CN212615888U

CN212615888U - Bearing system and thrust plate thereof

Info

Publication number: CN212615888U
Application number: CN202020262243.3U
Authority: CN
Inventors: 洪银树; 谢坤利; 张怡鑫
Original assignee: Sunonwealth Electric Machine Industry Co Ltd
Current assignee: Sunonwealth Electric Machine Industry Co Ltd
Priority date: 2020-02-25
Filing date: 2020-03-05
Publication date: 2021-02-26
Anticipated expiration: 2030-03-05
Also published as: TWI715450B; CN211670722U; TW202132695A; CN113374782A

Abstract

The utility model provides a bearing system and thrust plate thereof for solve the problem that current bearing system is difficult to promote the dynamic pressure. The thrust plate of the utility model comprises a body and a plurality of dynamic pressure grooves, wherein the dynamic pressure grooves are annularly arranged on the periphery of the inner edge of the body, and each dynamic pressure groove is provided with a turning part positioned between an inner arc section and an outer arc section; the extending direction of the inner arc section from the turning part to the inner edge is opposite to the rotating direction of the thrust plate, and the extending direction of the outer arc section from the turning part to the outer edge is opposite to the rotating direction of the thrust plate; or, the extending direction of the inner arc section from the turning part to the inner edge is the same as the rotating direction of the thrust plate, the extending direction of the outer arc section from the turning part to the outer edge is the same as the rotating direction of the thrust plate, and the turning part of each dynamic pressure groove is communicated with one liquid storage cavity.

Description

Bearing system and thrust plate thereof

Technical Field

The utility model discloses a spare part of motor or fan, especially a bearing system and thrust plate thereof.

Background

Referring to fig. 1, which is a conventional thrust plate 9 used in a bearing system of a motor or a fan, an axial end surface 91 of the conventional thrust plate 9 is recessed with a plurality of dynamic pressure grooves 92, each dynamic pressure groove 92 is generally in a herringbone shape, and has a middle bending portion 921 connecting an inner portion 922 and an outer portion 923; the extending direction of the inner portion 922 of each dynamic pressure groove 92 from the middle curved portion 921 to the inside is the same as the rotating direction of the thrust plate 9 (indicated by the hollow arrow in fig. 1), and the extending direction of the outer portion 923 of each dynamic pressure groove 92 from the middle curved portion 921 to the outside is the same as the rotating direction of the thrust plate 9. In operation, oil in the bearing system can smoothly flow from the inner portion 922 to the outer portion 923 through the middle bend 921. An embodiment similar to the prior art bearing system 9 is disclosed in chinese patent publication nos. CN1619170A and CN 1914429A.

Although the dynamic pressure generated by the conventional thrust plate 9 has a good performance, it is still necessary to improve the dynamic pressure to further improve the performance of the motor or the fan during operation.

SUMMERY OF THE UTILITY MODEL

To solve the above problems, an object of the present invention is to provide a bearing system and a thrust plate thereof, which can further improve dynamic pressure by a dynamic pressure groove having a simple shape and easy to form.

The utility model discloses a next purpose provides a bearing system and thrust plate thereof can promote smooth and easy degree of fluid circulation and circulation effect.

It is still another object of the present invention to provide a bearing system and a thrust plate thereof, which can improve the rotational stability of the thrust plate.

Another object of the present invention is to provide a bearing system and a thrust plate thereof, which can improve the convenience of manufacturing and assembling.

In the present invention, the directions or the similar terms thereof, such as "front", "back", "left", "right", "top", "bottom", "inner", "outer", "side", etc., refer to the directions of the drawings, and the directions or the similar terms thereof are only used to assist the explanation and understanding of the embodiments of the present invention, but not to limit the present invention.

The elements and components described throughout the present invention are referred to by the term "a" or "an" merely for convenience and to provide a general meaning of the scope of the invention; in the present invention, it is to be understood that one or at least one is included, and a single concept also includes a plurality unless it is obvious that other meanings are included.

The present invention relates to a method for manufacturing a semiconductor device, and more particularly to a method for manufacturing a semiconductor device, which can be used for manufacturing a semiconductor device, and a semiconductor device manufactured by the method.

The utility model discloses bearing system's thrust plate, include: a body having an inner edge and an outer edge; and a plurality of dynamic pressure grooves which are annularly arranged on the periphery of the inner edge, wherein each dynamic pressure groove is provided with a turning part positioned between an inner arc section and an outer arc section, and the inner arc section is positioned between the turning part and the inner edge; the extending direction of the inner arc section from the turning part to the inner edge is opposite to the rotating direction of the thrust plate, and the extending direction of the outer arc section from the turning part to the outer edge is opposite to the rotating direction of the thrust plate; or, the extending direction of the inner arc section from the turning part to the inner edge is the same as the rotating direction of the thrust plate, the extending direction of the outer arc section from the turning part to the outer edge is the same as the rotating direction of the thrust plate, and the turning part of each dynamic pressure groove is communicated with one liquid storage cavity.

The utility model discloses a bearing system contains: a sleeve; a bearing located inside the sleeve; and a rotating member having a thrust plate and a rotating shaft, the inner edge of the thrust plate being connected to the rotating shaft, the thrust plate being capable of forming a dynamic pressure gap with the bearing when rotating.

Therefore, the bearing system and the thrust plate thereof of the present invention can make the extending direction of the inner arc section from the turning part to the inner edge opposite to the rotation direction of the thrust plate, and the extending direction of the outer arc section from the turning part to the outer edge opposite to the rotation direction of the thrust plate; or the extending direction of the inner arc section from the turning part to the inner edge is the same as the rotating direction of the thrust plate, the extending direction of the outer arc section from the turning part to the outer edge is the same as the rotating direction of the thrust plate, and a liquid storage cavity is arranged at the turning part of each dynamic pressure groove, thereby achieving the effect of further improving dynamic pressure by using a simple and easily formed dynamic pressure groove form.

The thrust plate of the bearing system may further include an inner ring groove, and the inner ring groove and a plurality of dynamic pressure grooves may be located at an end surface of the body, the inner ring groove being adjacent to the inner edge, and each dynamic pressure groove may communicate with the inner ring groove. Therefore, the oil in the movable pressure grooves can circulate, and the oil circulation device has the effects of improving the smoothness of oil circulation, improving the circulation effect and the like.

Wherein, two relative terminal surfaces of this body can all be equipped with a plurality of and move and press the ditch. Therefore, the rotation stability of the thrust plate is improved.

Wherein, a boss is arranged between any two adjacent dynamic pressure grooves, the side wall of the boss is provided with a starting point and an end point, the starting point is adjacent to the inner edge of the body, and the end point can be positioned at the outer edge of the body. Therefore, the oil circulation device has the effects of improving the smoothness of oil circulation, improving the circulation effect and the like.

Wherein, a boss is arranged between any two adjacent dynamic pressure grooves, the body is provided with a hole center, and the arc length of the boss and the dynamic pressure groove on the same circumference taking the hole center as the center can be approximately equal. Therefore, the width of the boss and the dynamic pressure groove can be approximately equal, and the bearing system has the effects of improving the dynamic pressure of the bearing system and the rotation stability of the thrust plate and the like.

The number of the dynamic pressure grooves can be more than or equal to 10, and a plurality of dynamic pressure grooves can be annularly arranged on the periphery of the inner edge at equal intervals. Therefore, the dynamic pressure of the bearing system and the rotation stability of the thrust plate are improved.

The body is provided with a hole center, and the sharp points of the plurality of bosses can be positioned on the same circumference taking the hole center as the center. Therefore, the dynamic pressure generating device has the effects of improving the uniformity of dynamic pressure generated by the bearing system and the like.

Wherein, the extending direction of the inner arc section from the turning part to the inner edge is opposite to the rotating direction of the thrust plate, and the radial distance (D1) from the sharp point to the inner edge of the body can be smaller than the radial distance (D2) from the sharp point to the outer edge of the body. Therefore, the dynamic pressure of the bearing system is improved.

Wherein, the extension direction of the inner arc section from the turning part to the inner edge is opposite to the rotation direction of the thrust plate, the side wall of the boss is provided with a starting point and an end point, and the ratio (D3/D4) of the radial distance (D3) of the circumference from the starting point to the sharp point to the radial distance (D4) from the starting point to the outer edge of the body is about 0.1-0.3. Therefore, the dynamic pressure of the bearing system is improved.

Wherein, the extension direction of the inner arc section from the turning part to the inner edge is opposite to the rotation direction of the thrust plate, the side wall of the boss has a starting point and an end point, and the ratio (D4/U) of the radial distance (D4) from the starting point to the outer edge of the body to the total length (U) of the side wall of the boss from the starting point to the end point is about 0.2-0.7. Therefore, the dynamic pressure of the bearing system is improved.

The extending direction of the inner arc section from the turning part to the inner edge is opposite to the rotating direction of the thrust plate, and the turning part of each dynamic pressure groove can be communicated with one liquid storage cavity. Therefore, the speed of the oil flowing to the outer arc section can be delayed, and the dynamic pressure of the bearing system is further improved.

Wherein, the extending direction of the inner arc section from the turning part to the inner edge is the same as the rotating direction of the thrust plate, and the radial distance (D1) from the sharp point to the inner edge of the body can be larger than or equal to the radial distance (D2) from the sharp point to the outer edge of the body. Therefore, the dynamic pressure of the bearing system is improved.

Wherein, the extending direction of the inner arc section from the turning part to the inner edge is the same as the rotating direction of the thrust plate, and the ratio (T1/T2) of the linear distance (T1) from the end of the liquid storage cavity to the adjacent sharp point to the linear distance (T2) between any two adjacent sharp points is about 0.4-0.45. Therefore, the dynamic pressure of the bearing system is improved.

Wherein, the extension direction of the inner arc section from the turning part to the inner edge is the same as the rotation direction of the thrust plate, the side wall of the boss has a starting point and an end point, and the ratio (D2/D4) of the radial distance (D2) from the sharp point to the outer edge of the body to the radial distance (D4) from the starting point to the outer edge of the body is about 0.2-0.4. Therefore, the dynamic pressure of the bearing system is improved.

The extending direction of the inner arc section from the turning part to the inner edge is the same as the rotating direction of the thrust plate, the side wall of the boss is provided with a starting point and an end point, a first chord passes through the sharp point and the starting point, a second chord passes through the sharp point and the end point, and the included angle between the first chord and the second chord is about 50-60 degrees. Therefore, the dynamic pressure of the bearing system is improved.

The sleeve may have a shoulder inside, and an inner surface of the bearing may abut against the shoulder, so that the inner surface and a closed end of the sleeve may be axially opposite and spaced apart. Therefore, the rotary part has the effects of improving the assembly convenience, the rotation smoothness of the rotary part and the like.

The sleeve can be internally provided with a groove which can be concavely arranged at one closed end of the sleeve, one end of the rotating shaft can extend into the groove, and the other end of the rotating shaft can protrude out of the bearing. Therefore, the groove can be used as a space for storing oil, and has the effects of improving the assembly convenience, the rotating smoothness of the rotating part and the like.

The rotating shaft may have a ring groove, and the ring groove may be adjacent to an end of the bearing away from the thrust plate. Therefore, when the oil rises to the ring groove, the oil is not easy to continue to flow upwards, and the bearing system has the effects of preventing the oil from overflowing and the like.

Drawings

The present invention will be described in further detail with reference to the accompanying drawings and specific embodiments.

FIG. 1: a schematic plane structure of a conventional thrust plate;

FIG. 2: the utility model discloses an exploded perspective view of a first embodiment;

FIG. 3: the utility model discloses the combined sectional view of the first embodiment;

FIG. 4: the plane structure of the thrust plate of the first embodiment of the present invention is schematically illustrated;

FIG. 5: an enlarged view of a portion of the structure shown in FIG. 4;

FIG. 6: the enlarged view of a partial structure of another aspect of the thrust plate according to the first embodiment of the present invention;

FIG. 7: an exploded perspective view of a second embodiment of the present invention;

FIG. 8: the plane structure of the thrust plate according to the second embodiment of the present invention is schematically illustrated;

FIG. 9: as shown in the enlarged view of the partial structure in fig. 8.

Description of the reference numerals

[ utility model ] to solve the problems

1: sleeve

11 opening of the container

12: closed end

13 shoulder part

14: a groove

2: bearing

21 inner surface

3: rotating member

3a thrust plate

3b rotating shaft

31 main body

311 end face

32 dynamic pressure groove

321 turning part

322 inner arc section

323 outer arc segment

33: boss

331: side wall

332 point of the tip

34 inner ring groove

35 ring groove

36 reservoir cavity

B bearing system

C, hole center

D, direction of rotation

D1, D2, D3, D4 radial distances

E1 inner edge

E2 outer edge

G dynamic pressure gap

L is a connecting line

L1 first chord

L2 second chord

P is the point of intersection

P1 starting point

P2 endpoint

R is circumference

S rotation axis

T1, T2 straight-line distance

Total length of U

U1, U2 arc length

Angle of theta 1, theta 2, alpha

[ conventional ]

9: thrust plate

91 axial end face

92 dynamic pressure groove

921 middle bent part

922 inner part

923, the outer side part.

Detailed Description

In order to make the above and other objects, features and advantages of the present invention more comprehensible, preferred embodiments accompanied with figures are described in detail as follows:

referring to fig. 2 and fig. 3, a first embodiment of the bearing system B of the present invention includes a sleeve 1, a bearing 2 and a rotating member 3, wherein the bearing 2 is located inside the sleeve 1, and the rotating member 3 is rotatably disposed on the bearing 2.

The sleeve 1 can be a hollow cup shape for accommodating the bearing 2 and injecting oil; in this embodiment, the sleeve 1 may have an opening 11 and a closed end 12 opposite to each other, the bearing 2 may be inserted into the sleeve 1 through the opening 11, and the closed end 12 may completely close the bottom end of the sleeve 1, thereby effectively preventing oil inside the sleeve 1 from leaking. The interior of the sleeve 1 can additionally have a shoulder 13, so that the bearing 2 introduced from the opening 11 can abut against the shoulder 13. The sleeve 1 may also have a groove 14 formed therein, the groove 14 being optionally recessed in the closed end 12 such that the groove 14 is axially opposite the rotor 3, the groove 14 serving as a space for oil storage or partial penetration of the rotor 3.

The bearing 2 is located inside the sleeve 1, and the bearing 2 can abut against the shoulder 13 by an inner surface 21, so that the inner surface 21 can be axially opposite to and spaced apart from the closed end 12 of the sleeve 1. Wherein, the bearing 2 can be tightly fitted and combined with the inner annular surface of the sleeve 1, and the outer end of the joint is preferably laser welded, so as to improve the combination stability of the bearing 2 and the sleeve 1.

The rotating member 3 has a thrust plate 3a and a rotating shaft 3b, the thrust plate 3a has a main body 31, the main body 31 has an inner edge E1 and an outer edge E2, and the inner edge E1 of the thrust plate 3a is connected to the rotating shaft 3 b. More specifically, in the present embodiment, the body 31 of the thrust plate 3a may be generally annular, so that the rotating shaft 3b can penetrate through the body 31, and the inner edge E1 of the body 31 is connected to the rotating shaft 3b, for example, by tight fit, preferably by laser welding at the connection; in other embodiments, the thrust plate 3a and the shaft 3b may be integrally connected, in other words, the thrust plate 3a may be regarded as a portion extending outward from the outer ring surface of the shaft 3b, and the inner edge E1 of the body 31 is located at the outer ring surface of the thrust plate 3a connected to the shaft 3 b.

The thrust plate 3a is located between the bearing 2 and the closed end 12 of the sleeve 1, the rotating shaft 3b penetrates through the bearing 2, in this embodiment, one end of the rotating shaft 3b can extend into the groove 14 in the sleeve 1, and the other end can protrude out of the bearing 2 for connecting with a rotor of a motor or a fan. The thrust plate 3a and the rotating shaft 3b can rotate synchronously around a rotation axis S, and the thrust plate 3a can form a dynamic pressure gap G with the bearing 2 during rotation, so that the thrust plate 3a does not contact with the bearing 2 during rotation, thereby reducing noise generated by rotation.

Referring to fig. 2 and 4, the thrust plate 3a has a plurality of dynamic pressure grooves 32, and the dynamic pressure grooves 32 may be arranged around the outer periphery of the inner edge E1 at equal intervals. Each dynamic pressure groove 32 has a turning part 321 located between an inner arc section 322 and an outer arc section 323, and the inner arc section 322 is located between the turning part 321 and the inner edge E1; in the present embodiment, each dynamic pressure groove 32 may have a generally chevron shape, and the number of the dynamic pressure grooves 32 may be greater than or equal to 10 to provide a suitable dynamic pressure effect.

A boss 33 is provided between any two adjacent dynamic pressure grooves 32, and both sidewalls 331 of each boss 33 respectively have a starting point P1 and an end point P2, the starting point P1 is adjacent to the inner edge E1 of the body 31, and the end point P2 can be located at the outer edge E2 of the body 31. In addition, in each dynamic pressure groove 32 of the present embodiment, the extending direction of the inner arc section 322 from the turning part 321 to the inner edge E1 is opposite to the rotating direction D of the thrust plate 3a, and the extending direction of the outer arc section 323 from the turning part 321 to the outer edge E2 is also opposite to the rotating direction D of the thrust plate 3 a.

The sidewall 331 of the protrusion 33 may have a sharp point 332, and the sharp point 332 approximately corresponds to the turning portion 321 of the dynamic pressure groove 231. The radial distance D1 from the point 332 to the inner edge E1 of the body 31 may be less than the radial distance D2 from the point 332 to the outer edge E2 of the body 31.

Referring to fig. 4 and 5, the body 31 has a hole center C passing through the rotation axis S (shown in fig. 3), and the sharp points 332 of the plurality of bosses 33 may be located on the same circumference R centered on the hole center C. The ratio (D3/D4) of the radial distance D3 from the starting point P1 to the circumference R through which the sharp point 332 passes to the radial distance D4 from the starting point P1 to the outer edge E2 of the body 31 is about 0.1-0.3. The ratio (D4/U) of the radial distance D4 from the starting point P1 to the outer edge E2 of the body 31 to the total length U (shown by the thick line in FIGS. 4 and 5) of the sidewall 331 of the boss 33 from the starting point P1 to the end point P2 is about 0.2-0.7; preferably, the two sidewalls 331 of the protrusion 33 have the same total length U from the starting point P1 to the ending point P2.

Further, the width of the boss 33 and the dynamic pressure groove 32 may be set to be equal; that is, the arcuate lengths U1 and U2 (indicated by thick lines in fig. 5) of the boss 33 and the dynamic pressure groove 32 on the same circumference R around the hole center C are equal. In the present embodiment, the arc lengths U1 and U2 of the dynamic pressure groove 32 and the boss 33 may be equal to each other on any one of the circumferences R centered on the hole center C. In other words, any one of the circles R may form three intersection points P on the two adjacent bosses 33 and the dynamic pressure groove 32, the three intersection points P may form three connecting lines L with the hole center C, the three connecting lines L may form two included angles θ 1 and θ 2, and the two included angles θ 1 and θ 2 are substantially equal to each other, so that the arc lengths U1 and U2 of the two adjacent bosses 33 and the dynamic pressure groove 32 on the circle R are also substantially equal to each other. It should be noted that, although fig. 5 illustrates the circumference R through which the sharp point 332 passes, the circumference R is not limited thereto, and any circumference R that intersects with the dynamic pressure grooves 32 and that is centered on the hole center C has the above-described characteristics.

The thrust plate 3a may further have an inner annular groove 34, the inner annular groove 34 being adjacent to the inner edge E1, and each dynamic pressure groove 32 communicating with the inner annular groove 34 to allow oil in the plurality of dynamic pressure grooves 32 to flow therethrough. As shown in fig. 3, the inner ring groove 34 and the plurality of dynamic pressure grooves 32 may be located on an end surface 311 of the body 31 facing the bearing 2, and preferably, the inner ring groove 34 and the plurality of dynamic pressure grooves 32 are disposed on both end surfaces 311 of the body 31. The groove 14 of the sleeve 1 can be aligned within the radial extent of the inner annular groove 34. Alternatively, the shaft 3B may have an annular groove 35, and the annular groove 35 may be adjacent to the end of the bearing 2 away from the thrust plate 3a, so that the oil does not flow upward until the annular groove 35, thereby preventing the oil from overflowing the bearing system B.

Referring to fig. 3 and 4, according to the above-described structure, the bearing system B of the present embodiment can induce dynamic pressure in the oil when the rotor 3 rotates, and a pressure peak at which the dynamic pressure is maximum occurs near the turning portion 321 of each dynamic pressure groove 32. In addition, by setting the inner arc section 322 of the dynamic pressure groove 32 of the thrust plate 3a of the rotor 3 to the extending direction opposite to the rotating direction D, the oil located beside the rotating shaft 3b of the rotor 3 can smoothly flow to the turning part 321 of the dynamic pressure groove 32, and the speed of the oil flowing to the outer arc section 323 of the dynamic pressure groove 32 is delayed due to the setting of the turning part 321, so that the oil can stay in the dynamic pressure groove 32 for a long time, the pressure difference of the oil from the inner edge E1 to the outer edge E2 of the thrust plate 3a is reduced, and the effect of increasing the dynamic pressure is achieved.

The simulation analysis software is used to compare the dynamic pressure distribution simulation of the thrust plate 3a of the present embodiment with that of the control thrust plate under the same conditions. The simulation conditions of this time are as follows: the number of the dynamic pressure grooves is 12, the groove depth of each dynamic pressure groove is 17.5 mu m, and the oil film thickness is 10 mu m. The simulation results are: the dynamic pressure of the thrust plate in the comparison group is about 0.1607N, and the dynamic pressure of the thrust plate 3a in the embodiment is about 0.2501N, which is about 55.6% higher.

In addition, referring to fig. 6, the thrust plate 3a of the embodiment may further include a plurality of liquid storage cavities 36, the turning portion 321 of each dynamic pressure groove 32 communicates with one of the liquid storage cavities 36, and the liquid storage cavities 36 may be located in the recess of the boss 33 and extend toward the protrusion of the boss 33, so that only a peak 332 of the protrusion is left on the sidewall 331 of the boss 33, so that a part of the oil flowing from the inner arc section 322 to the turning portion 321 can flow into the liquid storage cavities 36, thereby further slowing down the speed of the oil flowing to the outer arc section 323, and further increasing the dynamic pressure.

Referring to fig. 7 and 8, which are second embodiments of the bearing system B of the present invention, in the dynamic pressure groove 32 of the thrust plate 3a of the present embodiment, the extending direction of the inner arc section 322 from the turning part 321 to the inner edge E1 may be the same as the rotating direction D of the thrust plate 3a, the extending direction of the outer arc section 323 from the turning part 321 to the outer edge E2 may also be the same as the rotating direction D of the thrust plate 3a, and the thrust plate 3a may further have a plurality of liquid storage cavities 36, the turning part 321 of each dynamic pressure groove 32 communicates with one liquid storage cavity 36, and the liquid storage cavity 36 may be located in the recess of the boss 33 and extend to the projection of the boss 33, so that only one sharp point 332 at the projection is left on the sidewall 331 of the boss 33.

Wherein, the thrust plate 3a has an inner ring groove 34 communicating with a plurality of dynamic pressure grooves 32. The radial distance D1 from the sharp point 332 of the boss 33 between any two adjacent dynamic pressure grooves 32 to the inner edge E1 of the body 31 may be greater than or equal to the radial distance D2 from the sharp point 332 to the outer edge E2 of the body 31. The ratio (D2/D4) of the radial distance D2 from the sharp point 332 to the outer edge E2 of the body 31 to the radial distance D4 from the starting point P1 to the outer edge E2 of the body 31 is about 0.2-0.4. Furthermore, a first chord L1 passes through the point 332 and the starting point P1, a second chord L2 passes through the point 332 and the ending point P2, and the included angle α between the first chord L1 and the second chord L2 is about 50-60 degrees.

In addition, as shown in fig. 9, the width of the boss 33 is substantially equal to that of the dynamic pressure groove 32; that is, the boss 33 is equal to the arc lengths U1, U2 (indicated by the thick lines in fig. 8) of the dynamic pressure groove 32 on the same circumference R centered on the hole center C except for the circumference R through which the plurality of sharp points 332 pass (i.e., the circumference R having the plurality of liquid storage cavities 36) (i.e., the included angle θ 1 is equal to the included angle θ 2). Wherein, the ratio (T1/T2) of the linear distance T1 from the end of the liquid storage cavity 36 to the adjacent point 332 to the linear distance T2 between any two adjacent points 332 is about 0.4-0.45.

According to the above structure, the bearing system B of the embodiment can delay the speed of the oil flowing to the outer arc section 323 by providing the liquid storage cavity 36 at the turning part 321 of each dynamic pressure groove 32, so that the oil can stay in the dynamic pressure groove 32 for a long time and achieve the effect of increasing dynamic pressure.

The simulation analysis software is used to compare the dynamic pressure distribution simulation of the thrust plate 3a of the present embodiment with that of the control thrust plate under the same conditions. The simulation conditions of this time are as follows: the number of the dynamic pressure grooves is 12, the groove depth of each dynamic pressure groove is 17.5 mu m, and the oil film thickness is 10 mu m. The simulation results are: the dynamic pressure of the thrust plate in the comparison group is about 0.1607N, and the dynamic pressure of the thrust plate 3a in the embodiment is about 0.1663N, which is improved by about 3.5%.

To sum up, the bearing system and the thrust plate thereof of the present invention can make the extending direction of the inner arc section from the turning part to the inner edge opposite to the rotation direction of the thrust plate, and the extending direction of the outer arc section from the turning part to the outer edge opposite to the rotation direction of the thrust plate; or the extending direction of the inner arc section from the turning part to the inner edge is the same as the rotating direction of the thrust plate, the extending direction of the outer arc section from the turning part to the outer edge is the same as the rotating direction of the thrust plate, and a liquid storage cavity is arranged at the turning part of each dynamic pressure groove, thereby achieving the effect of further improving dynamic pressure by using a simple and easily formed dynamic pressure groove form.

Claims

1. A thrust plate of a bearing system, comprising:

a body having an inner edge and an outer edge; and

a plurality of dynamic pressure grooves which are annularly arranged on the periphery of the inner edge, each dynamic pressure groove is provided with a turning part positioned between an inner arc section and an outer arc section, and the inner arc section is positioned between the turning part and the inner edge;

the extending direction of the inner arc section from the turning part to the inner edge is opposite to the rotating direction of the thrust plate, and the extending direction of the outer arc section from the turning part to the outer edge is opposite to the rotating direction of the thrust plate; or, the extending direction of the inner arc section from the turning part to the inner edge is the same as the rotating direction of the thrust plate, the extending direction of the outer arc section from the turning part to the outer edge is the same as the rotating direction of the thrust plate, and the turning part of each dynamic pressure groove is communicated with one liquid storage cavity.

2. A thrust plate for a bearing system as set forth in claim 1, further comprising an inner annular groove, said inner annular groove and a plurality of dynamic pressure grooves being provided on an end surface of said body, said inner annular groove being adjacent said inner edge, each dynamic pressure groove communicating with said inner annular groove.

3. A thrust plate for a bearing system as set forth in claim 1 wherein said body has a plurality of dynamic pressure grooves on opposite end surfaces.

4. A thrust plate for a bearing system as claimed in claim 1, wherein a land is provided between any two adjacent dynamic pressure grooves, the side wall of the land having a start point adjacent the inner edge of the body and an end point at the outer edge of the body.

5. A thrust plate for a bearing system as claimed in claim 1, wherein a projection is provided between any two adjacent dynamic pressure grooves, the body has a hole center, and the projection and the dynamic pressure groove have the same arc length on the same circumference centered on the hole center.

6. The thrust plate of a bearing system as claimed in claim 1, wherein the number of dynamic pressure grooves is greater than or equal to 10, and a plurality of dynamic pressure grooves are annularly arranged on the outer periphery of the inner edge at equal intervals.

7. The thrust plate of a bearing system as claimed in claim 1, wherein a projection is formed between any two adjacent dynamic pressure grooves, the side wall of the projection has a point corresponding to the turning portion of the dynamic pressure groove, the body has a hole center, and the points of the projections are located on the same circumference centered on the hole center.

8. The thrust plate of claim 7, wherein the extension direction of the inner arc from the turning portion to the inner edge is opposite to the rotation direction of the thrust plate, and the radial distance (D1) from the point to the inner edge of the body is smaller than the radial distance (D2) from the point to the outer edge of the body.

9. The thrust plate of claim 7, wherein the inner arc extends from the inflection portion toward the inner edge in a direction opposite to a rotation direction of the thrust plate, the sidewall of the protrusion has a start point and an end point, and a ratio (D3/D4) of a radial distance (D3) from the start point to a circumference through which the tip point passes to a radial distance (D4) from the start point to the outer edge of the body is 0.1 to 0.3.

10. The thrust plate of claim 7, wherein the inner arc extends from the inflection portion toward the inner edge in a direction opposite to a rotation direction of the thrust plate, the sidewall of the protrusion has a start point and an end point, and a ratio (D4/U) of a radial distance (D4) from the start point to the outer edge of the body to a total length (U) of the sidewall of the protrusion from the start point to the end point is 0.2-0.7.

11. The thrust plate of claim 7, wherein the inner arc extends from the inflection portion to the inner edge in a direction opposite to the rotation direction of the thrust plate, and the inflection portion of each dynamic pressure groove communicates with a reservoir cavity.

12. The thrust plate of claim 7, wherein the extension direction of the inner arc from the turning portion to the inner edge is the same as the rotation direction of the thrust plate, and the radial distance (D1) from the sharp point to the inner edge of the body is greater than or equal to the radial distance (D2) from the sharp point to the outer edge of the body.

13. The thrust plate of claim 7, wherein the extension direction of the inner arc from the turning portion to the inner edge is the same as the rotation direction of the thrust plate, and the ratio (T1/T2) of the linear distance (T1) from the end of the liquid storage cavity to the adjacent peak to the linear distance (T2) between any two adjacent peaks is 0.4-0.45.

14. The thrust plate of claim 7, wherein the inner arc extends from the inflection portion to the inner edge in the same direction as the rotation of the thrust plate, the sidewall of the protrusion has a start point and an end point, and the ratio (D2/D4) of the radial distance (D2) from the tip point to the outer edge of the body to the radial distance (D4) from the start point to the outer edge of the body is 0.2-0.4.

15. The thrust plate of claim 7, wherein the inner arc extends from the turning portion to the inner edge in the same direction as the rotation direction of the thrust plate, the sidewall of the protrusion has a start point and an end point, a first chord passes through the tip point and the start point, a second chord passes through the tip point and the end point, and an included angle between the first chord and the second chord is 50-60 degrees.

16. A bearing system, comprising:

a sleeve;

a bearing located inside the sleeve; and

a rotating member having a thrust plate as claimed in any one of claims 1 to 15 and a rotating shaft, the inner edge of the thrust plate being connected to the rotating shaft, the thrust plate being capable of forming a dynamic pressure gap with the bearing when rotating.

17. The bearing system defined in claim 16 in which the sleeve has a shoulder therein, an inner surface of the bearing abutting the shoulder with the inner surface axially opposed to and spaced from a closed end of the sleeve.

18. The bearing system defined in claim 16 in which the sleeve has a recess therein, the recess being recessed in a closed end of the sleeve, one end of the shaft projecting into the recess and the other end projecting out of the bearing.

19. The bearing system defined in claim 16 in which the shaft has a circumferential groove adjacent the end of the bearing remote from the thrust plate.