Hydrodynamic bearing and combination of hydrodynamic bearing and wing plate

Abstract

The present application relates to a hydrodynamic bearing and a combination of a hydrodynamic bearing and a wing plate. The combination of the hydrodynamic bearing and the wing plate includes: a hydrodynamic bearing, a rotating shaft, and a wing plate. The rotating shaft is disposed on the wing plate, and the rotating shaft is inserted into the shaft hole of the hydrodynamic bearing. At least two oil guiding groove groups are provided on the inner wall of the shaft hole of the hydrodynamic bearing. Each oil guiding groove group includes a plurality of oil guiding grooves. A cusp is formed at the bent portion of each oil guiding groove. The cusps of the plurality of oil guiding grooves in the same oil guiding groove group form a cusp corresponding portion arranged circumferentially in the shaft hole. An acting area region is formed between the cusp corresponding portions of every two adjacent oil guiding groove groups in the shaft hole. The mass center of the wing plate and the rotating shaft falls within or near the acting area region. Therefore, the hydrodynamic bearing has better supporting force, can support the balanced rotation of the rotating shaft and the wing plate, and effectively reduces the generation of noise and vibration.

Description

Technical Field

[0001] The present invention relates to a hydrodynamic bearing and a combination of a hydrodynamic bearing and a wing plate, and particularly to a hydrodynamic bearing that can generate a pressure field due to a change in flow velocity when a fluid passes between the bearing and a rotating shaft, enabling the rotating shaft to rotate stably without contacting the bearing, and a combination thereof with a wing plate. Background Art

[0002] In existing hydrodynamic bearings, oil guiding grooves are provided on the inner wall of the bearing body or the outer wall of the rotating shaft. When a lubricating fluid flows between the rotating shaft and the bearing body, pressure can be concentrated to form a pressure. Through the supporting force of the oil film, the rotating shaft will not contact the shaft hole when rotating. Therefore, it is possible to avoid the mutual collision and wear between the rotating shaft and the bearing body, and further reduce the generation of noise and vibration, becoming a commonly used bearing technology in current information products. The hydrodynamic bearing can be installed on the wing plate of a fan to support the rotation of the wing plate of the fan. However, the hydrodynamic bearing cannot provide a better supporting force between the rotating shaft and the wing plate, resulting in collisions between the rotating shaft and the hydrodynamic bearing, and further generating noise and vibration. Summary of the Invention

[0003] The technical problem to be solved by the present invention is to provide a hydrodynamic bearing and a combination thereof with a wing plate in view of the deficiencies of the prior art. The hydrodynamic bearing can provide a better supporting force between the rotating shaft and the wing plate, so that there is no collision between the rotating shaft and the hydrodynamic bearing, effectively avoiding the generation of noise and vibration.

[0004] To solve the above technical problem, the present invention provides a hydrodynamic bearing that can be combined with a rotating shaft and a wing plate. One end of the rotating shaft is fixed to the wing plate. The hydrodynamic bearing has a bearing body, and a shaft hole is formed in the bearing body. At least two groups of oil guiding grooves are provided on the inner wall of the shaft hole. Each group of oil guiding grooves includes a plurality of oil guiding grooves, and these oil guiding grooves are bent in a V shape. The rotating shaft can be inserted into the shaft hole, and a gap is formed between the rotating shaft and the hydrodynamic bearing to accommodate a lubricating fluid; a tip point is formed at the bending position of each oil guiding groove, and the tip points of the plurality of oil guiding grooves in the same group of oil guiding grooves form a circumferentially arranged tip point corresponding position in the shaft hole. An acting area region is formed between the tip point corresponding positions of every two adjacent groups of oil guiding grooves in the shaft hole. The mass center of the wing plate and the rotating shaft falls within or near the acting area region. The mass center of the wing plate and the rotating shaft being near the acting area region means that the acting area region forms an acting area length along the axial direction of the hydrodynamic bearing, and the mass center of the wing plate and the rotating shaft is outside the acting area region and within a range of one-tenth of the acting area length from the acting area region.

[0005] Preferably, the outer diameter of the vane is defined as a vane diameter. The vane has a first end face. The hydrodynamic bearing can be installed in a housing cover which has a second end face. The first end face and the second end face are on the sides of the vane and the housing cover away from each other. The distance between the first end face and the second end face is defined as a fan height. The height of the hydrodynamic bearing is defined as a bearing height. The inner diameter of the hydrodynamic bearing is defined as a bearing inner diameter. The bearing height is from 0.6 mm to 15 mm. The bearing inner diameter is from 0.6 mm to 5 mm. The fan height is from 1 mm to 150 mm. The size of the vane diameter is from 1 mm to 150 mm.

[0006] Preferably, the bearing inner diameter is from 0.6 mm to 2 mm, the bearing height is from 0.6 mm to 2 mm, and the included angle of each of the oil guiding grooves is from 10 degrees to 40 degrees.

[0007] Preferably, the bearing inner diameter is from 2 mm to 5 mm, the bearing height is from 2 mm to 15 mm, and the included angle of each of the oil guiding grooves is from 30 degrees to 90 degrees.

[0008] Preferably, the clearance between the rotating shaft and the hydrodynamic bearing is from 1 μm to 10 μm.

[0009] Preferably, the applicable temperature range of the hydrodynamic bearing is from -40°C to 150°C and the lubricating fluid is an ester oil product, or the applicable temperature range of the hydrodynamic bearing is from -50°C to 250°C and the lubricating fluid is a fluorine-based oil product, or the applicable temperature range of the hydrodynamic bearing is from -50°C to 160°C and the lubricating fluid is a silicone oil product.

[0010] To solve the above technical problems, the present invention provides a combination of a hydrodynamic bearing and a wing plate, comprising: a rotating shaft; a wing plate, one end of the rotating shaft is fixed to the wing plate; and a hydrodynamic bearing having a bearing body with a rotating shaft hole formed therein. At least two oil guiding groove groups are provided on the inner wall of the rotating shaft hole, and each of the oil guiding groove groups includes a plurality of oil guiding grooves which are bent in a V shape. The rotating shaft is inserted into the rotating shaft hole, and a gap is formed between the rotating shaft and the hydrodynamic bearing for accommodating a lubricating fluid; wherein a cusp is formed at the bent portion of each of the oil guiding grooves, and the cusps of the plurality of oil guiding grooves in the same oil guiding groove group form a circumferentially arranged cusp corresponding portion in the rotating shaft hole. An acting area region is formed between the cusp corresponding portions of every two adjacent oil guiding groove groups in the rotating shaft hole, and the mass center of the wing plate and the rotating shaft falls within or near the acting area region. The mass center of the wing plate and the rotating shaft being near the acting area region means that the acting area region forms an acting area length along the axial direction of the hydrodynamic bearing, and the mass center of the wing plate and the rotating shaft is outside the acting area region and within a range of one-tenth of the acting area length from the acting area region.

[0011] Preferably, the outer diameter of the wing plate is defined as a wing diameter. The wing plate has a first end face, and the hydrodynamic bearing can be installed in a housing cover which has a second end face. The first end face and the second end face are located on the sides of the wing plate and the housing cover away from each other. The distance between the first end face and the second end face is defined as a fan height, the height of the hydrodynamic bearing is defined as a bearing height, the inner diameter of the hydrodynamic bearing is defined as a bearing inner diameter. The bearing height is 0.6 mm to 15 mm, the bearing inner diameter is 0.6 mm to 5 mm, the fan height is 1 mm to 150 mm, and the size of the wing diameter is 1 mm to 150 mm.

[0012] Preferably, the bearing inner diameter is 0.6 mm to 2 mm, the bearing height is 0.6 mm to 2 mm, and the included angle of each of the oil guiding grooves is 10 degrees to 40 degrees.

[0013] Preferably, the bearing inner diameter is 2 mm to 5 mm, the bearing height is 2 mm to 15 mm, and the included angle of each of the oil guiding grooves is 30 degrees to 90 degrees.

[0014] Preferably, the gap between the rotating shaft and the hydrodynamic bearing is 1 μm to 10 μm.

[0015] Preferably, the applicable temperature range of the hydrodynamic bearing is -40°C to 150°C, and the lubricating fluid is an ester oil product; or the applicable temperature range of the hydrodynamic bearing is -50°C to 250°C, and the lubricating fluid is a fluorine-based oil product; or the applicable temperature range of the hydrodynamic bearing is -50°C to 160°C, and the lubricating fluid is a silicone oil product.

[0016] The beneficial effect of the present invention is that the hydrodynamic bearing provided by the present invention can be used in combination with a rotating shaft and a wing plate. The inner wall of the rotating shaft hole of the hydrodynamic bearing is provided with at least two oil guiding groove groups. Each oil guiding groove group includes a plurality of oil guiding grooves. A cusp is formed at the bending part of each oil guiding groove. The cusps of the plurality of oil guiding grooves in the same oil guiding groove group form a cusp corresponding part arranged along the circumferential direction in the rotating shaft hole. An acting area region is formed between the cusp corresponding parts of every two adjacent oil guiding groove groups in the rotating shaft hole. The mass centers of the wing plate and the rotating shaft fall within or near the acting area region. Therefore, the hydrodynamic bearing has better supporting force, can support the balanced rotation of the rotating shaft and the wing plate, effectively avoids the mutual collision and wear between the rotating shaft and the bearing body, thereby reducing the generation of noise and vibration, and increasing the service life.

[0017] To further understand the features and technical content of the present invention, please refer to the following detailed description and drawings of the present invention. However, the drawings are only for reference and illustration, and are not intended to limit the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] Figure 1 It is a cross-sectional view of the combination of the hydrodynamic bearing and the wing plate of the present invention.

[0019] Figure 2 It is a cross-sectional view of the hydrodynamic bearing of the present invention.

[0020] Figure 3 It is a three-dimensional view of the hydrodynamic bearing of the present invention. DETAILED DESCRIPTION OF THE INVENTION

[0021] [Embodiment]

[0022] Please refer to Figures 1 to 3 , the present invention provides a hydrodynamic bearing. The hydrodynamic bearing 1 can be used in combination with a rotating shaft 2 and a wing plate 3. The wing plate 3 is the wing plate of a fan. The rotating shaft 2 is arranged on the wing plate 3. The rotating shaft 2 is a cylindrical shaft body. One end of the rotating shaft 2 is fixed to the wing plate 3, so that the rotating shaft 2 is vertically arranged on the wing plate 3. The hydrodynamic bearing 1 can be installed in a housing cover 4. The rotating shaft 2 is fitted with the hydrodynamic bearing 1. The hydrodynamic bearing 1 can support the rotation of the rotating shaft 2 and the wing plate 3. A wear-resistant sheet 5 can also be arranged in the housing cover 4. The other end of the rotating shaft 2 abuts against the wear-resistant sheet 5, so as to reduce the frictional resistance of the rotating shaft 2.

[0023] The hydrodynamic bearing 1 is made of solid material by turning. The hydrodynamic bearing 1 has a bearing body 11 which is a hollow cylinder. The outer wall (outer surface) of the bearing body 11 can be of equal diameter or variable diameter. A rotating shaft hole 12 is formed in the bearing body 11. The rotating shaft hole 12 is a circular hole and can penetrate through both ends of the bearing body 11 and can cooperate with the rotating shaft 2. At least two oil guiding groove groups 13 are provided on the inner wall (inner surface) of the rotating shaft hole 12. The number of the oil guiding groove groups 13 can be two, three, four or more groups, and the number is not limited. Each oil guiding groove group 13 includes a plurality of oil guiding grooves 131. These oil guiding grooves 131 are bent in a V shape, that is, in a herringbone shape, and these oil guiding grooves 131 can be arranged at equal intervals. The rotating shaft 2 is inserted into the rotating shaft hole 12. These oil guiding grooves 131 can be used to guide the lubricating fluid so that the lubricating fluid flows between the rotating shaft 2 and the bearing body 11 and forms pressure concentratedly. Through the supporting force of the oil film, the rotating shaft 2 will not contact the inner wall of the rotating shaft hole 12 when rotating, and the collision and wear between the rotating shaft 2 and the bearing body 11 can be avoided, thereby reducing the generation of noise and vibration.

[0024] The present invention can accommodate the lubricating fluid through the gap between the rotating shaft 2 and the hydrodynamic bearing 1, select different types of oil products (including ester oil products, fluorine-based oil products, silicone oil products), and cooperate with the herringbone-shaped oil guiding groove 131 design to achieve non-contact and stable operation of the hydrodynamic bearing 1 and the rotating shaft 2 under different regional environmental conditions. Preferably, the gap G between the rotating shaft 2 and the hydrodynamic bearing 1 is 1 μm to 10 μm. The gap G between the rotating shaft 2 and the hydrodynamic bearing 1 can be 1 μm, 2 μm, 3 μm, 4 μm, 5 μm, 6 μm, 7 μm, 8 μm, 9 μm or 10 μm, etc., so as to form an optimized gap with better supporting force, so that no collision will occur between the rotating shaft 2 and the hydrodynamic bearing 1, and the generation of noise and vibration can be effectively avoided.

[0025] If the different regional environments include, for example, polar climate, temperate climate, tropical climate, etc., then different categories of oil products (lubricating fluids) are correspondingly selected. The loss rate of the oil product is below 10%, and preferably 3% to 4%. The viscosity of ester-based oil products is easily changed with the ambient temperature, and the applicable temperature range is -40°C to 150°C. For example, it can be applicable to regions such as the equator and North Asia, and can be applicable to electronic products, etc. The viscosity of fluorine-based oil products changes little with the ambient temperature, is relatively stable at high and low temperatures, and the viscosity change is not significant. The applicable temperature range is -50°C to 250°C. For example, it can be applicable to regions such as North Asia and South Asia, and can also be applicable to regions with extremely high and low temperatures, and can be applicable to electronic and automotive products, etc. The viscosity of silicone oil products changes little with the ambient temperature, and the applicable temperature range is -50°C to 160°C. For example, it can be applicable to regions such as the polar regions, and can be applicable to electronic and automotive products, etc. The present invention can be applicable to miniaturized and high-speed products, such as heat dissipation components of 3C products, automobiles (such as electric vehicles), instrument panels, heat dissipation components of unmanned aerial vehicles, e-sports mobile phones, game consoles, projectors, laptop computers, and servers, etc.

[0026] The outer diameter of the wing plate 3 can be defined as a wing diameter A. The wing plate 3 has a first end face 31, and the housing cover 4 has a second end face 41. The first end face 31 and the second end face 41 are located on the sides of the wing plate 3 and the housing cover 4 that are away from each other. The distance between the first end face 31 and the second end face 41 can be defined as a fan height B, and the fan height B can also be regarded as the overall height of the fan. The height of the hydrodynamic bearing 1 can be defined as a bearing height C, and the bearing height C is the length of the hydrodynamic bearing 1 along the axial direction. The inner diameter of the hydrodynamic bearing 1 can be defined as a bearing inner diameter D, and the bearing inner diameter D is the inner diameter of the rotating shaft hole 12.

[0027] The bearing height C and the bearing inner diameter D can be adjusted according to the fan height B and the wing diameter A. The bearing height C is 0.6 mm to 15 mm, and the bearing height C can be 0.6 mm, 0.7 mm, 0.8 mm, 0.9 mm, 1 mm, 2 mm, 3 mm, 4 mm, 5 mm, 7 mm, 9 mm, 10 mm, or 15 mm, etc. The bearing inner diameter D is 0.6 mm to 5 mm, and the bearing inner diameter D can be 0.6 mm, 0.7 mm, 0.8 mm, 0.9 mm, 1 mm, 2 mm, 3 mm, 4 mm, or 5 mm, etc. This embodiment has better supporting force and can effectively avoid the generation of noise and vibration.

[0028] The height B of the fan ranges from 1 mm to 150 mm, and the height B of the fan can be 1 mm, 2 mm, 3 mm, 4 mm, 5 mm, 7 mm, 9 mm, 10 mm, 15 mm, 20 mm, 30 mm, 40 mm, 50 mm, 60 mm, 70 mm, 80 mm, 90 mm, 100 mm, 110 mm, 120 mm, 130 mm, 140 mm or 150 mm, etc. The size of the wing diameter A is from 1 mm to 150 mm, and the size of the wing diameter A can be 1 mm, 2 mm, 3 mm, 4 mm, 5 mm, 7 mm, 9 mm, 10 mm, 15 mm, 20 mm, 30 mm, 40 mm, 50 mm, 60 mm, 70 mm, 80 mm, 90 mm, 100 mm, 110 mm, 120 mm, 130 mm, 140 mm or 150 mm, etc. The sizes of the height B of the fan and the wing diameter A can be adjusted according to market trends. This embodiment has better supporting force and can effectively avoid the generation of noise and vibration.

[0029] In this embodiment, when the inner diameter D of the bearing is from 0.6 mm to 2 mm and the height C of the bearing is from 0.6 mm to 2 mm, the included angle θ of the oil guiding groove 131 is from 10 degrees to 40 degrees, and the included angle θ of the oil guiding groove 131 can be 10 degrees, 15 degrees, 20 degrees, 25 degrees, 30 degrees, 35 degrees or 40 degrees, etc. When the inner diameter D of the bearing is from 2 mm to 5 mm and the height C of the bearing is from 2 mm to 15 mm, the included angle θ of the oil guiding groove 131 is from 30 degrees to 90 degrees, and the included angle θ of the oil guiding groove 131 can be 30 degrees, 35 degrees, 40 degrees, 45 degrees, 50 degrees, 55 degrees, 60 degrees, 65 degrees, 70 degrees, 75 degrees, 80 degrees, 85 degrees or 90 degrees, etc. This embodiment has better supporting force and can effectively avoid the generation of noise and vibration.

[0030] The positions where the oil guiding grooves 131 are arranged can adjust the design parameters according to the magnitude of the force borne by the fan system. A cusp 132 is formed at the bent portion of each oil guiding groove 131. The cusps 132 of the plurality of oil guiding grooves 131 in the same oil guiding groove group 13 are located at the same horizontal height, that is, the cusps 132 of the plurality of oil guiding grooves 131 in the same oil guiding groove group 13 form a cusp corresponding portion 121 arranged along the circumferential direction in the rotating shaft hole 12. The cusps 132 of the plurality of oil guiding grooves 131 in each oil guiding groove group 13 all form a cusp corresponding portion 121 arranged along the circumferential direction in the rotating shaft hole 12. An acting area region E is formed between the cusp corresponding portions 121 of every two adjacent oil guiding groove groups 13 in the rotating shaft hole 12. The mass center F of the wing plate 3 and the rotating shaft 2 falls within the acting area region E or near the acting area region E, so that the hydrodynamic bearing 1 can provide better supporting force for the rotating shaft 2 and the wing plate 3. In this embodiment, the mass center F of the wing plate 3 and the rotating shaft 2 falls within the acting area region E.

[0031] The mass center F of the wing plate 3 and the rotating shaft 2 being close to the acting area region E means that the acting area region E forms an acting area length H along the axial direction of the hydrodynamic bearing 1. The mass center F of the wing plate 3 and the rotating shaft 2 is outside the acting area region E and within the range of one-tenth of the acting area length H from the acting area region E. Thus, even if the mass center F of the wing plate 3 and the rotating shaft 2 does not fall within the acting area region E but is still close to the acting area region E, the hydrodynamic bearing 1 can provide better supporting force for the rotating shaft 2 and the wing plate 3.

[0032] [Advantages of the Embodiment]

[0033] The advantage of the present invention lies in that the hydrodynamic bearing provided by the present invention can be used in combination with a rotating shaft and a wing plate. The inner wall of the rotating shaft hole of the hydrodynamic bearing is provided with at least two groups of oil guiding grooves. Each group of oil guiding grooves includes a plurality of oil guiding grooves. A cusp is formed at the bending position of each oil guiding groove. The cusps of the plurality of oil guiding grooves in the same group of oil guiding grooves form a circumferentially arranged cusp corresponding position in the rotating shaft hole. An acting area region is formed between the cusp corresponding positions of every two adjacent groups of oil guiding grooves in the rotating shaft hole. The mass center of the wing plate and the rotating shaft falls within or close to the acting area region. Therefore, the hydrodynamic bearing has better supporting force, can support the balanced rotation of the rotating shaft and the wing plate, effectively avoids the mutual collision and wear between the rotating shaft and the bearing body, thereby reducing the generation of noise and vibration, and increasing the service life.

[0034] The above are only the preferred embodiments of the present invention and are not intended to limit the patent protection scope of the present invention. Therefore, all equivalent changes made by using the content of the specification and drawings of the present invention are equally included in the scope of the rights protection of the present invention.

Claims

1. A hydrodynamic bearing, characterized in that, It can be used to combine with a rotating shaft and a wing plate. One end of the rotating shaft is fixed to the wing plate. The hydrodynamic bearing has a bearing body, and a rotating shaft hole is formed in the bearing body. At least two groups of oil guiding grooves are provided on the inner wall of the rotating shaft hole. Each group of oil guiding grooves includes a plurality of oil guiding grooves, and these oil guiding grooves are bent in a V shape. The rotating shaft can be inserted into the rotating shaft hole, and a gap is formed between the rotating shaft and the hydrodynamic bearing to accommodate a lubricating fluid. A cusp is formed at the bending position of each oil guiding groove. The cusps of the plurality of oil guiding grooves in the same group of oil guiding grooves form a cusp corresponding position arranged circumferentially in the rotating shaft hole. An acting area region is formed between the cusp corresponding positions of every two adjacent groups of oil guiding grooves in the rotating shaft hole. The mass center of the wing plate and the rotating shaft falls within or near the acting area region. The mass center of the wing plate and the rotating shaft being near the acting area region means that the acting area region forms an acting area length along the axial direction of the hydrodynamic bearing. The mass center of the wing plate and the rotating shaft is outside the acting area region and within a range of one-tenth of the acting area length from the acting area region.

2. The hydrodynamic bearing according to claim 1, characterized in that, The outer diameter of the wing plate is defined as a wing diameter. The wing plate has a first end face. The hydrodynamic bearing can be installed in a housing cover, and the housing cover has a second end face. The first end face and the second end face are located on the sides of the wing plate and the housing cover that are away from each other. The distance between the first end face and the second end face is defined as a fan height. The height of the hydrodynamic bearing is defined as a bearing height. The inner diameter of the hydrodynamic bearing is defined as a bearing inner diameter. The bearing height is 0.6 mm to 15 mm, the bearing inner diameter is 0.6 mm to 5 mm, the fan height is 1 mm to 150 mm, and the size of the wing diameter is 1 mm to 150 mm.

3. The hydrodynamic bearing according to claim 2, characterized in that, The bearing inner diameter is 0.6 mm to 2 mm, the bearing height is 0.6 mm to 2 mm, and the included angle of each oil guiding groove is 10 degrees to 40 degrees.

4. The hydrodynamic bearing according to claim 2, wherein, The bearing inner diameter is 2 mm to 5 mm, the bearing height is 2 mm to 15 mm, and the included angle of each oil guiding groove is 30 degrees to 90 degrees.

5. The hydrodynamic bearing according to claim 1, characterized in that, The gap between the rotating shaft and the hydrodynamic bearing is 1 μm to 10 μm.

6. The hydrodynamic bearing according to claim 1, wherein, The applicable temperature range of the hydrodynamic bearing is -40°C to 150°C, and the lubricating fluid is an ester-based oil product, or the applicable temperature range of the hydrodynamic bearing is -50°C to 250°C, and the lubricating fluid is a fluorine-based oil product, or the applicable temperature range of the hydrodynamic bearing is -50°C to 160°C, and the lubricating fluid is a silicone oil product.

7. A combination of a hydrodynamic bearing and a wing plate, characterized in that, Including: A rotating shaft; A wing plate, with one end of the rotating shaft fixed to the wing plate; And A hydrodynamic bearing, the hydrodynamic bearing having a bearing body, a rotating shaft hole being formed in the bearing body, at least two oil guiding groove groups being provided on the inner wall of the rotating shaft hole, each of the oil guiding groove groups including a plurality of oil guiding grooves, these oil guiding grooves being bent in a V shape, the rotating shaft being inserted into the rotating shaft hole, and a gap being formed between the rotating shaft and the hydrodynamic bearing for accommodating a lubricating fluid; wherein a cusp is formed at the bent portion of each of the oil guiding grooves, and the cusps of the plurality of oil guiding grooves in the same oil guiding groove group form a cusp corresponding portion arranged circumferentially in the rotating shaft hole. An acting area region is formed between the cusp corresponding portions of every two adjacent oil guiding groove groups in the rotating shaft hole. The mass centers of the wing plate and the rotating shaft fall within the acting area region or are close to the acting area region. The mass centers of the wing plate and the rotating shaft being close to the acting area region means that the acting area region forms an acting area length along the axial direction of the hydrodynamic bearing. The mass centers of the wing plate and the rotating shaft are outside the acting area region and within a range of one tenth of the acting area length from the acting area region.

8. The combination of a hydrodynamic bearing and a wing plate according to claim 7, characterized in that, The outer diameter of the wing plate is defined as a wing diameter. The wing plate has a first end face. The hydrodynamic bearing can be installed in a housing cover, and the housing cover has a second end face. The first end face and the second end face are located on the sides of the wing plate and the housing cover that are away from each other. The distance between the first end face and the second end face is defined as a fan height. The height of the hydrodynamic bearing is defined as a bearing height. The inner diameter of the hydrodynamic bearing is defined as a bearing inner diameter. The bearing height is 0.6 mm to 15 mm, the bearing inner diameter is 0.6 mm to 5 mm, the fan height is 1 mm to 150 mm, and the size of the wing diameter is 1 mm to 150 mm.

9. The combination of a hydrodynamic bearing and a wing plate according to claim 8, characterized in that, The bearing inner diameter is 0.6 mm to 2 mm, the bearing height is 0.6 mm to 2 mm, and the included angle of each of the oil guiding grooves is 10 degrees to 40 degrees.

10. The combination of a hydrodynamic bearing and a wing plate according to claim 8, characterized in that, The bearing inner diameter is 2 mm to 5 mm, the bearing height is 2 mm to 15 mm, and the included angle of each of the oil guiding grooves is 30 degrees to 90 degrees.

11. The combination of the hydrodynamic bearing and the wing plate according to claim 7, characterized in that, The gap between the rotating shaft and the hydrodynamic bearing is 1 μm to 10 μm.

12. The combination of the hydrodynamic bearing and the wing plate according to claim 7, characterized in that, The applicable temperature range of the hydrodynamic bearing is -40°C to 150°C, and the lubricating fluid is an ester-based oil product, or the applicable temperature range of the hydrodynamic bearing is -50°C to 250°C, and the lubricating fluid is a fluorine-based oil product, or the applicable temperature range of the hydrodynamic bearing is -50°C to 160°C, and the lubricating fluid is a silicone oil.

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