. Combined with the subsequent radial flow, the refrigerant can cover any position of the bearing cavity 2, ensuring the uniformity of heat dissipation at various positions of the bearing cavity 2 and the bearing body 6.

[0051] It should be noted that whether the annular gap is constructed on the first cavity wall or the second cavity wall mainly depends on which cavity wall is closer to the refrigerant flow channel 1 , that is, which cavity wall is closer to the inner center of the support component 5 .

[0052] Furthermore, the bearing cavity 2 is configured with a refrigerant outlet 4 for discharging refrigerant, and the refrigerant outlet 4 is radially located outside the bearing body 6 and offset from the bearing body 6 ; preferably, the refrigerant outlet 4 is located at the radially outermost position of the bearing cavity 2 .

[0053] Specifically, as shown in the attached figure Figure 1As shown, the size of the inner space of the bearing cavity 2 in the radial direction of the rotating shaft 7 is larger than the bearing body 6. Therefore, the inner space of the bearing cavity 2 also has an annular space located outside the bearing body 6, and the position of the refrigerant outlet 4 corresponds to the annular space, so it is staggered with the bearing body 6. The purpose of this design is to ensure the bearing capacity of the bearing. Because in this embodiment, the bearing type is an air-suspended thrust bearing, the two cavity walls of the bearing cavity 2 need to cooperate with the bearing body 6 to achieve the axial thrust of the rotating shaft 7. Therefore, if the position of the refrigerant outlet 4 corresponds to the bearing body 6 in the radial direction, the notch formed at the refrigerant outlet 4 cannot contact the bearing body 6 to achieve thrust, that is, the area of ​​the part of the cavity wall of the bearing cavity 2 that can originally contact the bearing body 6 is reduced, which will lead to a decrease in the bearing capacity. Setting the refrigerant outlet 4 to be completely staggered with the bearing body 6 can avoid the occurrence of this problem. In terms of size, the position of the refrigerant outlet 4 cannot fall into the center of the axis position of the rotating shaft 7 and the center of the attached figure. Figure 2 The d5 in the figure is the inner diameter of the circle, and d5 is the outer diameter of the bearing body 6.

[0054] In addition, the refrigerant outlet 4 is preferably arranged at the radially outermost position of the bearing cavity 2. Combined with the previous description of using the innermost annular gap as the refrigerant inlet 3, the refrigerant inlet 3 and the refrigerant outlet 4 are respectively located at the radially innermost and outermost sides of the bearing cavity 2, thereby further ensuring that the flow path of the refrigerant in the bearing cavity 2 is radially outward.

[0055] Furthermore, the refrigerant outlet 4 includes a plurality of first outlets 41 and a plurality of second outlets 42 , and the plurality of first outlets 41 and the plurality of second outlets 42 are respectively constructed on two side walls of the bearing cavity 2 that are opposite to each other in the axial direction of the rotating shaft 7 .

[0056] Specifically, the accompanying drawings Figure 1 and Figure 2 As shown, the refrigerant outlet 4 includes two types of outlets: a first outlet 41 and a second outlet 42. There are multiple outlets in each type. The main difference between the two types of outlets is that the directions are different. Figure 2 As shown, in the axial direction of the rotating shaft 7, the first outlet 41 faces right and the second outlet 41 faces left. The purpose of this design is that the two outlets make the destination of the refrigerant more diverse. The two cavities before and after the bearing can be used for the refrigerant in the bearing cavity 2 to be discharged, thereby providing a larger discharge space for the refrigerant, ensuring the fluidity of the refrigerant, and thus ensuring the cooling effect of the refrigerant on the bearing cavity 2 and the bearing body 6.

[0057] Furthermore, the plurality of first outlets 41 and the plurality of second outlets 42 are arranged along the circumferential direction on the corresponding cavity wall, and the positions of the first outlets 41 and the second outlets 42 are staggered from each other in the circumferential direction.

[0058] Specifically, the first outlet 41 and the second outlet 42 are arranged along the circumference of the rotating shaft 7, so that the refrigerant can be discharged through outlets at different positions in the circumference, avoiding the refrigerant being discharged in one place and affecting the smoothness of the discharge, and ensuring that the refrigerant has good fluidity. The first outlet 41 and the second outlet 42 are staggered in the circumference, so as to further increase the distribution density of the refrigerant outlet 4 in the circumference of the bearing cavity 2 without increasing the number of the first outlet 41 and the second outlet 42 (too many outlets will reduce the structural strength of the bearing), and improve the uniformity of the refrigerant discharge at various positions.

[0059] Furthermore, the first outlet 41 is constructed such that the positional relationship between its axis and the axis of the rotating shaft 7 is between parallel and perpendicular, and in the direction from the inside of the bearing cavity 2 along the axis of the first outlet 41 to the outside, the first outlet 41 gradually deviates from the rotating shaft 7 .

[0060] Specifically, as shown in the attached figure Figure 1 As shown, the first outlet 41 is constructed as an inclined hole structure that is inclined relative to the axial direction of the rotating shaft 7, that is, the positional relationship between the axis of the first outlet 41 and the axis of the rotating shaft 7 is between parallel and vertical, and the first outlet 41 is inclined radially outward with the bearing cavity 2 as a reference, and its direct purpose is to reduce the degree of change in the direction of the flow path of the refrigerant in the bearing cavity 2. The refrigerant flows radially outward in the bearing cavity 2, and after reaching the first outlet 41, it needs to change direction to continue flowing along the first outlet 41. In addition, the reduction in the degree of change in direction is conducive to the refrigerant entering the first outlet 41 from the bearing cavity 2 more smoothly. The fundamental purpose is that based on the fact that the refrigerant can enter the first outlet 41 more smoothly, the debris generated by wear in the bearing cavity 2 can be effectively discharged through the first outlet 41 with the refrigerant, avoiding the accumulation of debris in the bearing cavity 2 and causing further wear of the bearing.

[0061] Furthermore, the bearing cavity 2 is configured with an inner chamfer 21 at the radially outermost cavity wall corner, and the inner chamfer 21 continuously extends along the circumference of the rotating shaft 7 to form an annular structure. The ends of the multiple first outlets 41 connected to the bearing cavity 2 are all configured on the surface of the inner chamfer 21.

[0062] Specifically, as shown in the attached figure Figure 1 and Figure 2 As shown, based on the use of the first outlet 41 for chip removal, the first outlet 41 is arranged on the radially outer side of the bearing cavity 2 in this embodiment, so that the chips that move to the radially outermost side under the action of centrifugal force can be effectively collected. However, since the radially outer side of the bearing cavity 2 is close to the corner of the cavity wall, the corner is prone to form a dead angle for the accumulation of chips, so an inner chamfer 21 is constructed at the corner, and the inclined surface structure of the inner chamfer 21 is used to eliminate the dead angle, and the inclined surface of the inner chamfer 21 can also guide the chips that move to this place, and introduce the chips into the first outlet 41 for external discharge.

[0063] Furthermore, the second outlet 42 is constructed such that its axis is parallel to the axis of the rotating shaft 7 , and the position of one end of the second outlet 42 communicating with the bearing cavity 2 in the radial direction of the rotating shaft 7 corresponds to the inner chamfer 21 .

[0064] Specifically, as shown in the attached figure Figure 2 As shown, the second outlet 42 is constructed to be parallel to the axis of the rotating shaft 7, and is mainly used to discharge the refrigerant. The mouth of the second outlet 42 corresponds to the inner chamfer 21. When the refrigerant in the bearing cavity 2 reaches the inner chamfer 21, the inclined surface of the inner chamfer 21 can reflect the refrigerant to the second outlet 42, thereby improving the smoothness of the refrigerant entering the second outlet 42.

[0065] In addition, as shown in the attached figure Figure 2 As shown, multiple second outlets 42 are distributed along the circumferential direction. In addition to being staggered with the bearing body 6, the overall radial size of the bearing cavity 2 also needs to be considered. At the same time, the size of the second opening itself also needs to consider the impact on the refrigerant discharge flow, that is, the impact on the heat dissipation effect. Therefore, after comprehensive consideration, the diameter (d7) of the second opening is 8 to 16 mm, and the number of second openings is 6 to 10; at the same time, the pitch circle diameter (d6) corresponding to the multiple second openings cannot be too small, because they need to be staggered with the bearing body 6. Due to the limitation of the radial size of the bearing cavity 2, d6 cannot be too large. After comprehensive consideration, d6 is 163 to 177 mm.

[0066] Furthermore, multiple first outlets 41 are arranged circumferentially on the corresponding cavity wall, and the central angle corresponding to the distribution area of ​​the multiple first outlets 41 on the corresponding cavity wall is not greater than 180°; wherein, when the rotating shaft 7 is in a horizontal use state, the height of the center of the first outlet 41 is not lower than the axis of the rotating shaft 7.

[0067] Specifically, as shown in the attached figure Figure 3 As shown, multiple first outlets 41 are distributed in a corresponding area on the cavity wall of the bearing cavity 2 where they are located, and the angle of the central angle corresponding to the maximum range of the area in the circumferential direction is not greater than 180°. The direct purpose of this design is to ensure that when the shaft 7 is in a horizontal state of use, the height of the center of the first outlet 41 is not lower than the axis of the shaft 7; the fundamental purpose is to prevent liquid refrigerant from entering the bearing cavity 2 through the first outlet 41. In the air suspension thrust bearing structure, no liquid refrigerant can enter the bearing cavity 2, and there may be a risk of suction with liquid to the compressor, so there may be liquid refrigerant in the lower part of the external cavity corresponding to the first outlet 41, so that the first outlet 41 is higher than the axis of the shaft 7, so as to avoid the area where the liquid refrigerant may exist. In addition, based on the requirements for the distribution area of ​​the first outlet 41, the number of the first outlet 41 cannot be too many, so as to avoid causing the orifice structure to be too dense and reduce the structural strength, so the number of the first outlet 41 is 4 to 8, and the diameter (d4) of the first outlet 41 is 7 to 12 mm.

[0068] Example 3

[0069] An embodiment of the utility model provides a bearing cooling structure, which includes a refrigerant flow channel 1 and a bearing cavity 2, the bearing cavity 2 is used to accommodate a bearing body 6 and a rotating shaft 7 where the bearing body 6 is located passes through the bearing cavity 2, the bearing cavity 2 is respectively constructed with a refrigerant inlet 3 and a refrigerant outlet 4, the refrigerant inlet 3 is connected to the refrigerant flow channel 1; wherein, in the radial direction of the rotating shaft 7, the refrigerant inlet 3 is closer to the center of the bearing body 6 than the refrigerant outlet 4.

[0070] Specifically, in this embodiment, an air suspension axial bearing (that is, an air suspension thrust bearing) is used as an example to illustrate the technical solution of the utility model, as shown in the accompanying drawings. Figure 1 As shown, a coolant flow channel 1 and a bearing cavity 2 are constructed in the support component 5 corresponding to the air suspension axial bearing, and the bearing body 6 (that is, the thrust plate of the air suspension thrust bearing) is accommodated in the bearing cavity 2, and the rotating shaft 7 matched with the bearing body 6 passes through the bearing cavity 2. One end of the coolant flow channel 1 is connected to the coolant source through a pipeline, and the other end is connected to the bearing cavity 2, so that coolant can be introduced into the bearing cavity 2, thereby realizing the cooling of the bearing cavity 2 and the bearing body 6. The bearing cavity 2 is constructed with a coolant inlet 3 and a coolant outlet 4, which are used to realize the input and discharge of the coolant, and then cooperate with the coolant flow channel 1 to realize the circulation of the coolant.

[0071] In this embodiment, the relative positions of the refrigerant inlet 3 and the refrigerant outlet 4 are specially designed, that is, in the radial direction of the rotating shaft 7, the refrigerant inlet 3 is set to be closer to the center of the bearing body 6 than the refrigerant outlet 4. The purpose of this design is to make the flow path of the refrigerant in the bearing cavity 2 radially outward, and the technical effect that can be finally achieved is to enhance the fluidity of the refrigerant in the bearing cavity 2, thereby accelerating the heat dissipation of the bearing cavity 2 and the bearing body 6. The principle for achieving this technical effect is that in the air suspension thrust bearing structure, the bearing body 6 and the rotating shaft 7 are fixedly connected, and then the bearing body 6 will rotate with the rotating shaft 7; when the refrigerant enters the bearing cavity 2, it will contact the surface of the bearing body 6, so that under the action of friction, the bearing body 6 will drive the refrigerant to flow along the circumferential direction of the rotating shaft 7 (equivalent to generating rotation), so the refrigerant will be affected by the centrifugal force and then deviate from the rotating shaft 7 radially outward. Based on the design of the relative positions of the refrigerant inlet 3 and the refrigerant outlet 4, the direction of the flow path of the refrigerant in the bearing cavity 2 is consistent with the direction of movement of the refrigerant radially outward away from the rotating shaft 7 under the action of centrifugal force. Therefore, the refrigerant can flow faster under the action of centrifugal force, thereby improving the fluidity of the refrigerant in the bearing cavity 2 and accelerating the heat dissipation of the bearing cavity 2 and the bearing body 6.

[0072] Furthermore, an annular gap is provided between the cavity wall of the bearing cavity 2 on one side in the axial direction of the rotating shaft 7 and the outer peripheral surface of the rotating shaft 7 , and the refrigerant inlet 3 is configured in the annular gap.

[0073] Specifically, the bearing cavity 2 has a first cavity wall and a second cavity wall opposite to each other in the axial direction of the rotating shaft 7, and an annular gap is formed between the innermost side of one of the first cavity wall and the outer peripheral surface of the rotating shaft 7 in the radial direction of the rotating shaft 7, as shown in the attached Figure 1 and Figure 2 As shown; that is, the center of the cavity wall has a central hole for the shaft 7 to pass through, the diameter of the central hole is larger than the diameter of the shaft 7, and the difference between the two diameters needs to be large enough to allow the refrigerant to flow normally. In this embodiment, the diameter of the central hole is 4 to 10 mm larger than the diameter of the shaft 7, so that an annular gap with a ring width of 2 to 5 mm can be formed. According to the attached drawings Figure 1 and Figure 2 It can be seen that the annular gap is at the innermost side of the bearing cavity 2 in the radial direction. Therefore, using the annular gap as the refrigerant inlet 3 can ensure that the refrigerant in the bearing cavity 2 flows radially outward, ensuring that there will be no reverse flow in any part. At the same time, the refrigerant is input into the bearing cavity 2 through the annular gap, so that it can first cover any position of the bearing cavity 2 in the circumferential direction of the rotating shaft 7. Combined with the subsequent radial flow, the refrigerant can cover any position of the bearing cavity 2, ensuring the uniformity of heat dissipation at various positions of the bearing cavity 2 and the bearing body 6.

[0074] It should be noted that whether the annular gap is constructed on the first cavity wall or the second cavity wall mainly depends on which cavity wall is closer to the refrigerant flow channel 1 , that is, which cavity wall is closer to the inner center of the support component 5 .

[0075] Furthermore, the radial dimension of the bearing cavity 2 is larger than the outer diameter of the bearing body 6 , and the refrigerant outlet 4 is located radially outside the bearing body 6 and offset from the bearing body 6 ; preferably, the refrigerant outlet 4 is located at the radially outermost position of the bearing cavity 2 .

[0076] Specifically, as shown in the attached figure Figure 1As shown, the size of the inner space of the bearing cavity 2 in the radial direction of the rotating shaft 7 is larger than the bearing body 6. Therefore, the inner space of the bearing cavity 2 also has an annular space located outside the bearing body 6, and the position of the refrigerant outlet 4 corresponds to the annular space, so it is staggered with the bearing body 6. The purpose of this design is to ensure the bearing capacity of the bearing. Because in this embodiment, the bearing type is an air-suspended thrust bearing, the two cavity walls of the bearing cavity 2 need to cooperate with the bearing body 6 to achieve the axial thrust of the rotating shaft 7. Therefore, if the position of the refrigerant outlet 4 corresponds to the bearing body 6 in the radial direction, the notch formed at the refrigerant outlet 4 cannot contact the bearing body 6 to achieve thrust, that is, the area of ​​the part of the cavity wall of the bearing cavity 2 that can originally contact the bearing body 6 is reduced, which will lead to a decrease in the bearing capacity. Setting the refrigerant outlet 4 to be completely staggered with the bearing body 6 can avoid the occurrence of this problem. In terms of size, the position of the refrigerant outlet 4 cannot fall into the center of the axis position of the rotating shaft 7 and the center of the attached figure. Figure 2 The d5 in the figure is the inner diameter of the circle, and d5 is the outer diameter of the bearing body 6.

[0077] In addition, the refrigerant outlet 4 is preferably arranged at the radially outermost position of the bearing cavity 2. Combined with the previous description of using the innermost annular gap as the refrigerant inlet 3, the refrigerant inlet 3 and the refrigerant outlet 4 are respectively located at the radially innermost and outermost sides of the bearing cavity 2, thereby further ensuring that the flow path of the refrigerant in the bearing cavity 2 is radially outward.

[0078] Furthermore, the refrigerant outlet 4 includes a plurality of first outlets 41 and a plurality of second outlets 42 , and the plurality of first outlets 41 and the plurality of second outlets 42 are respectively constructed on two side walls of the bearing cavity 2 that are opposite to each other in the axial direction of the rotating shaft 7 .

[0079] Specifically, the accompanying drawings Figure 1 and Figure 2 As shown, the refrigerant outlet 4 includes two types of outlets: a first outlet 41 and a second outlet 42. There are multiple outlets in each type. The main difference between the two types of outlets is that the directions are different. Figure 2 As shown, in the axial direction of the rotating shaft 7, the first outlet 41 faces right and the second outlet 41 faces left. The purpose of this design is that the two outlets make the destination of the refrigerant more diverse. The two cavities before and after the bearing can be used for the refrigerant in the bearing cavity 2 to be discharged, thereby providing a larger discharge space for the refrigerant, ensuring the fluidity of the refrigerant, and thus ensuring the cooling effect of the refrigerant on the bearing cavity 2 and the bearing body 6.

[0080] Furthermore, the plurality of first outlets 41 and the plurality of second outlets 42 are arranged along the circumferential direction on the corresponding cavity wall, and the positions of the first outlets 41 and the second outlets 42 are staggered from each other in the circumferential direction.

[0081] Specifically, the first outlet 41 and the second outlet 42 are arranged along the circumference of the rotating shaft 7, so that the refrigerant can be discharged through outlets at different positions in the circumference, avoiding the refrigerant being discharged in one place and affecting the smoothness of the discharge, and ensuring that the refrigerant has good fluidity. The first outlet 41 and the second outlet 42 are staggered in the circumference, so as to further increase the distribution density of the refrigerant outlet 4 in the circumference of the bearing cavity 2 without increasing the number of the first outlet 41 and the second outlet 42 (too many outlets will reduce the structural strength of the bearing), and improve the uniformity of the refrigerant discharge at various positions.

[0082] Furthermore, the first outlet 41 is constructed such that the positional relationship between its axis and the axis of the rotating shaft 7 is between parallel and perpendicular, and in the direction from the inside of the bearing cavity 2 along the axis of the first outlet 41 to the outside, the first outlet 41 gradually deviates from the rotating shaft 7 .

[0083] Specifically, as shown in the attached figure Figure 1 As shown, the first outlet 41 is constructed as an inclined hole structure that is inclined relative to the axial direction of the rotating shaft 7, that is, the positional relationship between the axis of the first outlet 41 and the axis of the rotating shaft 7 is between parallel and vertical, and the first outlet 41 is inclined radially outward with the bearing cavity 2 as a reference, and its direct purpose is to reduce the degree of change in the direction of the flow path of the refrigerant in the bearing cavity 2. The refrigerant flows radially outward in the bearing cavity 2, and after reaching the first outlet 41, it needs to change direction to continue flowing along the first outlet 41. In addition, the reduction in the degree of change in direction is conducive to the refrigerant entering the first outlet 41 from the bearing cavity 2 more smoothly. The fundamental purpose is that based on the fact that the refrigerant can enter the first outlet 41 more smoothly, the debris generated by wear in the bearing cavity 2 can be effectively discharged through the first outlet 41 with the refrigerant, avoiding the accumulation of debris in the bearing cavity 2 and causing further wear of the bearing.

[0084] Furthermore, the bearing cavity 2 is configured with an inner chamfer 21 at the radially outermost cavity wall corner, and the inner chamfer 21 continuously extends along the circumference of the rotating shaft 7 to form an annular structure. The ends of the multiple first outlets 41 connected to the bearing cavity 2 are all configured on the surface of the inner chamfer 21.

[0085] Specifically, as shown in the attached figure Figure 1 and Figure 2 As shown, based on the use of the first outlet 41 for chip removal, the first outlet 41 is arranged on the radially outer side of the bearing cavity 2 in this embodiment, so that the chips that move to the radially outermost side under the action of centrifugal force can be effectively collected. However, since the radially outer side of the bearing cavity 2 is close to the corner of the cavity wall, the corner is prone to form a dead angle for the accumulation of chips, so an inner chamfer 21 is constructed at the corner, and the inclined surface structure of the inner chamfer 21 is used to eliminate the dead angle, and the inclined surface of the inner chamfer 21 can also guide the chips that move to this place, and introduce the chips into the first outlet 41 for external discharge.

[0086] Furthermore, the second outlet 42 is constructed such that its axis is parallel to the axis of the rotating shaft 7 , and the position of one end of the second outlet 42 communicating with the bearing cavity 2 in the radial direction of the rotating shaft 7 corresponds to the inner chamfer 21 .

[0087] Specifically, as shown in the attached figure Figure 2 As shown, the second outlet 42 is constructed to be parallel to the axis of the rotating shaft 7, and is mainly used to discharge the refrigerant. The mouth of the second outlet 42 corresponds to the inner chamfer 21. When the refrigerant in the bearing cavity 2 reaches the inner chamfer 21, the inclined surface of the inner chamfer 21 can reflect the refrigerant to the second outlet 42, thereby improving the smoothness of the refrigerant entering the second outlet 42.

[0088] In addition, as shown in the attached figure Figure 2 As shown, multiple second outlets 42 are distributed along the circumferential direction. In addition to being staggered with the bearing body 6, the overall radial size of the bearing cavity 2 also needs to be considered. At the same time, the size of the second opening itself also needs to consider the impact on the refrigerant discharge flow, that is, the impact on the heat dissipation effect. Therefore, after comprehensive consideration, the diameter (d7) of the second opening is 8 to 16 mm, and the number of second openings is 6 to 10; at the same time, the pitch circle diameter (d6) corresponding to the multiple second openings cannot be too small, because they need to be staggered with the bearing body 6. Due to the limitation of the radial size of the bearing cavity 2, d6 cannot be too large. After comprehensive consideration, d6 is 163 to 177 mm.

[0089] Furthermore, multiple first outlets 41 are arranged circumferentially on the corresponding cavity wall, and the central angle corresponding to the distribution area of ​​the multiple first outlets 41 on the corresponding cavity wall is not greater than 180°; wherein, when the rotating shaft 7 is in a horizontal use state, the height of the center of the first outlet 41 is not lower than the axis of the rotating shaft 7.

[0090] Specifically, as shown in the attached figure Figure 3 As shown, multiple first outlets 41 are distributed in a corresponding area on the cavity wall of the bearing cavity 2 where they are located, and the angle of the central angle corresponding to the maximum range of the area in the circumferential direction is not greater than 180°. The direct purpose of this design is to ensure that when the shaft 7 is in a horizontal state of use, the height of the center of the first outlet 41 is not lower than the axis of the shaft 7; the fundamental purpose is to prevent liquid refrigerant from entering the bearing cavity 2 through the first outlet 41. In the air suspension thrust bearing structure, no liquid refrigerant can enter the bearing cavity 2, and there may be a risk of suction with liquid to the compressor, so there may be liquid refrigerant in the lower part of the external cavity corresponding to the first outlet 41, so that the first outlet 41 is higher than the axis of the shaft 7, so as to avoid the area where the liquid refrigerant may exist. In addition, based on the requirements for the distribution area of ​​the first outlet 41, the number of the first outlet 41 cannot be too many, so as to avoid causing the orifice structure to be too dense and reduce the structural strength, so the number of the first outlet 41 is 4 to 8, and the diameter (d4) of the first outlet 41 is 7 to 12 mm.

[0091] Furthermore, the refrigerant flow channel 1 and the bearing cavity 2 are both constructed on the supporting component 5 corresponding to the bearing body 6, and the supporting component 5 includes an outer cylinder 51, a bearing support 52, and a main thrust plate 53 and an auxiliary thrust plate 54 sleeved on the rotating shaft 7; the main thrust plate 53 and the auxiliary thrust plate 54 surround the bearing cavity 2, and an annular gap connecting the main thrust plate 53 and the outer peripheral surface of the rotating shaft 7 is provided, which connects to the bearing cavity 2, and the refrigerant flow channel 1 is connected to the annular gap.

[0092] Specifically, as shown in the attached figure Figure 1 As shown, the refrigerant flow channel 1 and the bearing cavity 2 are both constructed on the support component 5 corresponding to the bearing body 6, wherein the bearing support 52, the main thrust plate 53 and the auxiliary thrust plate 54 are all sleeved on the rotating shaft 7 and are sequentially distributed along the axial direction of the rotating shaft 7, the outer cylinder 51 is located radially at the periphery of the whole formed by the bearing support 52, the main thrust plate 53 and the auxiliary thrust plate 54, and the outer side of the inner side of the outer cylinder 51 is limitedly matched with the outer side of the bearing support 52. The main thrust plate 53 and the auxiliary thrust plate 54 together surround the bearing cavity 2, and the refrigerant flow channel 1 is mainly constructed on the outer cylinder 51, the bearing support 52 and the main thrust plate 53. The main thrust plate 53 is closer to the center of the support component 5 than the auxiliary thrust plate 54, so the annular gap serving as the refrigerant inlet 3 is constructed between the inner side of the main thrust plate 53 and the rotating shaft 7.

[0093] Furthermore, the refrigerant flow channel 1 includes a first flow channel section 11, a second flow channel section 12 and a third flow channel section 13. The first flow channel section 11 extends from the outer cylinder 51 to the bearing support 52; the second flow channel section 12 extends from the bearing support 52 to the main thrust plate 53; the third flow channel section 13 extends from the main thrust plate 53 to the bearing cavity 2, and the third flow channel section 13 is constructed as a groove structure on the side of the main thrust plate 53, and the third flow channel section 13 extends radially and connects the annular gap.

[0094] The refrigerant channel 1 is constructed to have direction changes between the first channel section 11 and the second channel section 12 and between the second channel section 12 and the third channel section 13, and the radial dimensions of the first channel section 11, the second channel section 12 and the third channel section 13 are the same or different.

[0095] Specifically, as shown in the attached figure Figure 1 As shown, the refrigerant flow channel 1 reaches the bearing cavity 2 from the outer cylinder 51 through the bearing support 52 and the main thrust plate 53, and then forms the first flow channel section 11, the second flow channel section 12 and the third flow channel section 13 in sequence. In order to adapt to the structural changes of the outer cylinder 51, the bearing support 52 and the main thrust plate 53, there are changes in direction from the first flow channel section 11 to the second flow channel section 12 and from the second flow channel section 12 to the third flow channel section 13. In addition to adapting to the changes in the structural position, the change in direction can also collide with the refrigerant through the corners at the change in direction, and use the collision to separate the liquid refrigerant that may exist in the gaseous refrigerant.

[0096] In addition, the radial dimensions of the first flow channel section 11, the second flow channel section 12 and the third flow channel section 13 can be set to be consistent if conditions permit. In this embodiment, due to the differences in the structural dimensions of the outer cylinder 51, the bearing support 52 and the main thrust plate 53, in order to adapt to the dimensions of different positions, the radial dimensions of the first flow channel section 11, the second flow channel section 12 and the third flow channel section 13 are set to be different. Among them, the diameter d1 of the first flow channel section 11 will affect the flow rate of the introduced refrigerant. If d1 is too large, the flow rate of the refrigerant introduced from the first-stage exhaust port of the compressor (refrigerant source) will be very large (a stop valve 111 connected to the first-stage exhaust port of the compressor is provided at the inlet of the first flow channel section 11, and the stop valve 111 can further flexibly adjust the input flow rate of the refrigerant), which will cause the flow rate of the compressor introduced from the first-stage exhaust to the second-stage side air inlet to be reduced, thereby reducing the efficiency of the compressor; if d1 is too small, the flow rate introduced into the bearing cavity 2 will be reduced, making the cooling effect worse. Considering comprehensively, d1 is 3 to 8 mm. The diameter d2 of the second flow channel section 12 will also affect the flow rate of the introduced refrigerant. If d2 is too small, the flow rate introduced into the bearing cavity 2 will be reduced, which will make the cooling effect worse. At the same time, due to the limitation of the size of the bearing support 52, d2 cannot be too large. Considering comprehensively, d2 is 5 to 12 mm. The depth d3 of the groove body of the third flow channel section 13 on the main thrust plate 53 will also affect the flow rate of the introduced refrigerant. If d3 is too small, the flow rate introduced into the bearing cavity 2 will be reduced, which will make the cooling effect worse. Due to the limitation of the thickness of the main thrust plate 53, d3 cannot be too large. Considering comprehensively, d3 is 2 to 4 mm, and the width of the groove body of the third flow channel section 13 is 8 to 12 mm.

[0097] Example 4

[0098] An embodiment of the utility model provides a compressor, which includes the bearing cooling structure of any of the above embodiments, and thus has all the technical effects possessed by it.

[0099] In addition, the compressor may further include components and parts for realizing its necessary functions, which may be realized in various ways known in the prior art.

[0100] Example 5

[0101] The embodiment of the utility model provides an electrical appliance, which includes the compressor of embodiment 4, and thus has all the technical effects thereof. The electrical appliance in this embodiment includes air conditioning equipment, refrigerator equipment or other equipment to which the compressor of embodiment 4 is applied.

[0102] In the description of the present invention, it should be understood that the terms "upper", "lower", "bottom", "top", "front", "back", "inside", "outside", "left", "right", etc., indicating directions or positional relationships, are based on the directions or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific direction, be constructed and operated in a specific direction, and therefore should not be understood as a limitation on the present invention.

[0103] Although the present invention is described herein with reference to specific embodiments, it should be understood that these embodiments are merely examples of the principles and applications of the present invention. It should therefore be understood that many modifications may be made to the exemplary embodiments, and other arrangements may be designed without departing from the spirit and scope of the present invention as defined by the appended claims. It should be understood that the features described in the various dependent claims and herein may be combined in a manner different from that described in the original claims. It may also be understood that the features described in conjunction with the individual embodiments may be used in other described embodiments.

Claims

1. A bearing cooling structure, characterized in that: It includes a refrigerant flow channel and a bearing cavity, wherein the bearing cavity is used to accommodate a bearing body and allow a rotating shaft matched with the bearing body to pass through, and the bearing cavity is communicated with the refrigerant flow channel; A flow path for circulating the refrigerant is constructed in the bearing cavity, and the flow path is constructed so that the refrigerant flows in a radially outward direction of the rotating shaft.

2. The bearing cooling structure according to claim 1, characterized in that: The bearing cavity is configured with a refrigerant inlet connected to the refrigerant flow channel. The bearing cavity has an annular gap between the cavity wall on one side of the shaft in the axial direction and the outer peripheral surface of the shaft, and the refrigerant inlet is configured in the annular gap.

3. The bearing cooling structure according to claim 1 or 2, characterized in that: The bearing cavity is configured with a refrigerant outlet for discharging refrigerant. The refrigerant outlet is located at the periphery of the bearing body in the radial direction and is staggered from the bearing body.

4. The bearing cooling structure according to claim 3, characterized in that: The refrigerant outlet includes a plurality of first outlets and a plurality of second outlets, and the plurality of first outlets and the plurality of second outlets are respectively constructed on two side walls of the bearing cavity that are opposite to each other in the axial direction of the rotating shaft.

5. The bearing cooling structure according to claim 4, characterized in that: The plurality of first outlets and the plurality of second outlets are arranged circumferentially on the corresponding cavity wall, and the positions of the first outlets and the second outlets are staggered from each other in the circumferential direction.

6. The bearing cooling structure according to claim 4, characterized in that: The first outlet is configured such that the positional relationship between its axis and the axis of the rotating shaft is between parallel and perpendicular, and the first outlet gradually deviates from the rotating shaft in a direction from the inside of the bearing cavity along the axis of the first outlet toward the outside.

7. The bearing cooling structure according to claim 6, characterized in that: The bearing cavity is configured with an inner chamfer at the outermost cavity wall corner in the radial direction, and the inner chamfer continuously extends along the circumference of the shaft to form an annular structure, and one end of each of the plurality of first outlets connected to the bearing cavity is configured on the surface of the inner chamfer.

8. The bearing cooling structure according to claim 7, characterized in that: The second outlet is constructed such that its axis is parallel to the axis of the rotating shaft, and the position of one end of the second outlet communicating with the bearing cavity in the radial direction of the rotating shaft corresponds to the inner chamfer.

9. The bearing cooling structure according to claim 6, characterized in that: The plurality of first outlets are arranged circumferentially on the corresponding cavity wall, and the central angle corresponding to the distribution area of ​​the plurality of first outlets on the corresponding cavity wall is not greater than 180°; Wherein, when the rotating shaft is in a horizontal use state, the height of the center of the first outlet is not lower than the axis of the rotating shaft.

10. The bearing cooling structure according to claim 1 or 2, characterized in that: The refrigerant flow channel and the bearing cavity are both constructed on a supporting component corresponding to the bearing body, and the supporting component includes an outer cylinder, a bearing support, and a main thrust plate and an auxiliary thrust plate sleeved on the rotating shaft; The main thrust plate and the auxiliary thrust plate form the bearing cavity. An annular gap communicating with the bearing cavity is provided between the main thrust plate and the outer peripheral surface of the rotating shaft. The refrigerant flow channel is communicated with the annular gap.

11. The bearing cooling structure according to claim 10, characterized in that: The refrigerant flow channel comprises: A first flow channel section extending from the outer cylinder to the bearing support; A second flow channel section extending from the bearing support to the main thrust plate; and A third flow channel section extending from the main thrust plate to communicate with the bearing cavity, the third flow channel section being constructed as a groove structure on the side surface of the main thrust plate, and the third flow channel section extending radially and communicating with the annular gap; The refrigerant flow channel is constructed to have a direction change between the first flow channel section and the second flow channel section and between the second flow channel section and the third flow channel section, and the radial dimensions of the first flow channel section, the second flow channel section and the third flow channel section are the same or different.

12. A compressor, characterized in that: The bearing cooling structure comprises the bearing cooling structure according to any one of claims 1 to 11.

13. An electrical device, characterized in that: Comprising the compressor of claim 12.

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