CN112963543B - Diffusion type self-pumping fluid dynamic and static pressure type mechanical seal - Google Patents
Diffusion type self-pumping fluid dynamic and static pressure type mechanical seal Download PDFInfo
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- CN112963543B CN112963543B CN202110307250.XA CN202110307250A CN112963543B CN 112963543 B CN112963543 B CN 112963543B CN 202110307250 A CN202110307250 A CN 202110307250A CN 112963543 B CN112963543 B CN 112963543B
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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
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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
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Abstract
The invention discloses a diffusion type self-pumping fluid dynamic and static pressure type mechanical seal which comprises a movable ring and a static ring which are coaxially arranged, wherein a first sealing surface of the movable ring comprises a diffusion ring groove, a spiral groove area and a sealing dam from outside to inside, and a backward bending type spiral groove is formed in the spiral groove area; the direction of a fluid outlet of the backward bending type spiral groove is opposite to the rotating direction of the movable ring; a second sealing surface of the static ring is provided with a flow collecting ring groove, a drainage pore channel communicated with the sealing cavity is arranged in a ring body of the static ring, an inlet of the drainage pore channel is positioned on the outer peripheral surface of the static ring, and an outlet of the drainage pore channel is positioned in the flow collecting ring groove; a gap between the second sealing surface and the diffusion ring groove forms an annular diffusion cavity with a radial opening; the first bottom surface of the diffusion ring groove is arranged into a slope surface or a curved surface from outside to inside along the radial direction, and the slope surface or the curved surface is gradually close to the second sealing surface from inside to outside along the radial direction. By the aid of the sealing device, large opening force of the sealing end face can be provided, and the requirement of non-contact mechanical sealing for zero-leakage long-period operation is met.
Description
Technical Field
The invention relates to a diffusion type self-pumping fluid dynamic static pressure type mechanical seal.
Background
The non-contact mechanical seal is widely applied to production equipment such as centrifugal pumps, centrifugal compressors, gas turbines and steam turbines in the industries such as petrochemical industry, aviation industry and nuclear power industry to ensure the seal between a rotating shaft and a shell. The two types of dry gas seal and upstream pumping mechanical seal are mainly used at present, and end face structures such as Chinese patent ZL201020106087.8 and US patent US4290611 are adopted. The fluid wedging type dynamic pressure mechanical seal is characterized in that fluid enters a groove from the inner diameter side or the outer diameter side, a high-pressure flow field is formed at the root of a pressure groove and is blocked by a sealing dam, opening force is generated to separate a dynamic ring sealing interface and a static ring sealing interface, and the friction and the abrasion of the dynamic ring sealing interface and the static ring sealing interface are reduced; when the sealed fluid passes through the sealing dam, the leakage rate is reduced under the action of the resistance of the sealing dam area, so that sealing is realized. However, if the wedging fluid contains solid particles, the flow through the sealing dam during a leak will break the seal interface, causing the seal to fail. To maintain long-term operation of the mechanical seal and improve wedge fluid cleanliness, existing sealing systems are built with blocking fluid supply subsystems, which significantly increases equipment construction and operating costs.
Based on this, chinese patent ZL201310201473.3 proposes a self-pumping fluid dynamic pressure mechanical seal structure, which utilizes the principle that a centrifugal pump or a centrifugal compressor pumps fluid to raise the fluid pressure, and solves the problem that the traditional fluid dynamic pressure seal work needs to provide clean blocking fluid; the chinese patent ZL201910607393.5 proposes that zero leakage of sealed fluid in a static state is achieved by controlling the void ratio between the brake and static ring seal interfaces or by using a combined non-contact double-end-face seal composed of a magnetic fluid seal and a fluid dynamic pressure mechanical seal. However, the self-pumping hydrodynamic mechanical seal solves the problem of blocking the supply subsystem of the fluid, but the low rigidity thereof affects the safety of the operation; the newly proposed combined non-contact double-end-face seal composed of the magnetic fluid seal and the self-pumping fluid dynamic pressure mechanical seal has too low pressure bearing capacity and is not suitable for being used as a rotating shaft seal of middle-low rotating speed rotating machinery such as a centrifugal pump and the like.
Disclosure of Invention
The invention aims to provide a diffusion type self-pumping flow which is provided with a diffusion ring groove and a dynamic pressure groove on the end surface of a dynamic ring of a mechanical seal and a drainage hole and a flow collecting ring groove on the end surface of a static ring
The body dynamic pressure mechanical seal can provide larger opening force of the sealing end face and meet the requirement of non-contact mechanical seal on zero leakage and long-period operation.
The specific technical scheme is as follows:
a diffusion type self-pumping fluid dynamic and static pressure type mechanical seal is arranged between a shell and a rotating shaft of rotating equipment and comprises a moving ring and a static ring which are matched with each other, wherein the moving ring and the static ring are coaxially arranged along an axis, a sealing cavity is formed among the shell, the moving ring and the static ring, the end surface of the moving ring facing the static ring is formed into a first sealing surface, the end surface of the static ring facing the moving ring is formed into a second sealing surface, the first sealing surface is sequentially provided with a diffusion ring groove, a spiral groove area and a sealing dam from outside to inside along the radial direction, at least three backward bending type spiral grooves are formed in the spiral groove area, the at least three backward bending type spiral grooves are uniformly arranged at intervals around the axis, and a sealing weir is formed in an area between two adjacent backward bending type spiral grooves;
the diffusion ring groove is formed by the fact that the outer side of the first sealing surface in the radial direction is recessed downwards along the axial direction, and the diffusion ring groove penetrates through the outer peripheral surface of the rotating ring outwards, so that the diffusion ring groove is provided with a circumferential side surface surrounding the axis and an annular first bottom surface extending in the radial direction; each backward bending type spiral groove is provided with a fluid outlet which penetrates through the circumferential side surface of the diffusion ring groove, and the direction of the fluid outlet is opposite to the rotating direction of the rotating ring;
a second sealing surface of the static ring is provided with a flow collecting ring groove, the flow collecting ring groove extends around the axis, a plurality of drainage pore channels are arranged in a ring body of the static ring, the inlet of each drainage pore channel is positioned on the outer peripheral surface of the static ring, the outlet of each drainage pore channel is positioned in the flow collecting ring groove, and the drainage pore channels are communicated with the sealing cavity and the flow collecting ring groove; when viewed along the axis direction, at least part of the collecting ring groove is overlapped with the spiral groove area, so that the collecting ring groove is communicated with the backward bent spiral groove;
a gap between the second sealing surface and the diffusion ring groove forms an annular diffusion cavity with a radial opening;
along the axis direction, the area of the second sealing surface, which is opposite to the pressure expansion cavity, is in a plane shape perpendicular to the axis; the first bottom surface of the diffusion ring groove is arranged into a slope surface or a curved surface from outside to inside along the radial direction, and the slope surface or the curved surface is gradually close to the second sealing surface from inside to outside along the radial direction.
When the movable ring rotates, the backward-bending spiral groove applies work to the fluid entering the groove, so that the pressure of the fluid is improved, and the speed of the fluid is improved; under the action of centrifugal force, the fluid is thrown out of the backward-bent spiral groove, flows through the pressure expansion cavity and returns to the sealing cavity.
In the process that fluid enters the sealing cavity from the backward-bending type spiral groove, as the flow section is enlarged, the flow velocity of the fluid is reduced, the static pressure is increased, an opening force for pushing the movable ring and the static ring to be separated is formed, a pressure fluid barrier formed by pumped fluid and fluid film shear flow rotating by the follow-up ring and the pressure is gradually increased from the groove root to the outlet of the backward-bending type spiral groove, and the resistance of the sealing dam is formed, so that the fluid in the sealing cavity is difficult to leak to the inner diameter side of the sealing surface to obtain the sealing performance. The fluid at the root of the backward bending type spiral groove flows out to form a low pressure area, the fluid in the sealing cavity enters the flow collecting ring groove through the drainage hole on the static ring under the action of pressure difference, enters the backward bending type spiral groove again, works on the fluid through the backward bending type spiral groove, flows through the pressure expansion cavity under the action of centrifugal force and returns to the sealing cavity, and self-pumping circulation is formed in cycles.
In the application, after fluid enters the diffusion cavity from the backward bending type spiral groove, the flow section of the fluid is suddenly increased, the flow speed is reduced, part of kinetic energy is converted into static pressure energy, and the static pressure energy forms opening force for pushing the static ring and the dynamic ring to divide force in opposite directions. Because the first bottom surface of the diffusion ring groove is arranged to be a slope surface or a curved surface, a relatively stable pressurization space is formed, and the static pressure can not be diluted quickly. Meanwhile, the pressure of the fluid on the slope surface or the curved surface can generate an axial component force, so that the opening force can be further increased.
The larger opening force ensures that the static ring and the dynamic ring have sufficient distance, and the distance is filled with fluid.
Furthermore, the backward-bending type spiral groove is provided with two inner side surfaces arranged along the circumferential direction, wherein one inner side surface is an inner convex side surface protruding towards the inside of the backward-bending type spiral groove, and the other inner side surface is an inner concave side surface recessed towards the inside of the backward-bending type spiral groove; the second bottom surface of the backward-bending spiral groove is obliquely arranged relative to the axis, and the depth of the backward-bending spiral groove is gradually increased from one side of the concave side surface to one side of the convex side surface.
Because the backward bending type spiral groove is a curved flow channel, when fluid flows out from the backward bending type spiral groove, the fluid has a tendency of flowing towards the direction of the inward concave side surface, and generates larger extrusion force to the fluid close to one side of the inward concave side surface, so that the fluid towards one side of the inward concave side surface has larger internal stress, and the internal pressure of the fluid is inconsistent. After the second bottom surface is arranged to be the inclined surface, the volume of the fluid on one side of the concave side surface can be reduced, so that the turbulence of the fluid when the fluid enters the diffusion cavity is reduced, and a larger proportion of potential energy is converted into opening force.
Specifically, the included angle between the second bottom surface of the backward-bending type spiral groove and the axis is 88-89 degrees. The depth of one side of the concave side surface of the backward bending type spiral groove is 20-40 mu m, and the depth of one side of the inner convex side surface is 60-80 mu m. The included angle is too large, so that the amount of fluid on one side of the concave side surface is increased, turbulence is easier to generate, the included angle is too small, the flow cross section on one side of the concave side surface is easy to be too small, smooth flow of the fluid is blocked, and excessive potential energy of the fluid is consumed.
Specifically, the outlet depth of the diffuser ring groove is 10 to 50% of the maximum depth of the backward-curved spiral groove in the axial direction. The design can provide the maximum opening force while ensuring that the fluid smoothly flows out of the diffusion cavity.
Specifically, when the first bottom surface of the diffuser ring groove is curved, the cross section of the first bottom surface is a parabola in a section passing through the axis. This design enables a greater component force in the axial direction to provide a greater opening force as the fluid flows outwardly out of the diffusion chamber.
Further, to provide smooth outward flow, the radially inner end of the parabola is tangent to a plane perpendicular to the axis. The design can ensure that the flow channel of the diffusion ring groove is smoother, and avoid backflow generated in the flowing process of fluid to cause consumption of fluid potential energy.
Specifically, to ensure that the fluid has sufficient flow time to be evenly distributed throughout the diffuser cavity to generate a smooth opening force that separates the stationary ring from the rotating ring, the radial width of the diffuser ring groove is 5-10% of the outer diameter of the rotating ring.
Further, in order to allow the fluid discharged from the collecting ring groove to smoothly enter the backward-curved spiral groove, the collecting ring groove is entirely located in the spiral groove region and the collecting ring groove is located at a radially inner side portion of the backward-curved spiral groove as viewed in the axial direction. Because the flow collecting ring groove is arranged at the radial inner side part of the backward-bending type spiral groove, the fluid entering the backward-bending type spiral groove has enough time to flow out of the backward-bending type spiral groove outwards, a stable flowing state is formed, and the influence of the turbulent flow in the inlet area on the fluid flowing out of the backward-bending type spiral groove is reduced.
Specifically, when the diffusion type self-pumping fluid hydrostatic mechanical seal works, the rotating speed of the rotating ring is 100-4000 rpm. In the rotating speed range, the opening force of the diffusion type self-pumping fluid hydrostatic mechanical seal in non-contact operation is larger than the opening force of the diffusion type self-pumping fluid hydrostatic mechanical seal when the second bottom surface of the backward-bending spiral groove is a plane and the first bottom surface of the diffusion ring groove is a plane.
Drawings
Fig. 1 is a partial structural schematic view of a water pump mounted with an embodiment of the present application.
Fig. 2 is a schematic structural diagram of the rotating ring.
Fig. 3 is a schematic structural diagram of a stationary ring.
Fig. 4 is a cross-sectional view taken along the line a-a in fig. 2.
FIG. 5 is a schematic structural view of another embodiment of a back-curved spiral groove.
Fig. 6 is a sectional view taken along line B-B in fig. 2.
Detailed Description
Referring to fig. 1, 2 and 3, a pressure-expanding self-pumping fluid dynamic static pressure type mechanical seal is arranged between a housing 2 and a rotating shaft 7 of a rotating device, and comprises a rotating ring 3 and a stationary ring 5 which are matched with each other, wherein the rotating ring 3 and the stationary ring 5 are coaxially arranged along an axis 100, and a sealing cavity 1 is formed between the housing and the rotating ring as well as between the housing and the stationary ring.
The rotating shaft 7 is sleeved with the shaft sleeve 6, the shaft sleeve 6 is fixed on the rotating shaft 7 by a set screw penetrating through the screw hole 61, and the rotating ring and the static ring are both sleeved on the rotating shaft 7. The rotating ring 3 is abutted against the step part 62 of the shaft sleeve 6, the static ring 5 is positioned on the outer side of the rotating ring, the static pressure seat 4 is used for abutting the static ring 5 on the rotating ring through the spring 44, and the pin 43 is used for fixing the static ring on the static pressure seat to prevent the static ring from rotating. An end face seal ring 42 is installed between the static pressure seat 4 and the housing 2, an outer seal ring 41 is installed between the static pressure seat 4 and the static ring 5, and an inner seal ring 63 is installed between the dynamic ring 3 and the shaft sleeve 6. The end face seal ring 42, the outer seal ring 41 and the inner seal ring 63 are all O-shaped rubber rings.
The side surface of the moving ring 3 facing the stationary ring 5 is formed into a first sealing surface 31, the side surface of the stationary ring 5 facing the moving ring 3 is formed into a second sealing surface 51, the first sealing surface sequentially comprises a sealing dam 32, a spiral groove area 39 and a diffusion ring groove 34 from inside to outside along the radial direction, ten backward-bent spiral grooves 33 are formed in the spiral groove area 39, the ten backward-bent spiral grooves 33 are uniformly arranged around the axis 100 at intervals, and a sealing weir 36 is formed in the area between every two adjacent backward-bent spiral grooves 33.
The diffuser ring groove 34 is formed by the first sealing surface 31 being recessed axially downward from the radially outer side, and the diffuser ring groove 34 outwardly penetrates the outer peripheral surface 35 of the rotating ring, so that the diffuser ring groove 34 has a circumferential side surface 344 surrounding the axis and a first annular bottom surface 345 extending in the radial direction. Each of the backward-curved spiral grooves has a fluid outlet 334 outwardly penetrating a circumferential side surface of the diffuser groove, the fluid outlet 334 being oriented opposite to a rotation direction of the rotating ring, which is indicated by an arrow 200 in fig. 2.
A collecting ring groove 52 is provided on the second sealing surface 51 of the stationary ring 5, which collecting ring groove 52 extends around the axis 100, and a plurality of flow ducts 56, one flow duct 56 being shown by way of example in fig. 3, are provided in the ring body of the stationary ring 5. The inlet 54 of each drainage channel 56 is positioned on the outer peripheral surface 55 of the stationary ring 5, the outlet 53 of each drainage channel 56 is positioned in the collecting ring groove 52, and the drainage channels 56 are communicated with the sealing cavity 1 and the collecting ring groove 52. The collecting ring groove 52 is partially located in the spiral groove region 39 as viewed in the axial direction, so that the collecting ring groove 52 communicates with the backward curved spiral groove 33. In the present embodiment, the collecting ring groove 52 is located at the radially inner side portion of the backward curved spiral groove.
The gap between the second sealing surface and the diffuser ring groove forms an annular diffuser cavity 60 with a radial opening.
Along the axis, the area of the second sealing surface 51 opposite to the pressure expansion cavity is in a plane shape perpendicular to the axis; the first bottom surface 345 of the diffuser ring groove is formed as a sloping surface that gradually approaches the second sealing surface 51 from the inside to the outside in the radial direction. Referring to fig. 4, a cross section of the first bottom surface 345 of the diffuser groove is an inclined line 341 inclined with respect to the axis.
Referring to fig. 2 and 6, each backward curved spiral groove 33 has two inner side surfaces arranged along the circumferential direction, wherein one inner side surface is an inner convex side surface 332 protruding towards the inside of the backward curved spiral groove, and the other inner side surface is an inner concave side surface 331 recessed towards the outside of the backward curved spiral groove.
In the present embodiment, the second bottom surface 333 of the backward spiral groove 33 is inclined with respect to the axis 100, and the depth of the second bottom surface 333 of the backward spiral groove 33 gradually increases from the concave side surface side toward the convex side surface side. Specifically, in this embodiment, the angle α between the second bottom surface 333 and the axis 100 is 88.8644 °. It is understood that in other embodiments, the included angle α may be other angles between 88-89. In fig. 6, the position of the axis 100 is shifted in parallel for clarity of illustration.
Referring to fig. 4, in the axial direction, the outlet depth S of the diffuser groove is 45% of the maximum depth H of the outlet 334 of the backward curved spiral groove, and the maximum depth H of the outlet 334 of the backward curved spiral groove is located at the side of the inward convex side surface 332.
It will be appreciated that in other embodiments, the outlet depth S of the diffuser groove may also be 10%, 30%, or 50% of the maximum depth H of the outlet 334 of the back-curved spiral groove.
In this embodiment, the radial width F of the diffuser ring groove is 8mm, and the outer diameter of the rotating ring is 100mm, that is, the radial width F of the diffuser ring groove is 8% of the outer diameter of the rotating ring, it can be understood that in other embodiments, the radial width F of the diffuser ring groove may also be 5%, 6%, 7%, 9%, or 10%, or other data between 5% and 10% of the outer diameter of the rotating ring according to different requirements.
In the present embodiment, the cross section of the first bottom surface 345 of the diffuser groove 34 in the cross section passing through the axis is an inclined line 341. Referring to fig. 5, in another embodiment, the cross section of the first bottom surface a745 of the diffuser ring groove a74 is a parabola 741, which starts from the circumferential side surface of the diffuser ring groove a74, extends outward in the radial direction, and bends toward the stationary ring direction, so that the first bottom surface a745 of the diffuser ring groove a74 presents a curved surface. The radially inner end of the parabola is tangent to a plane perpendicular to the axis.
Table 1 shows the change of the opening force between the stationary ring and the moving ring when the first bottom surface of the diffuser ring groove is provided with the slope. The cross section of the first bottom surface 345 of the diffuser groove 34 is an inclined line 341, and the inclination of the inclined line is adjusted to adjust the ratio between the outlet depth S of the diffuser groove and the maximum depth H of the outlet of the backward-curved spiral groove, and the other conditions are the same.
TABLE 1
| W | Opening force (n ═ 2000rpm) |
| 1/10 | 1248.09248N |
| 1/3 | 1211.92496N |
| 1/2 | 1204.878368N |
In table 1, W is S/H.
When the first bottom surface of the diffuser ring groove is in a planar shape perpendicular to the axis, the opening force (N ═ 2000rpm) is 1198.38224N, that is, when the first bottom surface of the diffuser ring groove is set to be a slope, the opening force can be increased by 4.15%.
The same effect is obtained when the first bottom surface of the diffuser ring groove is curved.
The included angle alpha between the second bottom surface of the backward-bending spiral groove and the axis is set to 88-89 degrees, and when the depth of one side of the concave side surface of the backward-bending spiral groove is more than or equal to 20 microns and less than or equal to 40 microns, the opening force can be improved by 2-4 percent.
When the diffusion type self-pumping fluid hydrostatic mechanical seal works, the rotating speed of the rotating ring is controlled to be 100-4000 rpm.
Claims (10)
1. A diffusion type self-pumping fluid dynamic static pressure type mechanical seal is arranged between a shell and a rotating shaft of rotating equipment, comprises a movable ring and a static ring which are matched with each other, the movable ring and the static ring are coaxially arranged along an axis, and a sealing cavity is formed between the shell and the movable ring as well as between the shell and the static ring,
the end face of the moving ring facing the static ring is formed into a first sealing face, the end face of the static ring facing the moving ring is formed into a second sealing face, the first sealing face sequentially comprises a diffusion ring groove, a spiral groove area and a sealing dam from outside to inside along the radial direction, the spiral groove area is provided with at least three backward-bending spiral grooves, the at least three backward-bending spiral grooves are uniformly arranged around the axis at intervals, and a sealing weir is formed in an area between every two adjacent backward-bending spiral grooves;
the diffusion ring groove is formed by the fact that the outer side of the first sealing surface in the radial direction is recessed downwards along the axial direction, and the diffusion ring groove penetrates through the outer peripheral surface of the rotating ring outwards, so that the diffusion ring groove is provided with a circumferential side surface surrounding the axis and an annular first bottom surface extending in the radial direction; each backward bending type spiral groove is provided with a fluid outlet which penetrates through the circumferential side surface of the diffusion ring groove, and the direction of the fluid outlet is opposite to the rotating direction of the rotating ring;
a second sealing surface of the static ring is provided with a flow collecting ring groove, the flow collecting ring groove extends around the axis, a plurality of drainage pore channels are arranged in a ring body of the static ring, the inlet of each drainage pore channel is positioned on the outer peripheral surface of the static ring, the outlet of each drainage pore channel is positioned in the flow collecting ring groove, and the drainage pore channels are communicated with the sealing cavity and the flow collecting ring groove; when viewed along the axis direction, at least part of the collecting ring groove is overlapped with the spiral groove area, so that the collecting ring groove is communicated with the backward bent spiral groove;
a gap between the second sealing surface and the diffusion ring groove forms an annular diffusion cavity with a radial opening;
along the axis direction, the area of the second sealing surface, which is opposite to the pressure expansion cavity, is in a plane shape perpendicular to the axis; the first bottom surface of the diffusion ring groove is arranged into a slope surface or a curved surface from outside to inside along the radial direction, and the slope surface or the curved surface is gradually close to the second sealing surface from inside to outside along the radial direction.
2. A diffusion-type self-pumping hydrodynamic static pressure-type mechanical seal according to claim 1,
the backward-bending type spiral groove is provided with two inner side surfaces arranged along the circumferential direction, wherein one inner side surface is an inward convex side surface protruding towards the inside of the backward-bending type spiral groove, and the other inner side surface is an inward concave side surface recessed towards the inside of the backward-bending type spiral groove;
the second bottom surface of the backward-bending spiral groove is obliquely arranged relative to the axis, and the depth of the backward-bending spiral groove is gradually increased from one side of the concave side surface to one side of the convex side surface.
3. A diffusion-type self-pumping hydrodynamic static pressure-type mechanical seal according to claim 2,
the included angle between the second bottom surface of the backward-bending type spiral groove and the axis is 88-89 degrees.
4. A diffusion-type self-pumping hydrodynamic static pressure-type mechanical seal according to claim 2,
the depth of the concave side surface of the backward bending type spiral groove is 20-40 μm, and the depth of the concave side surface of the backward bending type spiral groove is 60-80 μm.
5. A diffusion-type self-pumping hydrodynamic static pressure-type mechanical seal according to claim 1,
in the axial direction, the outlet depth of the diffusion ring groove is 10-50% of the maximum depth of the backward-bending type spiral groove.
6. A diffusion-type self-pumping hydrodynamic static pressure-type mechanical seal according to claim 1,
when the first bottom surface of the diffuser ring groove is curved, the cross section of the first bottom surface is a parabola on the cross section passing through the axis.
7. A diffusion self-pumping hydrodynamic static pressure type mechanical seal according to claim 6 wherein the radially inner end of the parabola is tangent to a plane perpendicular to the axis.
8. A diffusion self-pumping hydrostatic mechanical seal as claimed in claim 1, wherein the radial width of the diffusion ring groove is 5-10% of the outer diameter of the rotating ring.
9. A diffusion self-pumping fluid hydrostatic mechanical seal of claim 1, wherein the collector ring groove is located entirely in the spiral groove region and the collector ring groove is located radially inward of the backward curved spiral groove, as viewed along the axial line.
10. The diffusion-type self-pumping hydrostatic mechanical seal of claim 1, wherein the rotating speed of the rotating ring is 100-4000rpm when the diffusion-type self-pumping hydrostatic mechanical seal is operated.
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| CN202110307250.XA CN112963543B (en) | 2021-03-23 | 2021-03-23 | Diffusion type self-pumping fluid dynamic and static pressure type mechanical seal |
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| CN202110307250.XA CN112963543B (en) | 2021-03-23 | 2021-03-23 | Diffusion type self-pumping fluid dynamic and static pressure type mechanical seal |
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| CN112963543B true CN112963543B (en) | 2022-04-19 |
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| CN114382893B (en) * | 2021-12-15 | 2023-01-13 | 清华大学 | Dynamic pressure type self-circulation magnetic liquid sealing device |
| CN115325034B (en) * | 2022-08-16 | 2023-08-08 | 南京林业大学 | High-speed rolling bearing sealing structure with fluid self-pumping effect |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2006077899A (en) * | 2004-09-10 | 2006-03-23 | Nippon Pillar Packing Co Ltd | Non-contact sealing device |
| CN203363185U (en) * | 2013-07-10 | 2013-12-25 | 南京林业大学 | Split type mechanical seal with self-tightening seal capacity |
| CN105465371A (en) * | 2015-12-30 | 2016-04-06 | 南京林业大学 | Bidirectional-rotation self-pumping fluid dynamic pressure type mechanical seal |
| CN110410504A (en) * | 2019-07-15 | 2019-11-05 | 北京航空航天大学 | A kind of mechanical seal end surface structure of varying depth spiral T-slot |
| CN211288740U (en) * | 2019-12-26 | 2020-08-18 | 温州市天成密封件制造有限公司 | Upstream pumping mechanical sealing ring with elliptical groove |
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Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2006077899A (en) * | 2004-09-10 | 2006-03-23 | Nippon Pillar Packing Co Ltd | Non-contact sealing device |
| CN203363185U (en) * | 2013-07-10 | 2013-12-25 | 南京林业大学 | Split type mechanical seal with self-tightening seal capacity |
| CN105465371A (en) * | 2015-12-30 | 2016-04-06 | 南京林业大学 | Bidirectional-rotation self-pumping fluid dynamic pressure type mechanical seal |
| CN110410504A (en) * | 2019-07-15 | 2019-11-05 | 北京航空航天大学 | A kind of mechanical seal end surface structure of varying depth spiral T-slot |
| CN211288740U (en) * | 2019-12-26 | 2020-08-18 | 温州市天成密封件制造有限公司 | Upstream pumping mechanical sealing ring with elliptical groove |
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