CN113124166A

CN113124166A - Sealing structure

Info

Publication number: CN113124166A
Application number: CN202110348595.XA
Authority: CN
Inventors: 不公告发明人
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: 2021-07-16
Anticipated expiration: 2041-03-31
Also published as: CN113124166B

Abstract

The invention discloses a sealing structure, comprising: a support; the rotating disc can rotate relative to the support, and a flow channel is formed between the rotating disc and the support; the flexible sealing ring is fixedly arranged on the rotating disc and can deform along the radial direction when rotating along with the rotating disc, so that the flow channel is opened and closed. In the invention, when the rotating speed of the rotating disk is lower, the flexible sealing ring can close the flow channel, thereby realizing the static sealing effect on the flow channel. When the rotating speed of the rotating disk is high, the flexible sealing ring is separated from the flow channel under the action of centrifugal force, so that friction loss and component abrasion can be greatly reduced. In addition, certain gas-liquid dynamic pressure is formed in gaps in the flow channel under the action of 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 the effect of dynamic sealing is achieved.

Description

Sealing structure

Technical Field

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

Background

The sealing structure is a structure capable of realizing unidirectional gas separation from the inside of the sealing structure to the outside. The existing sealing structure, which is usually a mechanical seal, 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 the end faces are kept in fit and relatively slide under the action of fluid pressure and the elastic force (or magnetic force) of a compensation mechanism and the cooperation of an auxiliary seal. However, they generate large friction loss and part loss during rotation, and require regular maintenance.

CN101189414 mentions a sealing structure, which relates to a sealing structure between an oil-gas separation chamber and a driving oil chamber, and includes a rotor with an axial groove and a stator in clearance fit with the axial groove, and it is difficult to achieve a sealing effect in a static state due to the existence of a clearance. When the engine is inclined, the drive oil may submerge the rotating disk, so that the drive oil enters the gas-liquid separation cavity along the gap, and the gas-liquid separation function fails.

Disclosure of Invention

In order to overcome the defects in the prior art, embodiments of the present invention provide a sealing structure, which is used to solve the above-mentioned problems of large friction during rotation and difficulty in sealing in a static state.

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

Further, the flexible sealing ring comprises an annular sealing unit with a gradually reduced cross-sectional thickness.

Further, comprising: the rotating shaft can rotate around the axial direction of the rotating shaft; the annular outer wall encloses and establishes in the pivot outside and extends along the pivot axial.

And the driven part can synchronously rotate along with the rotating shaft and is partially inserted into the rotating disk so as to drive the rotating disk 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, including ball bearing, ball bearing sleeve locates the pivot, and ball bearing and annular outer wall close to one side butt of pivot.

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

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

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

The invention has the following beneficial effects:

1. when the rotating speed of the rotating disk is low, the flexible sealing ring can close the runner, and when the pressure outside the runner is greater than the pressure inside the runner, the pressure difference enables the joint force of the flexible sealing ring and the outer wall of the support to be increased, the sealing effect is enhanced accordingly, and the static sealing effect on the runner is achieved. When the rotating speed of the rotating disk is high, the flexible sealing ring is separated from the flow channel under the action of centrifugal force, so that friction loss and component abrasion can be greatly reduced. In addition, certain gas-liquid dynamic pressure is formed in gaps in the flow channel under the action of 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 the effect of dynamic sealing is achieved.

2. The flexible sealing ring can still be partially kept attached to the rotating disk in a high-speed rotating state. When the flexible sealing ring is used for opening the flow channel, the flexible sealing ring is not excessively separated from the flow channel.

3. When liquid passes through different positions of the rotating disc, the rotating disc can play a role in guiding liquid due to different thicknesses, and the collecting effect on the liquid is improved.

In order to make the aforementioned and other objects, features and advantages of the invention comprehensible, preferred embodiments accompanied with figures are described in detail below.

Drawings

In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the drawings without creative efforts.

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

FIG. 2 is a schematic structural diagram of an annular sealing unit in interference fit with an annular outer wall in a free state according to an embodiment of the invention;

FIG. 3 is a schematic structural view of an annular sealing unit in an actual installation state and an annular outer wall in the embodiment of the invention;

FIG. 4 is one embodiment of a seal configuration in an embodiment of the present invention;

FIG. 5 is another embodiment of a seal configuration in an embodiment of the present invention;

reference numerals of the above figures: 1. a support; 2. rotating the disk; 3. a flow channel; 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 circular ring; 7. a driven part; 8. ball bearings.

Detailed Description

The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.

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

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

The rotatable disk 2, the rotatable disk 2 being rotatable relative to the carrier 1, so that the liquid is discharged from the sealing arrangement via the flow channel 3 by means of the centrifugal force generated during rotation. Between the rotating disc 2 and the support 1 a flow channel 3 may be formed for the passage of liquid. The edge of the rotating disk 2 may extend into the flexible sealing ring 4, so as to increase the friction between the flexible sealing ring 4 and the rotating disk 2, so that the flexible sealing ring 4 is combined with the rotating disk 2 more firmly.

The flexible sealing ring 4, the flexible sealing ring 4 can be fixedly arranged on the rotating disk 2, thereby making the flexible sealing ring 4 rotate synchronously with the rotating disk 2. The flexible sealing ring 4 can deform along the radial direction when rotating along with the rotating disk 2, thereby opening and closing the flow channel 3.

In an alternative embodiment, as shown in fig. 4, the flexible sealing ring 4 is sleeved on the edge of the rotating disk, and when the rotating disk 2 rotates at a low speed, the flexible sealing ring 4 can seal the flow channel 3 between the rotating disk 2 and the support 1. When the rotating speed of the rotating disk 2 is increased, the part of the flexible sealing ring 4 positioned between the rotating disk 2 and the support 1 deforms along the radial direction of the rotating 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 rotating speed of the rotating disk 2.

In an alternative embodiment, as shown in fig. 5, the flexible sealing ring 4 is fitted over the intermediate region of the support 1 and the rotatable disk 2. When the rotating disk 2 rotates at a low speed, the flexible sealing ring 4 can seal the flow channel 3 between the rotating disk 2 and the support 1. When the rotating speed of the rotating disk 2 is gradually increased, the flexible sealing ring 4 deforms along the radial direction of the rotating 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 rotating speed of the rotating 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 outside the runner 3 is greater than the pressure inside the runner 3, the pressure difference enables the attaching force of the flexible sealing ring 4 and the outer wall of the support 1 to be increased, the sealing effect is enhanced accordingly, and therefore the static sealing effect on the runner 3 is achieved. When the rotating speed of the rotating disk 2 is high, the flexible sealing ring 4 is separated from the flow channel 3 under the action of centrifugal force, so that the friction loss and the part abrasion can be greatly reduced. In addition, a certain gas-liquid dynamic pressure is formed in the gap in the flow channel 3 under the action of centrifugal force, 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 is prevented from entering the flow channel, so that the effect of dynamic sealing is realized.

Specifically, as shown in fig. 2 and 3, the flexible sealing ring 4 may include a deformation portion 41 that is sleeved on the edge of the rotatable disk 2. The edge of the rotating disk 2 may have a protrusion protruding toward the support 1, so that the root of the flexible sealing ring 4 is wider after being sleeved on the protrusion, and the flexible sealing ring 4 can provide a constraint during high-speed rotation, so that the flexible sealing ring 4 and the rotating disk 2 are not excessively separated. The flexible sealing ring 4 can be partially kept attached to the rotating disk 2 in a high-speed rotating state between the flexible sealing ring 4 and the rotating disk 2. So that the flexible sealing ring 4 is not excessively separated from the flow passage 3 when the flexible sealing ring 4 is opening the flow passage 3. Therefore, the liquid in the flow channel 3 can form certain gas-liquid dynamic 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 the gas on the outer side can be prevented from entering the flow channel 3 in the liquid flowing process.

In particular, as shown in fig. 2 and 3, the flexible sealing ring 4 comprises an annular sealing unit 42 with a gradually decreasing cross-sectional thickness. The annular sealing unit 42 may contact the flow channel 3 when the rotating disk 2 is in a stationary state, thereby achieving an effect of sealing the flow channel 3. When the pressure at the outer side of the flow channel 3 is larger than the pressure at the inner side of the flow channel, the pressure difference increases the joint force between the annular sealing unit 42 and the flow channel 3, and the sealing effect is enhanced accordingly; when the rotation speed of the rotating disk 2 is gradually increased, the annular sealing unit 42 is separated from the flow passage 3 by the centrifugal force, so that the friction loss between the annular sealing unit 42 and the flow passage 3 and the abrasion between the parts can be greatly reduced. The annular sealing unit 42 may comprise a sealing disc extending along its centre, so that the annular sealing unit 42 is more easily sealed 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 rotating shaft 5 and the annular outer wall 6 are included, the rotating shaft 5 can rotate around the axial direction thereof, 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 rotating disk 2 can be sleeved on the rotating shaft 5 and can rotate along with the rotating shaft 5, so that the rotating disk 2 can rotate along with the rotating shaft 5 at different rotating speeds. The annular outer wall 6 may be enclosed outside the rotating shaft 5 and extend axially along the rotating shaft 5. The annular outer wall 6 may abut the annular sealing unit 42, thereby controlling the flow of the liquid in the flow passage 3 by the contact and the 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 formed integrally with the carrier 1 such that part of the flow channel 3 is located between the annular outer wall 6 and the disc. In another alternative embodiment (not shown in the figures) the annular outer wall 6 is formed integrally with the sealing disc such that part of the flow channel 3 is located between the annular outer wall 6 and the carrier 1.

Specifically, as shown in fig. 1 to fig. 3, the disc rotating apparatus includes a driven part 7 capable of synchronously rotating with the rotating shaft 5, and the driven part 7 may be partially inserted into the rotating disc 2, so as to drive the rotating disc 2 to synchronously rotate with the driven part 7. The sectional shape of the driven portion 7 may be the same as that of the rotating disk 2, thereby improving the fit between the driven portion 7 and the rotating disk 2. Of course, in other alternative embodiments, the shape of the driven part 7 can 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, because the annular sealing unit 42 belongs to the flexible sealing ring 4, and the flexible sealing ring 4 is made of flexible material, the annular sealing unit 42 is tightly attached to the annular outer wall 6 when the rotating disk 2 does not have a rotating speed or has a smaller rotating speed, and thus the sealing effect on the flow channel 3 is enhanced.

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

Specifically, as shown in fig. 2 and 3, the thickness of the portion of the rotatable disk 2 adjacent to the rotary shaft 5 may be larger than the thickness of the portion adjacent to the seal ring, the annular outer wall 6 may have an inner annular ring 61 extending toward the center of the rotary shaft 5, and the upper wall of the inner annular ring 61 may abut against the ball bearing 8. Part of the flow channel 3 may be formed between the lower wall of the inner ring 61 and the rotating disk 2. The part of the rotating disk 2 close to the rotating shaft 5 is abutted to the ball bearing 8, so that when liquid passes through different positions of the rotating disk 2, the rotating disk 2 is different in thickness, and therefore the liquid is guided, and the liquid collecting effect is improved.

Specifically, the equivalent elastic modulus of the material of the flexible sealing ring 4 is between 1000MPa and 10000 MPa. Thereby guarantee that flexible sealing washer 4 can form 0.05 ~ 0.5 mm's seal clearance with runner 3 under 1000 ~ 10000 rpm's rotational speed.

The principle and the implementation mode of the invention are explained by applying specific embodiments in the invention, and the description of the embodiments is only used for helping to understand the method and the core idea of the invention; meanwhile, for a person skilled in the art, according to the idea of the present invention, there may be variations in the specific embodiments and the application scope, and in summary, the content of the present specification should not be construed as a limitation to the present invention.

Claims

1. A sealing structure, comprising:

a support;

the rotating disk can rotate relative to the support, and a flow channel is formed between the rotating disk and the support;

the flexible sealing ring is fixedly arranged on the rotating disc and can deform along the radial direction when rotating along with the rotating disc, so that the flow channel is opened and closed.

2. The seal structure of claim 1, wherein the flexible seal ring includes a deformation around an edge of the rotatable disk.

3. The sealing structure of claim 1, wherein the flexible sealing ring comprises an annular sealing unit having a gradually decreasing cross-sectional thickness.

4. The seal structure of claim 1, comprising:

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

the annular outer wall encloses to be established the pivot outside just follows pivot axial extension.

5. The seal structure of claim 4, including a driven portion synchronously rotatable with the shaft, the driven portion being partially inserted into the rotating disc to thereby drive the rotating disc synchronously rotatable with the driven portion.

6. The sealing structure of claims 3 and 4, wherein the annular sealing unit has a diameter ratio to the annular outer wall of 0.6-0.99.

7. The seal structure of claim 4, comprising a ball bearing, wherein the ball bearing is sleeved on the rotating shaft and abuts against a side of the annular outer wall adjacent to the rotating shaft.

8. The seal structure of claim 7, wherein a thickness of the rotatable disk adjacent the shaft portion is greater than a thickness adjacent the compliant seal ring portion.

9. The seal structure according to claim 8, wherein said annular outer wall has an inner annular ring extending toward a center of said rotary shaft, an upper wall of said inner annular ring abutting said ball bearing, a part of said flow passage being formed between a lower wall of said inner annular ring and said rotary disk, and a part of said rotary disk adjacent to said rotary shaft abutting said ball bearing.

10. The sealing structure of claim 1, wherein the flexible sealing ring material has an equivalent modulus of elasticity between 1000MPa and 10000 MPa.