CN113124166B

CN113124166B - Sealing structure

Info

Publication number: CN113124166B
Application number: CN202110348595.XA
Authority: CN
Inventors: 请求不公布姓名
Original assignee: Dehaidi Automotive Technology Suzhou Co ltd
Current assignee: Dehaidi Automotive Technology Suzhou Co ltd
Priority date: 2021-03-31
Filing date: 2021-03-31
Publication date: 2023-10-10
Anticipated expiration: 2041-03-31
Also published as: CN113124166A

Abstract

The application discloses a sealing structure, which comprises: a support; the rotary disc can rotate relative to the support, and a flow channel is formed between the rotary disc and the support; the flexible sealing ring is fixedly arranged on the rotary disc, and can deform radially when rotating along with the rotary disc, so that the flow channel is opened and closed. In the application, when the rotating speed of the rotating disc is lower, the flexible sealing ring can close the flow channel, so that the static sealing effect on the flow channel is realized. When the rotating speed of the rotating disc is higher, the flexible sealing ring is separated from the runner under the action of centrifugal force, so that friction loss and component abrasion can be greatly reduced. In addition, the gap in the runner also forms certain pneumatic-hydraulic pressure under the action of centrifugal force to form unidirectional gas-liquid flow from the inside of the runner to the outside of the runner, so that the outside gas is prevented from entering the runner, and the effect of dynamic sealing is realized.

Description

Sealing structure

Technical Field

The application relates to the field of mechanical sealing, in particular to a sealing structure.

Background

The sealing structure is a structure capable of realizing unidirectional separation of gas from the inside of the sealing structure to the outside. The existing sealing structure is usually a mechanical seal, and refers to a structure for preventing fluid leakage, which is formed by at least one pair of end faces perpendicular to a rotation axis and keeping fit and relatively sliding under the action of fluid pressure and elasticity (or magnetic force) of a compensation mechanism and the cooperation of auxiliary seals. However, the rotation of the motor generates great friction loss and part loss, and periodic maintenance is required.

In CN101189414, a sealing structure is mentioned, which relates to a sealing structure between an oil-gas separation cavity and a driving oil cavity, and comprises a rotor with an axial groove and a stator in clearance fit with the rotor, and the sealing effect is difficult to realize in a static state due to the existence of a clearance. When the engine is inclined, the driving oil can submerge the rotating disc, so that the driving oil enters the gas-liquid separation cavity along the gap, and the gas-liquid separation function is disabled.

Disclosure of Invention

In order to overcome the defects in the prior art, the embodiment of the application provides a sealing structure which is used for solving the problems that friction is large during rotation and sealing is difficult in a static state.

The embodiment of the application discloses: a sealing structure, comprising: a support; the rotary disc can rotate relative to the support, and a flow channel is formed between the rotary disc and the support; the flexible sealing ring is fixedly arranged on the rotary disc, and can deform radially when rotating along with the rotary disc, so that the flow channel is opened and closed.

Further, the flexible sealing ring comprises a deformation part sleeved on the edge of the rotary disc.

Further, the flexible seal ring includes an annular seal unit having a gradually decreasing cross-sectional thickness.

Further, the method comprises the steps of: the rotating shaft can rotate around the axial direction of the rotating shaft; the annular outer wall is arranged on the outer side of the rotating shaft in a surrounding mode and extends along the axial direction of the rotating shaft.

Further, the rotary disk comprises a driven part which can synchronously rotate along with the rotating shaft, and the driven part is partially inserted into the rotary disk, so that the rotary disk is driven to synchronously rotate along with the driven part.

Further, the diameter ratio of the annular sealing unit to the annular outer wall is 0.6-0.99.

Further, the rotary shaft comprises a ball bearing, the ball bearing is sleeved on the rotary shaft, and the ball bearing is abutted with one side, close to the rotary shaft, of the annular outer wall.

Further, the thickness of the rotating disc adjacent the shaft portion is greater than the thickness of the rotating disc adjacent the seal ring portion.

Further, the annular outer wall is provided with an inner ring extending towards the center of the rotating shaft, the upper wall of the inner ring is abutted with the ball bearing, a part of flow channel is formed between the lower wall of the inner ring and the rotating disc, and the part of the rotating disc, which is close to the rotating shaft, is abutted with the ball bearing.

Further, the equivalent elastic modulus of the flexible sealing ring material is between 1000MPa and 10000 MPa.

The beneficial effects of the application are as follows:

1. when the rotating speed of the rotating disc is lower, the flexible sealing ring can close the flow channel, when the pressure at the outer side of the flow channel is larger than the pressure at the inner side of the flow channel, the pressure difference enables the bonding force between the flexible sealing ring and the outer wall of the support to be increased, the sealing effect is enhanced, and therefore the static sealing effect on the flow channel is achieved. When the rotating speed of the rotating disc is higher, the flexible sealing ring is separated from the runner under the action of centrifugal force, so that friction loss and component abrasion can be greatly reduced. In addition, the gap in the runner also forms certain pneumatic-hydraulic pressure under the action of centrifugal force to form unidirectional gas-liquid flow from the inside of the runner to the outside of the runner, so that the outside gas is prevented from entering the runner, and the effect of dynamic sealing is realized.

2. The flexible sealing ring can still be partially kept and attached when the flexible sealing ring and the rotary disc are in a high-speed rotation state. So that the flexible sealing ring is not excessively separated from the flow channel when the flexible sealing ring is opened to the flow channel.

3. When liquid passes through different positions of the rotary disc, the rotary disc can have different thicknesses, so that the liquid is guided, and the collecting effect of the liquid is improved.

The foregoing and other objects, features and advantages of the application will be apparent from the following more particular description of preferred embodiments, as illustrated in the accompanying drawings.

Drawings

In order to more clearly illustrate the embodiments of the application or the technical solutions in the prior art, the drawings that are required in the embodiments or the description of the prior art will be briefly described, it being obvious that the drawings in the following description are only some embodiments of the application, and that other drawings may be obtained according to these drawings without inventive effort for a person skilled in the art.

FIG. 1 is a schematic structural view of a seal structure in an embodiment of the present application;

FIG. 2 is a schematic view of an embodiment of the present application in which an annular sealing unit is in interference fit with an annular outer wall in a free state;

FIG. 3 is a schematic view of the structure between the annular sealing unit and the annular outer wall in the actual mounted state in an embodiment of the present application;

FIG. 4 is one embodiment of a seal structure in an embodiment of the application;

FIG. 5 is another embodiment of a seal structure in an embodiment of the application;

reference numerals of the above drawings: 1. a support; 2. rotating the disc; 3. a flow passage; 4. a flexible sealing ring; 41. a deformation section; 42. an annular sealing unit; 5. a rotating shaft; 6. an annular outer wall; 61. an inner ring; 7. a driven part; 8. ball bearings.

Detailed Description

The following description of the embodiments of the present application will be made clearly and completely with reference to the accompanying drawings, in which it is apparent that the embodiments described are only some embodiments of the present application, but not all embodiments. All other embodiments, which can be made by those skilled in the art based on the embodiments of the application without making any inventive effort, are intended to be within the scope of the application.

As shown in fig. 1 to 5, the seal structure of the present embodiment includes:

the support 1, the support 1 may include an annular plate parallel to the rotatable disk 2, and an edge of the annular plate may abut against a housing provided outside the sealing structure, and the housing may be substantially cylindrical in interior, so that the support 1 can partition the cylindrical space inside the housing. The support 1 may be kept stationary during rotation of the rotatable disc 2 such that a relative rotation between the support 1 and the rotatable disc 2 may occur. The support 1 may be provided with an opening therethrough for forming the flow channel 3.

The rotating disc 2 is rotatable relative to the support 1 such that liquid is forced out of the sealing structure via the flow channel 3 by centrifugal forces generated during rotation. A flow channel 3 may be formed between the rotatable disc 2 and the support 1 for passing the liquid. The edge of the rotary disk 2 may extend into the flexible sealing ring 4, thereby increasing the friction between the flexible sealing ring 4 and the rotary disk 2, and making the flexible sealing ring 4 more firmly bonded to the rotary disk 2.

The flexible sealing ring 4, the flexible sealing ring 4 can be fixedly arranged on the rotary disc 2, so that the flexible sealing ring 4 can rotate synchronously with the rotary disc 2. The flexible seal ring 4 is radially deformed when rotated with the rotary disk 2, and opens and closes the flow passage 3.

In an alternative embodiment, as shown in fig. 4, the flexible sealing ring 4 is sleeved on the edge of the rotating disc, and when the rotating speed of the rotating disc 2 is low, the flexible sealing ring 4 can seal the flow channel 3 positioned between the rotating disc 2 and the support 1. When the rotation speed of the rotary disk 2 increases, the part of the flexible sealing ring 4 positioned between the rotary disk 2 and the support 1 deforms along the radial direction of the rotary disk 2 under the action of centrifugal force, so that the flow channel 3 is opened, and the effect of opening and closing the flow channel 3 can be realized by controlling the rotation speed of the rotary disk 2.

In an alternative embodiment, as shown in fig. 5, a flexible sealing ring 4 is fitted over the intermediate region of the support 1 and the rotatable disc 2. When the rotation speed of the rotary disk 2 is low, the flexible sealing ring 4 can seal the flow channel 3 positioned between the rotary disk 2 and the support 1. When the rotation speed of the rotary disk 2 is gradually increased, the flexible sealing ring 4 deforms along the radial direction of the rotary disk 2 under the action of centrifugal force, so that the flow channel 3 is opened, and the effect of opening and closing the flow channel 3 can be realized by controlling the rotation speed of the rotary disk 2.

By means of the structure, when the rotating speed of the rotating disc 2 is low, the flexible sealing ring 4 can close the runner 3, when the pressure on the outer side of the runner 3 is greater than the pressure on the inner side of the runner 3, the pressure difference enables the bonding force between the flexible sealing ring 4 and the outer wall of the support 1 to be increased, the sealing effect is enhanced, and therefore the static sealing effect on the runner 3 is achieved. When the rotating speed of the rotating disc 2 is higher, the flexible sealing ring 4 is separated from the flow channel 3 under the action of centrifugal force, so that friction loss and component abrasion can be greatly reduced. In addition, the gap in the runner 3 also forms certain pneumatic-hydraulic pressure under the action of centrifugal force, and forms unidirectional gas-liquid flow from the inside of the runner 3 to the outside of the runner 3, so that outside gas is prevented from entering the runner, and the effect of dynamic sealing is realized.

Specifically, as shown in fig. 2 and 3, the flexible seal ring 4 may include a deformation portion 41 that is sleeved on the edge of the rotary disk 2. The edge of the rotatable disc 2 may have a protrusion protruding towards the support 1 so that the flexible sealing ring 4 is wider at its root after being fitted over the protrusion, providing a constraint during high speed rotation so that there is no excessive separation between the flexible sealing ring 4 and the rotatable disc 2. The flexible sealing ring 4 can still be partially kept fit when the flexible sealing ring 4 and the rotary disc 2 rotate at a high speed. So that the flexible sealing ring 4 is not excessively separated from the flow channel 3 when the flexible sealing ring 4 is opened to the flow channel 3. Therefore, the liquid in the flow channel 3 can also form certain pneumatic-hydraulic pressure under the action of centrifugal force, so that a unidirectional gas-liquid flow from the inside of the flow channel 3 to the outside of the flow channel 3 is formed, and outside gas can be prevented from entering the flow channel 3 in the process of liquid circulation.

Specifically, as shown in fig. 2 and 3, the flexible seal ring 4 includes an annular seal unit 42 having a gradually decreasing cross-sectional thickness. The annular sealing unit 42 may be in contact with the flow path 3 when the rotary disk 2 is in a stationary state, thereby achieving a sealing effect for the flow path 3. When the pressure on the outer side of the flow channel 3 is greater than the pressure on the inner side of the flow channel 3, the pressure difference increases the bonding force between the annular sealing unit 42 and the flow channel 3, and the sealing effect is enhanced; when the rotation speed of the rotary disk 2 is gradually increased, the annular sealing unit 42 is separated from the flow channel 3 by centrifugal force, so that friction loss between the annular sealing unit 42 and the flow channel 3 and abrasion between parts can be greatly reduced. The annular sealing unit 42 may include a sealing piece extending along its center, thereby making the annular sealing unit 42 easier to seal when in contact with the flow channel 3. Of course, in other alternative embodiments, the shape of the annular sealing unit 42 may be adjusted according to actual needs.

Specifically, as shown in fig. 1 to 3, the device includes a rotating shaft 5 and an annular outer wall 6, the rotating shaft 5 can rotate around the axial direction of the rotating shaft, the rotating shaft 5 can extend in the vertical direction, and of course, in other alternative embodiments, the extending direction of the rotating shaft 5 can be adjusted according to actual needs. The rotary disc 2 can be sleeved on the rotating shaft 5 and can rotate along with the rotating shaft 5, so that the rotary disc 2 can rotate along with the rotating shaft 5 at different rotation speeds. The annular outer wall 6 may be disposed around the outer side of the rotating shaft 5 and axially extend along the rotating shaft 5. The annular outer wall 6 may abut against the annular sealing unit 42, thereby controlling the flow of liquid in the flow channel 3 by contact and separation between the annular sealing unit 42 and the annular outer wall 6.

In an alternative embodiment, as shown in fig. 1 to 3, the annular outer wall 6 is integrally formed with the support 1 such that a portion of the flow channel 3 is located between the annular outer wall 6 and the disc. In an alternative embodiment (not shown), the annular outer wall 6 is integrally formed with the sealing disc such that part of the flow channel 3 is located between the annular outer wall 6 and the support 1.

Specifically, as shown in fig. 1 to 3, the rotary disk device comprises a driven part 7 capable of synchronously rotating along with the rotating shaft 5, and the driven part 7 can be partially inserted into the rotary disk 2, so that the rotary disk 2 can be driven to synchronously rotate along with the driven part 7. The cross-sectional shape of the driven portion 7 may be the same as that of the rotary disk 2, thereby improving the adaptability between the driven portion 7 and the rotary disk 2. Of course, in other alternative embodiments, the shape of the driven portion 7 may be adjusted according to actual needs.

Specifically, the diameter ratio of the annular sealing unit 42 to the annular outer wall 6 is 0.6-0.99, that is, the diameter of the annular sealing unit 42 is smaller than that of the annular outer wall 6 to a certain extent, and the annular sealing unit 42 is a flexible sealing ring 4, and the flexible sealing ring 4 is made of a flexible material, so that when the rotating disc 2 does not have a rotating speed or has a small rotating speed, the annular sealing unit 42 is tightly attached to the annular outer wall 6, and the sealing effect on the flow channel 3 is enhanced.

Specifically, as shown in fig. 1 to 3, the ball bearing 8 is included, and the ball bearing 8 may be sleeved on the rotating shaft 5. The ball bearing 8 may abut against the side of the annular outer wall 6 adjacent the shaft 5 so that liquid located above the support 1 can pass through the ball bearing 8. That is, in the present embodiment, the space in the middle of the ball bearing 8 is a part of the flow path 3.

Specifically, as shown in fig. 2 and 3, the thickness of the portion of the rotary disk 2 adjacent to the rotary shaft 5 may be greater than the thickness of the portion adjacent to the seal ring, the annular outer wall 6 may have an inner ring 61 extending toward the center of the rotary shaft 5, and an upper wall of the inner ring 61 may abut against the ball bearing 8. Part of the flow path 3 may be formed between the lower wall of the inner ring 61 and the rotating disc 2. The part of the rotary disc 2 adjacent to the rotating shaft 5 is abutted against the ball bearing 8, so that when liquid passes through different positions of the rotary disc 2, the rotary disc 2 has a diversion effect on the liquid due to different thicknesses, and the collection effect on the liquid is improved.

Specifically, the equivalent elastic modulus of the flexible sealing ring 4 material is between 1000MPa and 10000 MPa. Thereby ensuring that the flexible sealing ring 4 can form a sealing gap of 0.05-0.5 mm with the flow channel 3 at the rotating speed of 1000-10000 rpm.

The principles and embodiments of the present application have been described in detail with reference to specific examples, which are provided to facilitate understanding of the method and core ideas of the present application; meanwhile, as those skilled in the art will have variations in the specific embodiments and application scope in accordance with the ideas of the present application, the present description should not be construed as limiting the present application in view of the above.

Claims

1. A sealing structure, characterized by comprising:

a support;

a rotatable disk rotatable relative to the support, a flow path being formed between the rotatable disk and the support;

the flexible sealing ring is fixedly arranged on the rotary disc and can deform radially when rotating along with the rotary disc, so that the flow channel is opened and closed;

the flexible sealing ring comprises a deformation part sleeved on the edge of the rotary disc, the flexible sealing ring comprises an annular sealing unit with gradually reduced section thickness, the edge of the rotary disc is provided with a protruding part protruding towards the support, and the root part of the flexible sealing ring is sleeved on the protruding part;

when the rotating speed of the rotating disc is lower, the flexible sealing ring can close the flow channel, and when the pressure at the outer side of the flow channel is higher than the pressure at the inner side of the flow channel, the pressure difference enables the bonding force between the flexible sealing ring and the outer wall of the support to be increased, and the sealing effect is enhanced, so that the static sealing effect on the flow channel is realized; when the rotating speed of the rotating disc is higher, the flexible sealing ring is separated from the flow channel under the action of centrifugal force, so that friction loss and component abrasion are reduced, a certain pneumatic-hydraulic pressure is formed in a gap in the flow channel under the action of the centrifugal force, unidirectional gas-liquid flow from the inside of the flow channel to the outside of the flow channel is formed, and outside gas is prevented from entering the flow channel, so that dynamic sealing is realized.

2. The seal structure according to claim 1, comprising:

the rotating shaft can rotate around the axial direction of the rotating shaft;

the annular outer wall is arranged on the outer side of the rotating shaft in a surrounding mode and extends along the axial direction of the rotating shaft.

3. The seal of claim 2 including a driven portion synchronously rotatable with said shaft, said driven portion being partially inserted into said rotatable disk to thereby drive said rotatable disk to synchronously rotate with said driven portion.

4. The seal arrangement according to claim 2, wherein the diameter ratio of the annular sealing unit to the annular outer wall is 0.6-0.99.

5. The seal of claim 2, including a ball bearing, said ball bearing being disposed about said shaft and abutting a side of said annular outer wall adjacent said shaft.

6. The seal of claim 5, wherein the thickness of the rotatable disk adjacent the shaft portion is greater than the thickness of the flexible seal ring portion.

7. The seal of claim 6 wherein said annular outer wall has an inner annular ring extending toward the center of said shaft, an upper wall of said inner annular ring abutting said ball bearing, a portion of said flow path being defined between a lower wall of said inner annular ring and said rotatable disk, a portion of said rotatable disk adjacent said shaft abutting said ball bearing.

8. The seal structure of claim 1, wherein the flexible seal ring material has an equivalent elastic modulus between 1000MPa and 10000 MPa.