CN203051777U - Mechanical face seal with combined fluid groove structure - Google Patents
Mechanical face seal with combined fluid groove structure Download PDFInfo
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- CN203051777U CN203051777U CN 201220591958 CN201220591958U CN203051777U CN 203051777 U CN203051777 U CN 203051777U CN 201220591958 CN201220591958 CN 201220591958 CN 201220591958 U CN201220591958 U CN 201220591958U CN 203051777 U CN203051777 U CN 203051777U
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Abstract
The utility model relates to a mechanical face seal with a combined fluid groove structure. The seal face of a movable ring is provided with a plurality of groups of fluid grooves, the fluid grooves are periodically arranged in the circumferential direction of a seal face, the fluid grooves consist of large grooves and small grooves, each large groove is arranged at the outer radius side of the face, one end, communicated with a sealing medium, of each large groove is a pump suction port, the other end, connected with each small groove, of each large groove is a leak port, each small groove is arranged in the middle part of the seal face, one end, communicated with each large groove, of each small groove is a pump suction port, one end, connected with a sealing dam of a non-grooved area at the inner radius part of the seal face, of each small groove is a leak port, and the depths of the large grooves and the small grooves are gradually reduced in a convergent way according to the radius of the seal face, and are also changed in the convergent way from the convex surface to the concave surface of each groove wall in the circumferential direction. The mechanical face seal is suitable for the working conditions of wide pressure range of fluid at the two sides of the seal face and the wide viscosity range of seal fluid, and has the effects of larger face opening force, and smaller leakage rate under the condition of same opening force.
Description
Technical field
The invention belongs to technical field of sealing technology, particularly a kind of mechanical end face seal with composite fluid type groove structure is applicable to the sealing of the running shaft of rotating machineries such as various compressors, centrifugal pump, reactor stirrer.
Background technique
The rotating shaft sealing of fluid machinery often adopts traditional mechanical seal, packing seal, outside framework oil seal, labyrinth seal etc., but traditional mechanical seal, packing seal, the friction behavior that outside framework oil seal etc. exist, increase power consumption on the one hand, shortened sealing life on the other hand, increased the frequency of device maintenance; And the leak-down rate of labyrinth seal is bigger, and in the high parameter turbocompressor, labyrinth seal still causes the one of the main reasons of rotor-support-foundation system self-excited vibration.The appearance of hydrodynamic seal as the use of type groove non-contacting mechanical face seals such as spiral chute, has solved the fretting wear problem of rotating shaft sealing preferably.At present, utilize principle of hydrodynamics, realize that by offer the dynamic pressure groove at sealing surface the non-contacting mechanical face seal of seal face non-contact operation has been widely used on the equipment such as the centrifugal compressor of oil, chemical industry, chemical fibre, papermaking, electric power and metallurgy industry, blower fan, centrifugal pump.Certainly, when type groove non-contacting mechanical face seals such as spiral chute normally moved, the face type groove produced hydrodynamic and forms face opening power, has reduced the wearing and tearing of seal face, had also increased leak-down rate simultaneously.U. S. Patent 5,201,531 disclosed a kind of Hydrodynamic pressure type double spiral groove face seals have been in harmonious proportion this contradiction effectively.Under given rotation direction, this seal arrangement utilizes upstream one row spiral chute with fluid-encapsulated pumping downstream, downstream one row spiral chute is then with fluid-encapsulated pumping upstream, and the both sides fluid pressure difference balances each other inside and outside drawing pressure reduction and seal face by the pump that this two row spiral chute produces, thereby realizes the zero leakage of screw groove end face sealing.But this class seal request has wideer seal face, and it is less to be only applicable to the pressure reduction of seal face two side liquids, the operating mode that fluid-encapsulated viscosity is higher.
Summary of the invention
The objective of the invention is to propose a kind of seal face both sides hydrodynamic pressure, wide in range mechanical end face seal with composite fluid type groove structure of fluid-encapsulated range of viscosities of being applicable to, the single-row screw groove end face sealing spare face opening power of generally using now is little, leak-down rate is big to solve, the sealed end face width of double spiral groove edge face sealing member, the problem that installing space is big, acquisition has bigger face opening power than above-mentioned sealing under identical condition, perhaps have the effect of littler leak-down rate under identical opening force.
Technological scheme of the present invention is:
A kind of mechanical end face seal with composite fluid type groove structure, be arranged between the casing and axle of rotating machinery, casing is supporting stationary ring, be provided with spring between the back side of stationary ring and casing, under the effect of spring, the stationary ring seal face is set in one that axle is gone up and the seal face of the rotating ring that can rotate with axle is close to, seal face at described rotating ring is provided with many group fluid type grooves, described fluid type groove circumferentially is periodic arrangement along seal face, non-slot area between the described fluid type groove constitutes the sealing weir, and the non-slot area of described seal face inner radius constitutes the sealing dam; Described fluid type groove is constituted by large-scale groove and small-sized groove, and described large-scale groove is arranged on the outside diameter of described end face, and its end that is connected with sealing medium is that pump draws mouth, and the other end that links to each other with small-sized groove is leakage hole; Described small-sized groove is arranged on the middle part of described end face, and its end that is connected with large-scale groove is that pump draws mouth, and an end that links to each other with the sealing dam of the non-slot area of seal face inner radius is leakage hole; The groove depth of described large-scale groove and small-sized groove is the convergence type from large to small by the seal face radius and changes, and changes along circumferentially also being the convergence type by cell wall convex surface to concave surface.
The cell wall molded lines of the both sides of described large-scale groove and small-sized groove is helix.
The cell wall concave surface molded lines of described small-sized groove is connected on the concave surface molded lines of large-scale groove, and the pump of small-sized groove draws the leakage hole that mouth is connected in large-scale groove.
The groove depth of described large-scale groove and small-sized groove is the linear convergence type from large to small by the sealing surface radius and changes, and the groove depth of large-scale groove and small-sized groove changes along circumferentially being the linear convergence type by cell wall convex surface to concave surface.
The groove of described fluid type groove is counted n:10≤n≤40, the pitch angle alpha will of groove: 12 °≤α≤25 °, and bottom land straight line convergence inclined-plane radially or the angle β of ladder convergence inclined-plane and end face
r: 0.02 °≤β
r≤ 0.1 °, bottom land is along the angle β of circumferential linear convergence inclined-plane and end face
θ: 0.02 °≤β
θ≤ 0.1 °, large-scale groove compares L with the radial length of small-sized groove
1/ L
2: 2≤L
1/ L
2≤ 4, the radial length of fluid type groove and seal face width are than L/W:0.6≤L/W≤0.8, and it is wide than B/C:0.8≤B with the weir of each autotype groove that the pump of large-scale groove and small-sized groove draws mouthful width
1/ C
1≤ 1.2,0.2≤B
2/ C
2≤ 0.4.
The groove depth of described large-scale groove is 3-4 the ladder equal difference convergence type that successively decreases by seal face by the outside to inboard and changes, and small-sized groove is 1 ladder, and its groove depth is than 1 tolerance of the minigroove depth of large-scale groove; The groove depth of described large-scale groove and small-sized groove changes along circumferentially being the linear convergence type by cell wall convex surface to concave surface.
Working principle of the present invention is: radially and circumferentially be the fluid type groove of restraining the inclined-plane, when seal face rotates, draw mouth from the pump in the large-scale groove outside and pump into fluid, under the effect on bottom land straight line convergence inclined-plane or ladder convergence inclined-plane, produce hydrodynamic and opening force, and obtain bigger fluid film rigidity, form certain anti-interference capability and operation stability; The inboard small-sized groove that connects of large-scale groove, its degree of depth and groove width are all littler than large-scale groove, have further strengthened the bearing capacity of fluid film, have reduced leak-down rate, and the sealing dam on the seal face plays the effect of parking sealer and the leakage of retardance fluid.
Operational condition and sealing auxiliary system operating parameter at different pumped medium, pump, the radial length of the linear convergence inclined-plane of the groove number by optimal design fluid type groove, the helix angle of groove, bottom land or ladder convergence inclined-plane and the angle of end face, large-scale groove and small-sized groove draws the wide parameter such as compare in mouthful width and the weir of each autotype groove than the radial length of, fluid type groove and seal face width than the pump of, large-scale groove and small-sized groove, can satisfy under the different occasions usage requirement to sealability.
Beneficial effect of the present invention
Mechanical end face seal with composite fluid type groove structure of the present invention, its fluid dynamic pressure groove is made up of vat and sulculus, groove depth by the sealing surface radius from large to small, change along circumferentially being the convergence type by cell wall convex surface to concave surface, fluid-encapsulated when pumping into fluid dynamic pressure groove pressure increase gradually, so show as following advantage in its performance: 1. fluid film rigidity is big, bearing capacity is strong, the pressure differential range that is applicable to seal face two side liquids is bigger, the operating mode that fluid-encapsulated range of viscosities is wideer; 2. leak-down rate is little.Its leak-down rate is suitable with contact-type mechanical seal, is 85% of general screw groove end face sealing; 3. power consumpiton is little.The general screw groove end face sealing of its power consumption Lve Gaoding, but only be about 5% of contact-type mechanical seal; 4. because the fluid dynamic pressure groove circumferential lengths is longer, and fluid film pressure is more even, stable and reliable operation is not only applicable to high speed operation, is applicable to low cruise yet; 5. adopt single-row groove, seal f ace width is narrower than above-mentioned biserial groove sealing surface.
Description of drawings
Fig. 1 is a kind of mechanical end face seal schematic representation with composite fluid type groove structure.
Fig. 2 is a kind of rotating ring seal face schematic representation with composite fluid type groove structure.
Fig. 3 uses the groove depth sectional view of the helicoid intercepting that is parallel to cell wall for the mix flow build groove of Fig. 2.
Fig. 4 is the groove depth sectional view that the mix flow build groove of Fig. 2 is used the cylndrical surface intercepting of different radii.
Fig. 5 is the described rotating ring graphics with composite fluid type groove structure of Fig. 2.
Fig. 6 is another kind of rotating ring seal face schematic representation with composite fluid type groove structure.
Fig. 7 uses the groove depth sectional view of the helicoid intercepting that is parallel to cell wall for the mix flow build groove of Fig. 6.
Fig. 8 is the groove depth sectional view that the mix flow build groove of Fig. 6 is used the cylndrical surface intercepting of different radii.
Fig. 9 is the described rotating ring graphics with composite fluid type groove structure of Fig. 6.
Wherein,
The inside radius of the seal face of fitting mutually between R0---rotating ring and the stationary ring;
R1---the inside radius of small-sized groove 4-5;
R2---the outer radius of small-sized groove 4-5, the inside radius of large-scale groove 4-4;
The outer radius of the seal face of fitting mutually between R3---rotating ring and the stationary ring;
Rb---equilibrium radius;
G---the pump of fluid type groove 4-2 draws direction;
α---helix angle;
W---end face offers the rotation direction of the rotating ring of fluid type groove 4-2;
B
1/ C
1---the pump of large-scale groove draws mouthful width and the wide ratio in the weir of its type groove;
B
2/ C
2---the pump of small-sized groove draws mouthful width and the wide ratio in the weir of its type groove;
β
θ---bottom land is along circumferential linear convergence inclined-plane and the angle of end face;
β
r---bottom land straight line convergence inclined-plane radially or the angle of ladder convergence inclined-plane and end face;
The radial length of L/W---fluid type groove and seal face width ratio, L=R3-R1, W=R3-R0;
The 1-axle; The 2-casing; The 3-stationary ring; The 4-rotating ring; 4-1-seals the dam; 4-2-fluid type groove; 4-3-seals the weir; The large-scale groove of 4-4-; The small-sized groove of 4-5-; The pump of the large-scale groove of 4-6-draws mouth; The cell wall convex surface of the large-scale groove of 4-7-; The cell wall concave surface of the large-scale groove of 4-8-; The leakage hole of the large-scale groove of 4-9-; The pump of the small-sized groove of 4-10-draws mouth; The cell wall concave surface of the small-sized groove of 4-11-; The leakage hole of the small-sized groove of 4-12-; The cell wall convex surface of the large-scale groove of 4-13-; The 5-spring; The 6-axle sleeve.
Embodiment
Describe embodiments of the present invention in detail below in conjunction with drawings and Examples.
Embodiment one
Fig. 1 is a kind of mechanical end face seal with composite fluid type groove structure, be arranged between the casing 2 and axle 1 of rotating machinery, casing 2 is supporting stationary ring 3,2 of the back side of stationary ring 3 and casings are provided with spring 5, under the effect of spring 5, the seal face of the rotating ring 4 that the seal face of stationary ring 5 is set on the axle 1 with and can rotates with axle 1 is close to, seal face at described rotating ring 4 is provided with many group fluid type groove 4-2, described fluid type groove 4-2 circumferentially is periodic arrangement along seal face, non-slot area between the described fluid type groove 4-2 constitutes sealing weir 4-3, and the non-slot area of described seal face inner radius constitutes sealing dam 4-1; Described fluid type groove 4-2 is constituted by large-scale groove 4-4 and small-sized groove 4-5, and described large-scale groove 4-4 is arranged on the outside diameter of described end face, and its end that is connected with sealing medium is that pump draws a mouthful 4-6, and the other end that links to each other with small-sized groove 4-5 is leakage hole 4-9; Described small-sized groove 4-5 is arranged on the middle part of described end face, and its end that is connected with large-scale groove 4-4 is that pump draws a mouthful 4-10, and an end that links to each other with the sealing dam of the non-slot area of seal face inner radius is leakage hole 4-12; The groove depth of described large-scale groove 4-4 and small-sized groove 4-5 is the convergence type from large to small by the seal face radius and changes, and changes along circumferentially also being the convergence type by cell wall convex surface to concave surface.
The cell wall molded lines of the both sides of described large-scale groove 4-4 and small-sized groove 4-5 is helix.
The cell wall concave surface 4-11 molded lines of described small-sized groove is connected on the cell wall concave surface 4-8 molded lines of large-scale groove, and the pump of small-sized groove draws the leakage hole 4-9 that mouthful 4-10 is connected in large-scale groove.
The groove depth of described large-scale groove 4-4 and small-sized groove 4-5 is the linear convergence type from large to small by the sealing surface radius and changes, and the groove depth of large-scale groove 4-4 and small-sized groove 4-5 changes along circumferentially being the linear convergence type by cell wall convex surface to concave surface.
Fig. 2, Fig. 3 and Fig. 4 have expressed the form of the rotating ring with composite fluid type groove structure.In the present embodiment, the groove of fluid type groove is counted n=12, the pitch angle alpha will of groove=15.5 °, bottom land radially straight line convergence inclined-plane and the angle β of end face
r=0.04 °, bottom land is along the angle β of circumferential linear convergence inclined-plane and end face
θ=0.04 °, large-scale groove 4-4 compares L with the radial length of small-sized groove 4-54-2
1/ L
2=3, the radial length of fluid type groove and seal face width are than L/W=0.7, and the pump of large-scale groove 4-4 and small-sized groove 4-5 draws mouthful width and the wide B/C:B of ratio in the weir of each autotype groove
1/ C
1=1.0, B
2/ C
2=0.33, the graphics of its rotating ring as shown in Figure 5.
Radially and circumferentially be the fluid type groove 4-2 that restrains the inclined-plane, when seal face rotates with the w direction, pump outside large-scale groove 4-4 draws mouth and pumps into fluid (as G direction Fig. 1), under the effect on bottom land straight line convergence inclined-plane or ladder convergence inclined-plane, produce hydrodynamic and opening force, and obtain bigger fluid film rigidity, form certain anti-interference capability and operation stability; The inboard small-sized groove 4-5 that connects of large-scale groove 4-4, its degree of depth and groove width are all littler than large-scale groove, have further strengthened the bearing capacity of fluid film, have reduced leak-down rate, and the sealing dam on the seal face plays the effect of parking sealer and the leakage of retardance fluid.
Operational condition and sealing auxiliary system operating parameter at different pumped medium, pump, the radial length of the linear convergence inclined-plane of the groove number by optimal design fluid type groove, the helix angle of groove, bottom land or ladder convergence inclined-plane and the angle of end face, large-scale groove 4-4 and small-sized groove 4-5 draws the wide parameter such as compare in mouthful width and the weir of each autotype groove than the radial length of, fluid type groove and seal face width than the pump of, large-scale groove 4-4 and small-sized groove 4-5, can satisfy under the different occasions usage requirement to sealability.
Embodiment two
With reference to Fig. 6, Fig. 7 and Fig. 8, present embodiment and embodiment's one difference is that the groove depth of the large-scale groove 4-4 of described fluid type groove is 3 ladder equal difference convergence type that successively decreases by seal face by the outside to inboard and changes, small-sized groove 4-5 is 1 ladder, and its groove depth is than 1 tolerance of the minigroove depth of large-scale groove 4-4; Bottom land ladder is radially restrained the angle β of inclined-plane and end face
r=0.04 °; The large-scale groove 4-4 of fluid type groove and the groove depth of small-sized groove 4-5 change along circumferentially being the linear convergence type by cell wall convex surface to concave surface, and bottom land is along the angle β of circumferential linear convergence inclined-plane and end face
θ=0.04 °, the graphics of its rotating ring as shown in Figure 9.All the other structures and mode of execution are identical with embodiment one.
Claims (6)
1. mechanical end face seal with composite fluid type groove structure, be arranged between the casing (2) and axle (1) of rotating machinery, casing (2) is supporting stationary ring (3), be provided with spring (5) between the back side of stationary ring (3) and casing (2), under the effect of spring (5), stationary ring (3) seal face is set in one that axle (1) is gone up and the seal face of the rotating ring (4) that can rotate with axle (1) is close to, seal face at described rotating ring (4) is provided with many group fluid type grooves (4-2), described fluid type groove (4-2) circumferentially is periodic arrangement along seal face, non-slot area between the described fluid type groove (4-2) constitutes sealing weir (4-3), and the non-slot area of described seal face inner radius constitutes sealing dam (4-1); It is characterized in that: described fluid type groove (4-2) is constituted by large-scale groove (4-4) and small-sized groove (4-5), described large-scale groove (4-4) is arranged on the outside diameter of described end face, its end that is connected with sealing medium is that pump draws mouthful (4-6), and the other end that links to each other with small-sized groove (4-5) is leakage hole (4-9); Described small-sized groove (4-5) is arranged on the middle part of described end face, and its end that is connected with large-scale groove (4-4) is that pump draws mouthful (4-10), and an end that links to each other with the sealing dam (4-1) of the non-slot area of seal face inner radius is leakage hole (4-12); The groove depth of described large-scale groove (4-4) and small-sized groove (4-5) is the convergence type from large to small by the seal face radius and changes, and changes along circumferentially also being the convergence type by cell wall convex surface to concave surface.
2. the mechanical end face seal with composite fluid type groove structure as claimed in claim 1, it is characterized in that: the cell wall molded lines of the both sides of described large-scale groove (4-4) and small-sized groove (4-5) is helix.
3. the mechanical end face seal with composite fluid type groove structure as claimed in claim 2, it is characterized in that: cell wall concave surface (4-11) molded lines of described small-sized groove is connected on cell wall concave surface (4-8) molded lines of large-scale groove, and the pump of small-sized groove draws the leakage hole (4-9) that mouthful (4-10) is connected in large-scale groove.
4. the mechanical end face seal with composite fluid type groove structure as claimed in claim 3, it is characterized in that: the groove depth of described large-scale groove (4-4) and small-sized groove (4-5) is the linear convergence type from large to small by the sealing surface radius and changes, and the groove depth of large-scale groove (4-4) and small-sized groove (4-5) changes along circumferentially being the linear convergence type by cell wall convex surface to concave surface.
5. the mechanical end face seal with composite fluid type groove structure as claimed in claim 3, it is characterized in that: the groove of described fluid type groove is counted n:10≤n≤40, the pitch angle alpha will of groove: 12 °≤α≤25 °, bottom land straight line convergence inclined-plane radially or the angle β of ladder convergence inclined-plane and end face
r: 0.02 °≤β
r≤ 0.1 °, bottom land is along the angle β of circumferential linear convergence inclined-plane and end face
θ: 0.02 °≤β
θ≤ 0.1 °, large-scale groove (4-4) compares L with the radial length of small-sized groove (4-5)
1/ L
2: 2≤L
1/ L
2≤ 4, the radial length of fluid type groove and seal face width be than L/W:0.6≤L/W≤0.8, and it is wide than B/L:0.8≤B with the weir of each autotype groove that the pump of large-scale groove (4-4) and small-sized groove (4-5) draws mouthful width
1/ L
1≤ 1.2,0.2≤B
2/ L
2≤ 0.4.
6. the mechanical end face seal with composite fluid type groove structure as claimed in claim 3, it is characterized in that: the groove depth of described large-scale groove (4-4) is 3-4 the ladder equal difference convergence type that successively decreases by seal face by the outside to inboard and changes, small-sized groove (4-5) is 1 ladder, and its groove depth is than 1 tolerance of the minigroove depth of large-scale groove (4-4); The groove depth of described large-scale groove (4-4) and small-sized groove (4-5) changes along circumferentially being the linear convergence type by cell wall convex surface to concave surface.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201220591958 CN203051777U (en) | 2012-11-12 | 2012-11-12 | Mechanical face seal with combined fluid groove structure |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201220591958 CN203051777U (en) | 2012-11-12 | 2012-11-12 | Mechanical face seal with combined fluid groove structure |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203051777U true CN203051777U (en) | 2013-07-10 |
Family
ID=48734731
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201220591958 Expired - Fee Related CN203051777U (en) | 2012-11-12 | 2012-11-12 | Mechanical face seal with combined fluid groove structure |
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| Country | Link |
|---|---|
| CN (1) | CN203051777U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102927287A (en) * | 2012-11-12 | 2013-02-13 | 南京林业大学 | Mechanical end face seal with combined fluid slot structure |
| WO2015187657A3 (en) * | 2014-06-03 | 2017-05-18 | Thermo King Corporation | Mechanical face seal |
| CN114483962A (en) * | 2022-04-02 | 2022-05-13 | 东营海森密封技术有限责任公司 | Wing-shaped dynamic pressure non-contact sealing structure |
-
2012
- 2012-11-12 CN CN 201220591958 patent/CN203051777U/en not_active Expired - Fee Related
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102927287A (en) * | 2012-11-12 | 2013-02-13 | 南京林业大学 | Mechanical end face seal with combined fluid slot structure |
| WO2015187657A3 (en) * | 2014-06-03 | 2017-05-18 | Thermo King Corporation | Mechanical face seal |
| CN114483962A (en) * | 2022-04-02 | 2022-05-13 | 东营海森密封技术有限责任公司 | Wing-shaped dynamic pressure non-contact sealing structure |
| CN114483962B (en) * | 2022-04-02 | 2022-06-24 | 东营海森密封技术有限责任公司 | Wing-shaped dynamic pressure non-contact sealing structure |
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Granted publication date: 20130710 Termination date: 20161112 |
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