TWM629486U - Hydrodynamic bearing and combination with wing plate thereof - Google Patents

Abstract

A combination of a fluid dynamic pressure bearing and a wing plate comprises a fluid dynamic pressure bearing, a rotating shaft and a wing plate, the rotating shaft is arranged on the wing plate, and the rotating shaft is inserted into the shaft hole of the fluid dynamic pressure bearing. The inner wall of the shaft hole of the hydrodynamic bearing is provided with at least two oil guide groove groups, each oil guide groove group includes a plurality of oil guide grooves, and a sharp point is formed at the bend of each oil guide groove, The cusps of the multiple oil guide grooves of the same oil guide groove group form a corresponding cusp point arranged along the circumferential direction in the shaft hole, and the cusps of each adjacent two oil guide groove groups in the shaft hole An active area area is formed between the corresponding places, and the mass center of the wing plate and the rotating shaft falls within or close to the active area area. Therefore, the fluid dynamic pressure 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

Hydrodynamic bearing and its combination with wing plate

This creation relates to a hydrodynamic bearing, in particular to a hydrodynamic bearing that can pass fluid between the bearing and the rotating shaft, and generate a pressure field due to the change of the flow speed, so that the rotating shaft can rotate stably without contacting the bearing and its related combination of wings.

In the existing hydrodynamic bearing, oil guide grooves are arranged on the inner wall of the bearing body or the outer wall of the rotating shaft. When the lubricating fluid flows between the rotating shaft and the bearing body, pressure can be concentrated and formed, and the rotating shaft is rotated by the supporting force of the oil film. It will not contact the shaft hole, so it can prevent the shaft and the bearing body from colliding with each other and wear, thereby reducing the generation of noise and vibration, which has become a commonly used bearing technology for today's information products. The hydrodynamic bearing can be installed on the fan's blade to support the rotation of the fan's blade. However, the hydrodynamic bearing cannot provide a better support force between the shaft and the blade, so that there will still be generation between the shaft and the hydrodynamic bearing. Collision, resulting in noise and vibration.

The technical problem to be solved by this creation is to provide a hydrodynamic bearing and its combination with the wing plate in view of the deficiencies of the prior art. There will be no collision between the bearings, which can effectively avoid the generation of noise and vibration.

In order to solve the above-mentioned technical problems, the present invention provides a hydrodynamic bearing, which 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 inside the bearing body. A shaft hole is formed, and the inner wall of the shaft hole is provided with at least two oil guide groove groups, each of the oil guide groove groups includes a plurality of oil guide grooves, and the oil guide 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 for accommodating lubricating fluid; a sharp point is formed at the bend of each of the oil guide grooves, and the same as the The cusps of the plurality of oil guide grooves of the oil guide groove group form a corresponding point in the shaft hole arranged along the circumferential direction, and each adjacent two oil guide groove groups in the shaft hole An active area area is formed between the corresponding points of the cusps, the mass center of the wing plate and the rotating shaft falls in or close to the active area area, and the mass center of the wing plate and the rotating shaft is close to the active area area , means that the action area area forms an action area length along the axial direction of the hydrodynamic bearing, the mass center of the wing plate and the rotating shaft is outside the action area area, and the distance from the action area area is the action area within one-tenth of the area's length.

Preferably, the outer diameter of the wing plate is defined as a wing diameter, the wing plate has a first end surface, the hydrodynamic bearing can be installed in a shell cover, the shell cover has a second end surface, the first end surface And the second end face is located on the side of the wing plate and the shell 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 fluid dynamic pressure bearing is defined as a bearing height, the fluid The inner diameter of the dynamic pressure bearing is defined as a bearing inner diameter, the height of the bearing is 0.6mm to 15mm, the inner diameter of the bearing is 0.6mm to 5mm, the height of the fan is 1mm to 150mm, and the size of the wing diameter is 1mm to 150mm.

In order to solve the above-mentioned technical problems, the present invention provides a combination of a fluid dynamic pressure bearing and a wing plate, including: a rotating shaft; a wing plate, one end of the rotating shaft is fixed to the wing plate; and a fluid dynamic pressure bearing, the fluid dynamic pressure shaft The bearing has a bearing body, a shaft hole is formed in the bearing body, the inner wall of the shaft hole is provided with at least two oil guide groove groups, each of the oil guide groove groups includes a plurality of oil guide grooves, the The oil guide groove is 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 fluid dynamic pressure bearing to accommodate lubricating fluid; wherein the bending of each of the oil guide grooves A sharp point is formed at the fold, and the sharp points of the plurality of oil guide grooves of the same oil guide groove group form a corresponding point of the sharp point arranged along the circumferential direction in the shaft hole. An active area area is formed between the corresponding points of the cusps of each adjacent two oil guide groove groups. The mass center of the wing plate and the rotating shaft falls in or close to the active area area. The mass center of the rotating shaft is close to the active area area, which means that the active area area forms an active area length along the axial direction of the hydrodynamic bearing, the mass center of the wing plate and the rotating shaft is outside the active area area, and The distance from the active area area is within a range of one tenth of the length of the active area.

The beneficial effect of the present invention is that the fluid dynamic pressure bearing provided by the present invention can be combined with the rotating shaft and the wing plate, and the inner wall of the rotating shaft hole of the fluid dynamic pressure bearing is provided with at least two sets of oil guide grooves, each The oil guide groove group includes a plurality of oil guide grooves, and a sharp point is formed at the bend of each oil guide groove, and the sharp points of the multiple oil guide grooves of the same oil guide groove group form a point in the shaft hole Corresponding to the cusps set along the circumferential direction, an active area area is formed between the corresponding cusps of each adjacent two oil guide groove groups in the shaft hole, and the mass center of the wing plate and the rotating shaft falls in the active area area In or near the action area, the hydrodynamic bearing has better supporting force, can support the balanced rotation of the shaft and the wing plate, effectively avoid the collision between the shaft and the bearing body and wear and tear, thereby reducing noise and vibration. , and the service life is increased.

In order to further understand the features and technical content of this creation, please refer to the following detailed descriptions and drawings about this creation, however, the provided drawings are only for reference and description, and are not intended to limit this creation.

The following are specific specific embodiments to illustrate the related embodiments disclosed in the present creation, and those skilled in the art can understand the advantages and effects of the present creation from the content disclosed in this specification. This creation can be implemented or applied through other different specific embodiments, and various details in this specification can also be modified and changed based on different viewpoints and applications without departing from the concept of this creation. In addition, the drawings in this creation are only for simple schematic illustration, and are not drawn according to the actual size, and are stated in advance. The following embodiments will further describe the related technical contents of the present creation in detail, but the disclosed contents are not intended to limit the protection scope of the present creation. In addition, the term "or", as used herein, should include any one or a combination of more of the associated listed items, as the case may be.

[Example]

Please refer to FIG. 1 to FIG. 3 , the present invention provides a fluid dynamic pressure bearing. The fluid dynamic pressure bearing 1 can be combined with a rotating shaft 2 and a wing plate 3 . The wing plate 3 is a fan plate of a fan. The rotating shaft 2 is arranged on the On the wing plate 3 , the rotating shaft 2 is a cylindrical shaft body, and one end of the rotating shaft 2 is fixed to the wing plate 3 , so that the rotating shaft 2 is erected on the wing plate 3 . The fluid dynamic pressure bearing 1 can be installed in a housing cover 4 , the rotating shaft 2 is matched with the fluid dynamic pressure bearing 1 , and the fluid dynamic pressure bearing 1 can support the rotating shaft 2 and the wing plate 3 to rotate. A wear-resistant sheet 5 can also be arranged in the case cover 4 , and the other end of the rotating shaft 2 abuts against the wear-resistant sheet 5 , thereby reducing the frictional resistance of the rotating shaft 2 .

The fluid dynamic pressure bearing 1 is made of solid material by turning. The fluid dynamic pressure bearing 1 has a bearing body 11, the bearing body 11 is a hollow cylinder, and the outer wall (outer surface) of the bearing body 11 can be of equal diameter Or unequal diameter variation, the bearing body 11 is formed with a shaft hole 12, the shaft hole 12 is a circular hole, the shaft hole 12 can penetrate to both ends of the bearing body 11, the shaft hole 12 can be matched with the shaft 2 . The inner wall (inner surface) of the shaft hole 12 is provided with at least two sets of oil guide grooves 13 , and the number of sets of oil guide grooves 13 can be set in two, three or four groups, and the number is not limited. Each oil guide groove group 13 includes a plurality of oil guide grooves 131 , the oil guide grooves 131 are bent in a V shape, that is, a herringbone shape, and the oil guide grooves 131 can be arranged at equal intervals set up. The rotating shaft 2 is inserted into the rotating shaft hole 12 , and the 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 concentrates to form pressure, through the supporting force of the oil film , so that the rotating shaft 2 will not contact the inner wall of the rotating shaft hole 12 when rotating, which can prevent the rotating shaft 2 and the bearing body 11 from colliding with each other and wear, thereby reducing noise and vibration.

This creation can accommodate lubricating fluid through the gap between the rotating shaft 2 and the hydrodynamic bearing 1, and select different types of oil (including ester oil, fluorine oil, silicone oil), and match with The herringbone-shaped oil guide groove 131 is designed 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, and 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, 7μm, 8μm, 9μ or 10μm, etc., to form an optimized gap, with better support force, so that there will be no collision between the rotating shaft 2 and the hydrodynamic bearing 1, which can effectively avoid the generation of noise and vibration.

The different regional environments include, for example, polar climates, temperate climates, and tropical climates, etc., then different types of oils (lubricating fluids) are selected correspondingly. The loss rate of oil products is less than 10%, and the loss rate of oil products is preferably 3%. to 4%. The viscosity of ester oils is easy to change with the ambient temperature, and the applicable temperature range is -40°C to 150°C. For example, it can be applied to the equator, North Asia, etc. The viscosity of fluorine-based oils varies little with the ambient temperature, and is relatively stable at high and low temperatures, with little change in viscosity. The applicable temperature range is -50°C to 250°C. For example, it can be used in North Asia, South Asia and other regions. In extremely high and low temperature areas, it can be applied to electronic, automotive products, etc. The viscosity of silicone oil varies little with the ambient temperature, and the applicable temperature range is -50°C to 160°C. This creation can be applied to miniaturized, high-speed products, such as 3C products, cooling components for automobiles (such as electric vehicles), dashboards, cooling components for drones, gaming mobile phones, game consoles, projectors, and notebook computers and servers, etc.

The outer diameter of the wing plate 3 can be defined as a wing diameter A, the wing plate 3 has a first end surface 31 , the cover 4 has a second end surface 41 , and the first end surface 31 and the second end surface 41 are located between the wing plate 3 and the second end surface 41 . The distance between the first end surface 31 and the second end surface 41 on the side of the case cover 4 away from each other 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 fluid dynamic bearing 1 can be defined as a bearing height C, the bearing height C is the length of the fluid dynamic bearing 1 along the axial direction, and the inner diameter of the fluid dynamic bearing 1 can be defined as a bearing inner diameter D , the inner diameter D of the bearing is the inner diameter of the shaft hole 12 .

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

The height B of the fan is 1mm to 150mm, and the height B of the fan can be 1mm, 2mm, 3mm, 4mm, 5mm, 7mm, 9mm, 10mm, 15mm, 20mm, 30mm, 40mm, 50mm, 60mm, 70mm, 80mm, 90mm, 100mm , 110mm, 120mm, 130mm, 140mm or 150mm, etc. The size of the wing diameter A is 1mm to 150mm, and the size of the wing diameter A can be 1mm, 2mm, 3mm, 4mm, 5mm, 7mm, 9mm, 10mm, 15mm, 20mm, 30mm, 40mm, 50mm, 60mm, 70mm, 80mm , 90mm, 100mm, 110mm, 120mm, 130mm, 140mm or 150mm, etc. The size of the fan height B 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.

In this embodiment, when the inner diameter D of the bearing is 0.6 mm to 2 mm, and the height C of the bearing is 0.6 mm to 2 mm, the included angle θ of the oil guiding groove 131 is 10 degrees to 40 degrees, and the oil guiding groove The included angle θ of 131 may be 10 degrees, 15 degrees, 20 degrees, 25 degrees, 30 degrees, 35 degrees, or 40 degrees. When the bearing inner diameter D is 2mm to 5mm, and the bearing height C is 2mm to 15mm, the included angle θ of the oil guide groove 131 is 30° to 90°, and the included angle θ of the oil guide groove 131 can be 30° , 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.

The positions of the oil guide grooves 131 can be adjusted according to the design parameters of the fan system. A sharp point 132 is formed at the bend of each oil guide groove 131 , and the sharp points 132 of the plurality of oil guide grooves 131 of the same oil guide groove group 13 are located at the same level, that is, the same oil guide groove The cusps 132 of the plurality of oil guide grooves 131 of the groove group 13 form a cusp corresponding point 121 arranged in the circumferential direction in the shaft hole 12 . The plurality of guide grooves of each oil guide groove group 13 The cusps 132 of the oil grooves 131 are formed with corresponding cusps 121 arranged in the circumferential direction in the shaft hole 12 , and the cusps 121 of each adjacent two oil guide groove groups 13 in the shaft hole 12 correspond to the cusps 121 . An active area area E is formed therebetween, and the mass center F of the wing plate 3 and the rotating shaft 2 falls within the active area area E or is close to the active area area E, so that the hydrodynamic shaft 1 can provide a better balance between the rotating shaft 2 and the wing plate 3. Support strength. In this embodiment, the mass center F of the wing plate 3 and the rotating shaft 2 falls within the action area region E.

The mass center F of the wing plate 3 and the rotating shaft 2 is close to the active area area E, which means that the active area area E forms an active area length H along the axial direction of the hydrodynamic bearing 1. The mass center of the wing plate 3 and the rotating shaft 2 F is outside the active area area E, and the distance from the active area area E is within the range of one tenth of the active area length H, so even if the mass center F of the wing plate 3 and the rotating shaft 2 does not fall in the active area area E Inside, but still close to the action area area E, the hydrodynamic shaft 1 can also provide a better support force for the rotating shaft 2 and the wing plate 3 .

[Advantageous effects of the embodiment]

The beneficial effect of the present invention is that the fluid dynamic pressure bearing provided by the present invention can be combined with the rotating shaft and the wing plate, and the inner wall of the rotating shaft hole of the fluid dynamic pressure bearing is provided with at least two sets of oil guide grooves, each The oil guide groove group includes a plurality of oil guide grooves, and a sharp point is formed at the bend of each oil guide groove, and the sharp points of the multiple oil guide grooves of the same oil guide groove group form a point in the shaft hole Corresponding to the cusps set along the circumferential direction, an active area area is formed between the corresponding cusps of each adjacent two oil guide groove groups in the shaft hole, and the mass center of the wing plate and the rotating shaft falls in the active area area In or near the action area, the hydrodynamic bearing has better supporting force, can support the balanced rotation of the shaft and the wing plate, effectively avoid the collision between the shaft and the bearing body and wear and tear, thereby reducing noise and vibration. , and the service life is increased.

The contents disclosed above are only the preferred and feasible embodiments of this creation, and are not intended to limit the scope of the patent application of this creation. Therefore, any equivalent technical changes made by using the descriptions and drawings of this creation are included in the application for this creation. within the scope of the patent.

1: Hydrodynamic bearing 11: Bearing body 12: Shaft hole 121: Corresponding point of sharp point 13: Oil guide groove group 131: oil guide groove 132: sharp point 2: Spindle 3: wing plate 31: The first end face 4: Shell cover 41: Second end face 5: Wear-resistant sheet A: wing diameter B: Fan height C: Bearing height D: bearing inner diameter E: Action area area F: The mass center of the wing plate and the shaft G: Clearance between the shaft and the hydrodynamic bearing H: the length of the active area θ: The included angle of the oil guide groove

FIG. 1 is a cross-sectional view of a combination of a hydrodynamic bearing and a wing plate of the invention.

FIG. 2 is a cross-sectional view of a fluid dynamic bearing of the present invention.

FIG. 3 is a perspective view of a fluid dynamic bearing of the present invention.

1: Hydrodynamic bearing

11: Bearing body

12: Shaft hole

121: Corresponding point of sharp point

2: Spindle

3: wing plate

31: The first end face

4: Shell cover

41: Second end face

5: Wear-resistant sheet

A: wing diameter

B: Fan height

C: Bearing height

D: bearing inner diameter

E: Action area area

F: The mass center of the wing plate and the shaft

G: Clearance between the shaft and the hydrodynamic bearing

H: the length of the active area

Claims (12)

A fluid dynamic pressure bearing can be used to combine with a rotating shaft and a wing plate, one end of the rotating shaft is fixed on the wing plate, the fluid dynamic pressure bearing has a bearing body, a rotating shaft hole is formed in the bearing body, and the inner part of the rotating shaft hole is The wall is provided with at least two oil guide groove groups, each of the oil guide groove groups includes a plurality of oil guide grooves, the oil guide grooves are bent in a V shape, and the rotating shaft can be inserted into the rotating shaft hole , a gap is formed between the rotating shaft and the hydrodynamic bearing to accommodate lubricating fluid; A cusp is formed at the bend of each of the oil guide grooves, and the cusps of the plurality of oil guide grooves in the same set of oil guide grooves form a ring arranged along the circumferential direction in the shaft hole. At the corresponding point of the cusp, an action area is formed between the corresponding positions of the cusp points of each adjacent two oil guide groove groups in the shaft hole, and the mass center of the wing plate and the shaft falls within the action area area or Close to the active area area, the mass center of the wing plate and the rotating shaft is close to the active area area, which means that the active area area forms an active area length along the axial direction of the hydrodynamic bearing, and the distance between the wing plate and the rotating shaft is The center of mass is outside the active area, and the distance from the active area is within a range of one tenth of the length of the active area. The hydrodynamic bearing according to claim 1, wherein the outer diameter of the wing plate is defined as a wing diameter, the wing plate has a first end surface, and the hydrodynamic bearing can be installed in a shell cover, the shell cover has A second end surface, the first end surface and the second end surface are located on the side of the wing plate and the casing cover away from each other, the distance between the first end surface and the second end surface is defined as a fan height, the fluid dynamic pressure bearing The height is defined as the height of a bearing, the inner diameter of the hydrodynamic bearing is defined as the inner diameter of a bearing, the height of the bearing is 0.6mm to 15mm, the inner diameter of the bearing is 0.6mm to 5mm, the height of the fan is 1mm to 150mm, the The size of the wing diameter is 1mm to 150mm. The hydrodynamic bearing according to claim 2, wherein the inner diameter of the bearing is 0.6 mm to 2 mm, the height of the bearing is 0.6 mm to 2 mm, and the included angle of each of the oil guide grooves is 10 degrees to 40 degrees. The hydrodynamic bearing according to claim 2, wherein the inner diameter of the bearing is 2 mm to 5 mm, the height of the bearing is 2 mm to 15 mm, and the included angle of each of the oil guide grooves is 30 degrees to 90 degrees. The fluid dynamic pressure bearing of claim 1, wherein a gap between the rotating shaft and the fluid dynamic pressure bearing is 1 μm to 10 μm. The fluid dynamic pressure bearing according to claim 1, wherein the applicable temperature range of the fluid dynamic pressure bearing is -40°C to 150°C, the lubricating fluid is ester oil, or the applicable temperature range of the fluid dynamic pressure bearing is -50°C to 250°C, the lubricating fluid is fluorine oil, or the applicable temperature range of the fluid dynamic bearing is -50°C to 160°C, and the lubricating fluid is silicone oil. 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 fluid dynamic pressure bearing, the fluid dynamic pressure bearing has a bearing body, a shaft hole is formed in the bearing body, the inner wall of the shaft hole is provided with at least two sets of oil guide grooves, each set of oil guide grooves Including a plurality of oil guide grooves, the oil guide grooves are bent in a V shape, the shaft is inserted into the shaft hole, and a gap is formed between the shaft and the fluid dynamic pressure bearing to accommodate lubricating fluid; A cusp is formed at the bend of each of the oil guide grooves, and the cusps of the plurality of oil guide grooves in the same oil guide groove group form a ring in the shaft hole along the circumferential direction. A working area is formed between the corresponding cusps of the two adjacent oil guide groove groups in the shaft hole, and the mass center of the wing plate and the rotating shaft falls within the working area. Or close to the active area area, the mass center of the wing plate and the rotating shaft is close to the active area area, which means that the active area area forms an active area length along the axial direction of the hydrodynamic bearing, the wing plate and the rotating shaft. The center of mass is outside the active area, and the distance from the active area is within the range of one tenth of the length of the active area. The combination of a hydrodynamic bearing and a wing plate according to claim 7, wherein the outer diameter of the wing plate is defined as a wing diameter, the wing plate has a first end surface, and the hydrodynamic bearing can be installed in a shell cover , the shell cover has a second end surface, the first end surface and the second end surface are located on the side of the wing plate and the shell cover away from each other, the distance between the first end surface and the second end surface is defined as a fan height, the The height of the fluid dynamic bearing is defined as a bearing height, the inner diameter of the fluid dynamic bearing is defined as a bearing inner diameter, the bearing height is 0.6mm to 15mm, the bearing inner diameter is 0.6mm to 5mm, the fan height is 1mm to 150mm, the size of this wing diameter is 1mm to 150mm. The combination of a hydrodynamic bearing and a wing plate according to claim 8, wherein the inner diameter of the bearing is 0.6mm to 2mm, the height of the bearing is 0.6mm to 2mm, and the included angle of each of the oil guide grooves is 10 degrees to 40 degrees. The combination of a hydrodynamic bearing and a wing plate according to claim 8, wherein the inner diameter of the bearing is 2mm to 5mm, the height of the bearing is 2mm to 15mm, and the included angle of each of the oil guide grooves is 30° to 90° Spend. The combination of a hydrodynamic bearing and a wing plate according to claim 7, wherein the gap between the rotating shaft and the hydrodynamic bearing is 1 μm to 10 μm. The combination of a hydrodynamic bearing and a wing plate according to claim 7, wherein the applicable temperature range of the hydrodynamic bearing is -40°C to 150°C, the lubricating fluid is an ester oil, or the hydrodynamic bearing The applicable temperature range is -50°C to 250°C, and the lubricating fluid is fluorine oil, or the applicable temperature range of the fluid dynamic bearing is -50°C to 160°C, and the lubricating fluid is silicone oil.

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