CN112594395A - Double-rotation direction dynamic pressure synergistic sealing ring - Google Patents
Double-rotation direction dynamic pressure synergistic sealing ring Download PDFInfo
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- CN112594395A CN112594395A CN202011602588.XA CN202011602588A CN112594395A CN 112594395 A CN112594395 A CN 112594395A CN 202011602588 A CN202011602588 A CN 202011602588A CN 112594395 A CN112594395 A CN 112594395A
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- Prior art keywords
- rotation
- double
- groove
- ring
- dynamic pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
- F16J15/3404—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal
- F16J15/3408—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal at least one ring having an uneven slipping surface
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
- F16J15/3404—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal
- F16J15/3408—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal at least one ring having an uneven slipping surface
- F16J15/3412—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal at least one ring having an uneven slipping surface with cavities
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
- F16J15/3496—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member use of special materials
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/40—Sealings between relatively-moving surfaces by means of fluid
Abstract
The invention provides a double-rotation dynamic pressure synergistic sealing ring, which comprises: the novel sealing moving ring structure comprises a double-rotation-direction sealing moving ring, wherein a plurality of T-shaped grooves are uniformly distributed at the groove face end of the double-rotation-direction sealing moving ring along the circumferential direction, a pair of pressurizing holes are formed in the groove bottom surface, located in the double-rotation-direction sealing moving ring, of an arc groove, the pressurizing holes are step holes which penetrate through the double-rotation-direction sealing moving ring in the axial direction, a one-way duckbill valve is arranged in a large-diameter hole of each pressurizing hole, and the distribution condition and the opening force of the end face air film pressure of the novel sealing moving ring structure and the original structure are calculated and compared through CFD. The result shows that the opening force of the end surface of the novel double-rotation dynamic pressure synergistic sealing ring is increased by 2-4.6% compared with the original design. Particularly, when the rotating speed is lower than 5000 r/min, the dynamic pressure synergistic effect is obvious, and the double-rotation-direction dry gas seal with the structural design has excellent low-speed opening performance. The problem of dry friction of the dry gas sealing end face under the conditions of lower sealing gas pressure and lower rotating speed can be effectively solved.
Description
Technical Field
The invention belongs to the technical field of dry gas sealing, and particularly relates to a double-rotation-direction dynamic pressure synergistic sealing ring.
Background
Dry gas seals are commonly used to address shaft end sealing issues for high speed rotating machines such as centrifugal compressors. It belongs to non-contact gas lubrication mechanical seal, and is generally composed of a shaft sleeve, a movable ring, a static ring, a spring, an auxiliary sealing ring and other structural components. The most difference between the two types of mechanical seal is that hydrodynamic grooves with the depth of several microns are machined on the end face of a moving ring of the mechanical seal. When the movable ring and the static ring rotate relatively, the microgrooves on the end face shear gas, and local high pressure is formed at the root of the groove, so that a layer of gas film with high rigidity is formed between the whole movable ring and the whole static ring, and the whole friction pair shows a separation trend outwards. The medium pressure acts on the back of the static ring and the dynamic ring, and forms total closing force together with the spring force to make the friction pair show a closing trend. The closing force and the opening force of the dry gas seal are equal in the stable operation process.
The dynamic pressure groove design of the dry gas seal is one of the most important links in the whole seal design work, and is directly related to the success or failure of the seal use. It has been found through long-term research that a hydrodynamic groove profile using a logarithmic spiral or an archimedean spiral has an optimum hydrodynamic effect. Dry gas seal manufacturers, as represented by John Crane corporation, have primarily employed a single handed spiral groove shape. It has the advantages of high air film rigidity and strong anti-interference capability. However, since the single-direction dynamic pressure groove is limited by geometrical characteristics, in a specific application environment, the method has a fatal defect. If the compressor rotates reversely, the sealing end face with the single-rotation groove shape is contacted and rubbed for a relatively long time because the opening force cannot be generated, and the sealing end face is very easy to damage.
In addition, the dry gas seals are positioned at two ends of the compressor cylinder body, and the rotating directions of the two end seals are just opposite when the main shaft penetrates out of the cylinder body as the normal direction. If single-rotation-direction dry gas sealing is adopted, two sets of two rotation-direction products are required to be equipped for dry gas sealing products in the same batch, one set is operated for use, and the other set is reserved. Taking a single-cylinder compressor as an example, the single-cylinder compressor is provided with two sets of dry gas seals in clockwise rotation and anticlockwise rotation respectively. If the double-rotation-direction dry gas seal which is not influenced by the rotation direction is adopted, the seals at the driving end and the non-driving end of the compressor can be exchanged, and the number of spare parts is reduced. Therefore, the double-rotation direction dry gas sealing industrial application field is wide and cannot be replaced. The method has great significance for carrying out deep research on the double-rotation-direction dry gas sealing fluid dynamic pressure groove type.
The double-handed hydrodynamic grooves have one common feature: if the slot platform area is divided equally according to the number of the slots along the circumferential direction, the slots of the slot platform area are symmetrically distributed along a central radial straight line in a certain period division area. When the seal is in normal operation, one half of the grooves generate positive pressure to open the end faces, and the other half of the grooves generate negative pressure to enable the end faces to be attached. The CFD calculation found that the hydrodynamic opening force at this time was almost 0.
Disclosure of Invention
In view of the above-mentioned problems of the prior art, an object of the present invention is to provide a double-rotation dynamic pressure synergistic seal ring.
In order to achieve the purpose, the technical scheme of the invention is as follows:
a dual-rotation dynamic pressure enhanced seal ring comprising: the double-rotation-direction sealing movable ring 1 is characterized in that a plurality of T-shaped grooves 2 are uniformly distributed at the groove surface end 5 of the double-rotation-direction sealing movable ring 1 along the circumferential direction, the T-shaped grooves 2 do not penetrate through the double-rotation-direction sealing movable ring 1 in the axial direction, each T-shaped groove 2 comprises a linear groove 21 extending from the outer diameter to the inner diameter of the groove surface end 5 and an arc groove 22 connected with the tail end of the linear groove 21, the width of the arc groove 22 is larger than that of the linear groove 21, the surface of the double-rotation-direction sealing movable ring 1 without the T-shaped groove is a back surface end 6, a pair of pressurizing holes 3 are arranged on the bottom surface of the circular arc groove 22 positioned inside the double-rotation-direction sealing moving ring 1, the pressurizing holes 3 are stepped holes which axially penetrate through the double-rotation-direction sealing moving ring 1 and comprise a small-diameter hole 31 close to the groove surface end 5 and a large-diameter hole 32 close to the back surface end 6, a one-way duck bill valve 4 is arranged in the large-diameter hole 32 of each pressurizing hole 3, and a duck bill end 42 of the duck bill valve 4 extends into the small-diameter hole 31.
Preferably, each pair of pressurizing holes 3 is arranged on the groove bottom surface of the circular arc groove 22 where the pressurizing holes are arranged in a left-right symmetrical mode about the center line of the circular arc groove.
Preferably, 6-20T-shaped grooves are uniformly distributed at the groove surface end 5 of the double-rotation-direction sealing moving ring 1 along the circumferential direction.
Preferably, 3-6T-shaped grooves distributed at equal intervals in the circumferential direction of the double-rotation-direction sealing moving ring 1 are provided with the pressurizing holes 3. The reason for this is to make the pressure distribution of the pressurizing holes more balanced and uniform over the entire seal moving ring 1 and to make the total dynamic pressure formed by the entire groove group positive.
Preferably, when the number of the T-shaped grooves is an odd number, the number of pairs of the pressurizing holes 3 is an odd number of 3 or more; when the number of the T-shaped grooves is even, the number of pairs of the pressurizing holes 3 is even more than 4.
Preferably, the depth of the T-shaped groove in the groove surface end 5 of the double-screwing-direction sealing moving ring 1 is 8-10 microns.
As a preferred mode, the one-way duckbill valve is used for controlling the on-off of the air flow of the groove surface end and the back surface end of the double-rotation-direction sealing moving ring 1, and when the pressure of the back surface end of the double-rotation-direction sealing moving ring is higher than the pressure of the groove surface end and is greater than the opening pressure of the duckbill valve, medium gas flows to the moving ring groove surface end from the back surface end of the double-rotation-direction sealing moving ring; when the pressure of the groove surface end of the double-rotation-direction sealing moving ring is higher than the pressure of the back surface end and is higher than the closing pressure of the duckbill valve, the duckbill valve is closed, and the air flow is cut off.
Preferably, the one-way duckbill valve 4 includes a rubber seat 41 and a duckbill 42, the duckbill 42 being secured to the rubber seat 41.
Preferably, the double-rotary-direction sealing moving ring 1 is made of SiC material.
Preferably, the small diameter hole 31 of the pressurizing hole 3 has a diameter of 0.2 to 0.6mm, and the large diameter hole has a diameter of 3 to 6 mm.
The invention has the beneficial effects that: the invention provides a novel double-rotation-direction dynamic pressure synergistic sealing ring. Through CFD simulation, the pressure distribution condition and the opening force of the end face air film of the novel sealing moving ring structure and the original structure are calculated and compared. The result shows that the opening force of the end surface of the novel double-rotation dynamic pressure synergistic sealing ring is increased by 2-4.6% compared with the original design. Particularly, when the rotating speed is lower than 5000 r/min, the dynamic pressure synergistic effect is obvious, and the double-rotation-direction dry gas seal with the structural design has excellent low-speed opening performance. The problem of dry friction of the dry gas sealing end face under the conditions of lower sealing gas pressure and lower rotating speed can be effectively solved.
Drawings
FIG. 1 is a schematic view of the overall structure of the double-rotation dynamic pressure synergistic sealing ring of the present invention;
FIG. 2 is a cross-sectional view taken along line E-E of FIG. 1;
fig. 3 is a partially enlarged view of fig. 2.
Figure 4 is a schematic perspective view of the installation of the one-way duckbill valve in the double-rotation dynamic pressure synergistic sealing ring.
Figure 5 is a schematic view of the one-way duckbill valve of the present invention.
1 is sealed rotating ring of bispin to, 2 is T type groove, 21 is the straight line groove, 22 is the circular arc groove, 3 is the pressure boost hole, and 31 is the minor diameter hole, and 32 is the major diameter hole, and 4 are one-way duckbill valves, and 41 are the rubber seat, and 42 are the duckbilled end, and 5 are the groove face end, and 6 are the back face end.
Detailed Description
The embodiments of the present invention are described below with reference to specific embodiments, and other advantages and effects of the present invention will be easily understood by those skilled in the art from the disclosure of the present specification. The invention is capable of other and different embodiments and of being practiced or of being carried out in various ways, and its several details are capable of modification in various respects, all without departing from the spirit and scope of the present invention.
The embodiment provides a double-rotation dynamic pressure synergistic sealing ring, including: the double-rotation-direction sealing movable ring 1 is characterized in that a plurality of T-shaped grooves 2 are uniformly distributed at the groove surface end 5 of the double-rotation-direction sealing movable ring 1 along the circumferential direction, the T-shaped grooves 2 do not penetrate through the double-rotation-direction sealing movable ring 1 in the axial direction, each T-shaped groove 2 comprises a linear groove 21 extending from the outer diameter to the inner diameter of the groove surface end 5 and an arc groove 22 connected with the tail end of the linear groove 21, the width of the arc groove 22 is larger than that of the linear groove 21, the surface of the double-rotation-direction sealing movable ring 1 without the T-shaped groove is a back surface end 6, a pair of pressurizing holes 3 are arranged on the bottom surface of the circular arc groove 22 positioned inside the double-rotation-direction sealing moving ring 1, the pressurizing holes 3 are stepped holes which axially penetrate through the double-rotation-direction sealing moving ring 1 and comprise a small-diameter hole 31 close to the groove surface end 5 and a large-diameter hole 32 close to the back surface end 6, a one-way duck bill valve 4 is arranged in the large-diameter hole 32 of each pressurizing hole 3, and a duck bill end 42 of the duck bill valve 4 extends into the small-diameter hole 31.
Each pair of pressurizing holes 3 is arranged on the bottom surface of the arc groove 22 where the pressurizing holes are arranged in a left-right symmetrical mode relative to the center line of the arc groove.
6-20T-shaped grooves are uniformly distributed at the groove surface end 5 of the double-rotation-direction sealing moving ring 1 along the circumferential direction.
3-6T-shaped grooves distributed at equal intervals in the circumferential direction of the double-rotation-direction sealing moving ring 1 are selected to be provided with pressurizing holes 3. The reason for this is to make the pressure distribution of the pressurizing holes more balanced and uniform over the entire seal moving ring 1 and to make the total dynamic pressure formed by the entire groove group positive.
When the number of the T-shaped grooves is odd, the logarithm of the pressurizing holes 3 is an odd number more than 3; when the number of the T-shaped grooves is even, the number of pairs of the pressurizing holes 3 is even more than 4.
The depth of the T-shaped groove in the groove surface end 5 of the double-screwing-direction sealing moving ring 1 is 8-10 microns.
The one-way duckbill valve is used for controlling the on-off of the airflow at the groove surface end and the back surface end of the double-rotation-direction sealing moving ring 1, and when the pressure at the back surface end of the double-rotation-direction sealing moving ring is higher than the pressure at the groove surface end and is greater than the opening pressure of the duckbill valve, medium gas flows to the moving ring groove surface end from the back surface end of the double-rotation-direction sealing moving ring; when the pressure of the groove surface end of the double-rotation-direction sealing moving ring is higher than the pressure of the back surface end and is higher than the closing pressure of the duckbill valve, the duckbill valve is closed, and the air flow is cut off.
The one-way duck bill valve 4 comprises a rubber seat 41 and a duck bill portion 42, and the duck bill portion 42 is fixed on the rubber seat 41.
The double-rotation-direction sealing moving ring 1 is made of SiC material.
The aperture of the small-diameter hole 31 of the pressurizing hole 3 is 0.2-0.6mm, and the aperture of the large-diameter hole is 3-6 mm.
The embodiment provides a novel double-rotation dynamic pressure synergistic sealing ring. Through CFD simulation, the pressure distribution condition and the opening force of the end face air film of the novel sealing moving ring structure and the original structure are calculated and compared. The result shows that the opening force of the end surface of the novel double-rotation dynamic pressure synergistic sealing ring is increased by 2-4.6% compared with the original design. Particularly, when the rotating speed is lower than 5000 r/min, the dynamic pressure synergistic effect is obvious, and the double-rotation-direction dry gas seal with the structural design has excellent low-speed opening performance. The problem of dry friction of the dry gas sealing end face under the conditions of lower sealing gas pressure and lower rotating speed can be effectively solved.
It is particularly noted that this design is useful not only for T-slots, but also for other double-handed slots.
The foregoing embodiments are merely illustrative of the principles and utilities of the present invention and are not intended to limit the invention. Any person skilled in the art can modify or change the above-mentioned embodiments without departing from the spirit and scope of the present invention. Accordingly, it is intended that all equivalent modifications or changes which can be made by those skilled in the art without departing from the spirit and technical spirit of the present invention be covered by the claims of the present invention.
Claims (10)
1. A double-rotation-direction dynamic pressure synergistic sealing ring is characterized by comprising: the double-rotation-direction sealing movable ring comprises a double-rotation-direction sealing movable ring (1), a plurality of T-shaped grooves (2) are uniformly distributed at the groove face end (5) of the double-rotation-direction sealing movable ring (1) along the circumferential direction, the T-shaped grooves (2) do not penetrate through the double-rotation-direction sealing movable ring (1) in the axial direction, each T-shaped groove (2) comprises a linear groove (21) extending from the outer diameter to the inner diameter of the groove face end (5) and an arc groove (22) connected with the tail end of the linear groove (21), the width of the arc groove (22) is larger than that of the linear groove (21), one surface of the double-rotation-direction sealing movable ring (1) without the T-shaped groove is a back face end (6), a pair of pressurizing holes (3) are arranged on the groove bottom surface of the arc groove (22) positioned inside the double-rotation-direction sealing movable ring (1), the pressurizing holes (3) are stepped holes penetrating through the double-rotation-direction sealing movable ring (1) in the axial direction, and comprise small-diameter holes (, a one-way duckbill valve (4) is arranged in the large-diameter hole (32) of each pressurizing hole (3), and a duckbill end (42) of the duckbill valve (4) extends into the small-diameter hole (31).
2. The dual-rotation dynamic pressure synergistic seal ring of claim 1, wherein: each pair of pressurizing holes (3) are arranged on the bottom surface of the arc groove (22) where the pressurizing holes are located and are arranged in bilateral symmetry with respect to the center line of the arc groove.
3. The dual-rotation dynamic pressure synergistic seal ring of claim 1, wherein: 6-20T-shaped grooves are uniformly distributed at the groove surface end (5) of the double-rotation-direction sealing movable ring (1) along the circumferential direction.
4. The dual-rotation dynamic pressure synergistic seal ring of claim 1, wherein: 3-6T-shaped grooves distributed at equal intervals in the circumferential direction of the double-rotation-direction sealing moving ring (1) are selected to be provided with pressurizing holes (3).
5. A bi-rotational dynamic pressure enhancing seal ring according to claim 1, 3 or 4, wherein: when the number of the T-shaped grooves is odd, the logarithm of the pressurizing holes (3) is an odd number more than 3; when the number of the T-shaped grooves is even, the number of the pairs of the pressurizing holes (3) is an even number more than 4.
6. The dual-rotation dynamic pressure synergistic seal ring of claim 1, wherein: the depth of the T-shaped groove in the groove surface end (5) of the double-rotation-direction sealing moving ring (1) is 8-10 microns.
7. The dual-rotation dynamic pressure synergistic seal ring of claim 1, wherein: the one-way duckbill valve is used for controlling the on-off of the airflow at the groove surface end and the back surface end of the double-rotation-direction sealing moving ring (1), and when the pressure at the back surface end of the double-rotation-direction sealing moving ring is higher than the pressure at the groove surface end and is greater than the opening pressure of the duckbill valve, medium gas flows to the moving ring groove surface end from the back surface end of the double-rotation-direction sealing moving ring; when the pressure of the groove surface end of the double-rotation-direction sealing moving ring is higher than the pressure of the back surface end and is higher than the closing pressure of the duckbill valve, the duckbill valve is closed, and the air flow is cut off.
8. The dual-rotation dynamic pressure synergistic seal ring of claim 1, wherein: the one-way duckbill valve (4) comprises a rubber seat (41) and a duckbill part (42), and the duckbill part (42) is fixed on the rubber seat (41).
9. The dual-rotation dynamic pressure synergistic seal ring of claim 1, wherein: the double-rotation-direction sealing moving ring (1) is made of SiC material.
10. The dual-rotation dynamic pressure synergistic seal ring of claim 1, wherein: the aperture of the small-diameter hole (31) of the pressurizing hole (3) is 0.2-0.6mm, and the aperture of the large-diameter hole is 3-6 mm.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011602588.XA CN112594395A (en) | 2020-12-29 | 2020-12-29 | Double-rotation direction dynamic pressure synergistic sealing ring |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011602588.XA CN112594395A (en) | 2020-12-29 | 2020-12-29 | Double-rotation direction dynamic pressure synergistic sealing ring |
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| Publication Number | Publication Date |
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| CN112594395A true CN112594395A (en) | 2021-04-02 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN202011602588.XA Pending CN112594395A (en) | 2020-12-29 | 2020-12-29 | Double-rotation direction dynamic pressure synergistic sealing ring |
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| CN (1) | CN112594395A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114251455A (en) * | 2021-12-17 | 2022-03-29 | 浙江工业大学 | Mechanical seal end face with double-rotation-direction dynamic pressure effect |
| CN114857273A (en) * | 2022-03-31 | 2022-08-05 | 清华大学 | End face seal assembly |
-
2020
- 2020-12-29 CN CN202011602588.XA patent/CN112594395A/en active Pending
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114251455A (en) * | 2021-12-17 | 2022-03-29 | 浙江工业大学 | Mechanical seal end face with double-rotation-direction dynamic pressure effect |
| CN114857273A (en) * | 2022-03-31 | 2022-08-05 | 清华大学 | End face seal assembly |
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