CN102022542B - Negative pressure groove end face mechanical seal structure - Google Patents
Negative pressure groove end face mechanical seal structure Download PDFInfo
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- CN102022542B CN102022542B CN2010105830829A CN201010583082A CN102022542B CN 102022542 B CN102022542 B CN 102022542B CN 2010105830829 A CN2010105830829 A CN 2010105830829A CN 201010583082 A CN201010583082 A CN 201010583082A CN 102022542 B CN102022542 B CN 102022542B
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- dynamic pressure
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- 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
- 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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Abstract
The invention relates to a negative pressure groove end face mechanical seal structure, comprising a mechanically sealed moving ring and a mechanically sealed static ring, one side of the end faces of the moving ring and the static ring is a high pressure side namely upstream, the other side of the end faces of the moving ring and the static ring is a low pressure side namely downstream, at least one end face of the moving ring or the static ring is provided with negative pressure groove groups which are symmetrically distributed with the center of rotation, the upstream of each negative pressure groove group is provided with a micropore annular band, each negative pressure groove group is composed of micropore dynamic pressure grooves with spiral deformation and inclination and relief grooves, the micropore dynamic pressure grooves and the relief grooves are distributed at intervals, the relief grooves are close to the terminals of the dynamic pressure grooves, and the downstream of each negative pressure groove group is provided with an annular sealing dam with a smooth plane. The invention has the beneficial effects of enhancing antijamming capability of sealing in operation at high speed, improving dynamic pressure opening capability of a high speed seal face under the low speed working condition, realizing non-contact stability of the seal face under the high speed working condition, reducing end face contact wear, prolonging service life and improving sealing reliability.
Description
Technical field
The invention belongs to the mechanical end face seal technical field, particularly be applicable to the shaft end seal device of the rotating machinery rotating shafts such as various compressors, pump and still, relate in particular to a kind of negative-pressure profiled groove end face mechanical sealing structure.
Background technique
Dry gas seals is a kind of non-contacting mechanical seal, because its excellent properties at aspects such as energy-saving and environmental protection, high reliability, and the first-selected sealing means when becoming gradually the direction of Development of Mechanical Seal and main equipment design.Along with the fast development of the industries such as petrochemical industry, require mechanical seal to develop to high parameter, have higher stability and reliability and longer working life.
Since the nineties in 20th century, the released one after another sealing of the end patterns such as one-way spiral groove, unidirectional herringbone spiral chute, unidirectional Y shape spiral chute, unidirectional L shaped spiral chute, unidirectional arc groove, two-way T-slot, two-way U-groove bevel, two-way tree-like groove of domestic and international sealing company take Crane John Inc. as representative, realized the non-contacting mechanical seal form, be widely used on the shaft end seal device of centrifugal compressor and the rotating shaft of pump class.In above-mentioned grooved, best with spiral fluted dynamic pressure performance, namely along with the increase of rotating speed, unseal power and fluid film rigidity increase sharply, seal face is easily opened and is formed non-contact stable operation, so that it is most widely used in present dry gas seals engineering design.
But, for common sealing grooved, owing to the increase of sealing gas film stiffness along with rotating speed increases sharply, belong to the positive pressure type trench structure, the disturbance of sealing air film easily occurs, poor anti jamming capability under high-speed working condition, cause the accelerated wear test of seal face, reduction of service life.In addition, when being applied to the equipment such as steam turbine when dry gas seals, generally need warming-up process, namely move under the low speed certain hour, and then transfer normal high speed operation to.This not only requires the stability of Dry Gas Seal under having at a high speed, and seal face can be opened smoothly when requiring low speed, to satisfy the startup running requirements of equipment.
Summary of the invention
The disturbance of sealing air film, poor anti jamming capability, easy to wear, shortcoming that working life is short easily occur under high-speed working condition in order to overcome existing malleation type groove structure, the invention provides a kind of high-speed working condition that is applied to, strengthen seal clearance stability, low speed unlatching performance is good, the minimizing end contact weares and teares, reliability is high, the negative-pressure profiled groove end face mechanical sealing structure of long service life.
Technological scheme of the present invention is:
A kind of negative-pressure profiled groove end face mechanical sealing structure, the rotating ring that comprises mechanical seal, stationary ring, one side of the end face of described rotating ring and stationary ring is that the high pressure side is the upstream, the opposite side of the end face of described rotating ring and stationary ring is that low voltage side is the downstream, it is characterized in that: have at least one end face of described rotating ring or stationary ring according to the symmetrical negative pressure grooved group of rotating center, the upstream of described negative pressure grooved group is provided with the micropore endless belt, described negative pressure grooved group is comprised of spiral deformation inclination angle micropore dynamic pressure groove and decompressing groove spaced apart, described decompressing groove is terminal near dynamic pressure groove, and the downstream of described negative pressure grooved group is provided with the ring packing dam of smooth flat.
Further, the dynamic pressure micropore that described dynamic pressure groove is arranged by a plurality of spirality forms, described dynamic pressure micropore comprises major axis and minor axis, described major axis has certain angle of inclination with end face radius by this dynamic pressure micropore center, and described dynamic pressure micropore angle of inclination diminishes to the downstream gradually along upstream, micropore district.
Further, described micropore endless belt radially is provided with a plurality of micropores.
Further, described micropore endless belt micropore hole depth scope is 10～50 μ m, and described dynamic pressure micropore ratio of long axis to short axis scope is 1 ~ 10, and the groove depth scope is 2～10 μ m, and described decompressing groove groove depth scope is 2～50 μ m.
Further, the radial width scope on described ring packing dam is 0.1～10 mm.
The micro-pore shape of micropore endless belt of the present invention can be the regular shapes such as circle, ellipse, rectangular, triangle; The micro-pore shape of dynamic pressure groove can be the regular figures such as ellipse, rectangular, trigonometric form, but obvious directivity must be arranged; Decompressing groove be shaped as the regular figures such as circle, rectangular, rhombus, arc quadrilateral.
Working principle of the present invention:
The pressure flow that the upstream high pressure produces at first enters the micropore endless belt, and micropore can receive the particle that contains in the gas, can greatly reduce entering of hard particles and cause end-face friction to damage to seal clearance.The dynamic pressure groove that is made of change inclination micropore group can produce micropore dynamic pressure and two kinds of dynamic pressure opening forces of macroscopical spiral chute dynamic pressure.Because the good dynamic pressure performance of spiral slot, when air-flow after entering dynamic pressure groove under the tangential rotating speed cutting effect, gas will flow along the Hand of spiral of dynamic pressure groove and compression, dynamic pressure groove also can form obvious dynamic pressure opening force under the low speed.When fluid after continuing to enter the decompressing groove of dynamic pressure groove end under the shear action because fluid displacement increases suddenly, pressure sharply reduces, and forms underbalance effect.Because there are a determining deviation in decompressing groove and dynamic pressure groove, decompressing groove is less to dynamic pressure groove pressure influence under the low speed.Under high-speed working condition, the high pressure that the dynamic pressure groove dynamic pressure effect forms the tangentially extension of direction that distributes is subject to the decompressing groove restriction and can not continues to increase, even negative growth appears, the dynamic pressure opening force that dynamic pressure groove forms when namely reaching certain speed can obviously not increase even reduce again.On the other hand, make the radial fluid resistance reduce to cause sealing the upstream high pressure after micropore in the dynamic pressure groove tilts under the speed shear action and move and form the dynamic pressure opening force to low voltage side, its power is decided by pore size and angle of inclination.During low speed in the dynamic pressure groove dynamic pressure opening force of micropore not obvious, take the dynamic pressure opening force of dynamic pressure groove macroscopic view Spiral distribution Characteristics creation as main.When reaching certain speed, the dynamic pressure effect of micropore will become obvious in the dynamic pressure groove.The micropore of dynamic pressure groove adopts and becomes the inclination angle design, and dynamic pressure groove front end micropore inclination angle is larger, and along with dynamic pressure groove Hand of spiral micropore inclination angle reduces gradually, the terminal micropore of dynamic pressure groove inclination angle is minimum.The micropore dynamic pressure effect of dynamic pressure groove front end is strong, and be not subjected to the impact of underbalance effect away from decompressing groove, the dynamic pressure opening force that produces can constantly increase with the increase of speed, there is not a dynamic pressure effect and the terminal micropore of dynamic pressure groove inclination angle is little, and the dynamic pressure opening force of differing tilt angles micropore keeps dynamic pressure to open the stable of performance with the difference of gaining in strength of speed when being conducive to velocity variations.Therefore, spiral deformation inclination angle micropore dynamic pressure groove and decompressing groove acting in conjunction can be opened performance so that seal face all has good dynamic pressure under high speed and low speed, and the sealing gas film stiffness under can controlling at a high speed.
Micropore endless belt and the dynamic pressure groove of sealing structure are made of micropore, because the hole depth of micropore and the seal clearance size mutation effect of the larger formation of aperture ratio are so that flow to the γ-ray emission eddy current of micropore, resistance to motion and the energy loss of gas have been increased, thereby enlarge markedly the damping of seal face air film, reduce the sealing vibration, strengthen the Ability of Resisting Disturbance of seal face, obviously improved the seal clearance dynamic stability.
During seal operation, dynamic pressure groove provides micropore dynamic pressure and two kinds of dynamic pressure opening forces of macroscopical Spiral distribution dynamic pressure, decompressing groove can balance or is reduced the dynamic pressure opening force of macroscopical Spiral distribution when high speed, thereby can realize that high speed and low speed lower seal end face all have obvious dynamic pressure opening force, and can suppress the too fast increase of at a high speed lower gas film stiffness.The microcellular structure of end face can enlarge markedly gas film damping, reduces the sealing vibration and prevent the abrasion of particles ability.Under high-speed condition, the antijamming capability of Effective Raise sealing air film, stability and the servo-actuated property of assurance seal face reduce the contact wear between end face, realize stability and the high reliability of high speed end face seal.
Beneficial effect of the present invention is mainly manifested in: dynamic pressure groove and the decompressing groove Combination Design of uniqueness on l, the seal face, strengthened the antijamming capability that is sealed in when running up, and improve the dynamic pressure of high-speed sealing end face under the low speed operating mode and opened ability; 2, anti-dry seal is disturbed the enhancing of ability, has further realized the non-contact stability under the high-speed working condition of seal face, has reduced the end contact wearing and tearing, has prolonged working life; 3, the surface micro-pores structural reinforcing the anti-abrasion of particles ability of seal face under at a high speed, improved the reliability of sealing.
Description of drawings
Fig. 1 is end-face structure schematic representation of the present invention.
Fig. 2 is the enlarged view of A part among Fig. 1.
Fig. 3 is longitudinal sectional view of the present invention.
Embodiment
With reference to Fig. 1-3, a kind of negative-pressure profiled groove end face mechanical sealing structure, the rotating ring 5 that comprises mechanical seal, stationary ring 6, one side of the end face of described rotating ring 5 and stationary ring 6 is that the high pressure side is the upstream, the opposite side of the end face of described rotating ring 5 and stationary ring 6 is that low voltage side is the downstream, have on described rotating ring 5 end faces according to the symmetrical negative pressure grooved group of rotating center, the upstream of described negative pressure grooved group is provided with micropore endless belt 1, described negative pressure grooved group is comprised of spiral deformation inclination angle micropore dynamic pressure groove 2 and decompressing groove 3 spaced apart, described decompressing groove 3 is near dynamic pressure groove 2 ends, and the downstream of described negative pressure grooved group is provided with the ring packing dam 4 of smooth flat.
The dynamic pressure micropore 21 that described dynamic pressure groove 2 is arranged by a plurality of spirality forms, described dynamic pressure micropore 21 comprises major axis and minor axis, described major axis has certain angle of inclination with end face radius by this dynamic pressure micropore center, and described dynamic pressure micropore 21 angles of inclination diminish to the downstream gradually along upstream, micropore district.
Described micropore endless belt 1 radially is provided with a plurality of micropores.
Described micropore endless belt 1 micropore hole depth scope is 10～50 μ m, and described dynamic pressure micropore ratio of long axis to short axis scope is 1 ~ 10, and the groove depth scope is 2～10 μ m, and described decompressing groove 3 groove depth scopes are 2～50 μ m.
The radial width scope on described ring packing dam 4 is 0.1～10 mm.
Working principle of the present invention:
The pressure flow that the upstream high pressure produces at first enters micropore endless belt 1, and micropore can receive the particle that contains in the gas, can greatly reduce entering of hard particles and cause end-face friction to damage to seal clearance.The dynamic pressure groove 2 that is made of change inclination micropore group can produce micropore dynamic pressure and two kinds of dynamic pressure opening forces of macroscopical spiral chute dynamic pressure.Because the good dynamic pressure performance of spiral slot, when air-flow after entering dynamic pressure groove 2 under the tangential rotating speed cutting effect, gas will flow along the Hand of spiral of dynamic pressure groove 2 and compression, dynamic pressure groove 2 also can form obvious dynamic pressure opening force under the low speed.After fluid was continuing under the shear action to enter the decompressing groove 3 of dynamic pressure groove end, because fluid displacement increases suddenly, pressure sharply reduced, and formed underbalance effect.Because there is a determining deviation in decompressing groove 3 with dynamic pressure groove 2,3 pairs of dynamic pressure groove 2 pressure influences of decompressing groove are less under the low speed.Under high-speed working condition, the high pressure that dynamic pressure groove 2 dynamic pressure effects form the tangentially extension of direction that distributes is subject to decompressing groove 3 restrictions and can not continues to increase, even negative growth appears, the dynamic pressure opening force that dynamic pressure groove 2 forms when namely reaching certain speed can obviously not increase even reduce again.On the other hand, make the radial fluid resistance reduce to cause sealing the upstream high pressure after micropore in the dynamic pressure groove 2 tilts under the speed shear action and move and form the dynamic pressure opening force to low voltage side, its power is decided by pore size and angle of inclination.During low speed in the dynamic pressure groove dynamic pressure opening force of micropore not obvious, take the dynamic pressure opening force of dynamic pressure groove 2 macroscopical Spiral distribution Characteristics creations as main.When reaching certain speed, the dynamic pressure effect of micropore will become obvious in the dynamic pressure groove.The micropore of dynamic pressure groove 2 adopts and becomes the inclination angle design, and dynamic pressure groove 2 front end dynamic pressure micropores 21 inclination angles are larger, and along with dynamic pressure groove 2 Hand of spiral micropore inclination angles reduce gradually, dynamic pressure groove 2 terminal dynamic pressure micropores 22 inclination angles are minimum.Dynamic pressure groove 2 front end dynamic pressure micropores 21 dynamic pressure effects are strong, and be not subjected to the impact of underbalance effect away from decompressing groove, the dynamic pressure opening force that produces can constantly increase with the increase of speed, there is not a dynamic pressure effect and dynamic pressure groove 2 terminal dynamic pressure micropores 22 inclination angles are little, and the dynamic pressure opening force of differing tilt angles micropore keeps dynamic pressure to open the stable of performance with the difference of gaining in strength of speed when being conducive to velocity variations.Therefore, spiral deformation inclination angle micropore dynamic pressure groove 2 and decompressing groove 3 actings in conjunction can be opened performance so that seal face all has good dynamic pressure under high speed and low speed, and the sealing gas film stiffness under can controlling at a high speed.
The micropore endless belt 1 of sealing structure and dynamic pressure groove 2 are made of micropore, because the hole depth of micropore and the seal clearance size mutation effect of the larger formation of aperture ratio are so that flow to the γ-ray emission eddy current of micropore, resistance to motion and the energy loss of gas have been increased, thereby enlarge markedly the damping of seal face air film, reduce the sealing vibration, strengthen the Ability of Resisting Disturbance of seal face, obviously improved the seal clearance dynamic stability.
The sealing structure can be controlled sealing rigidity and increase damping, improve the sealing dynamic characteristic, make antijamming capability or the performance stable and under high-speed condition of sealing be better than the general fluid hydrodynamic mechanical seal, and can satisfy low voltage starting and run up to the requirement of dynamic pressure opening force, and have the anti-particle ability of good micropore, the sealability of sealing and reliability are improved.
The described content of this specification embodiment only is enumerating the way of realization of inventive concept; protection scope of the present invention should not be regarded as only limiting to the concrete form that embodiment states, protection scope of the present invention also reaches in those skilled in the art conceives the equivalent technologies means that can expect according to the present invention.
Claims (5)
1. negative-pressure profiled groove end face mechanical sealing structure, the rotating ring that comprises mechanical seal, stationary ring, one side of the end face of described rotating ring and stationary ring is that the high pressure side is the upstream, the opposite side of the end face of described rotating ring and stationary ring is that low voltage side is the downstream, it is characterized in that: have at least one end face of described rotating ring or stationary ring according to the symmetrical negative pressure grooved group of rotating center, the upstream of described negative pressure grooved group is provided with the micropore endless belt, described negative pressure grooved group is comprised of spiral deformation inclination angle micropore dynamic pressure groove and decompressing groove spaced apart, described decompressing groove is terminal near dynamic pressure groove, and the downstream of described negative pressure grooved group is provided with the ring packing dam of smooth flat.
2. a kind of negative-pressure profiled groove end face mechanical sealing structure according to claim 1, it is characterized in that: the dynamic pressure micropore that described dynamic pressure groove is arranged by a plurality of spirality forms, described dynamic pressure micropore comprises major axis and minor axis, described major axis has certain angle of inclination with end face radius by this dynamic pressure micropore center, and described dynamic pressure micropore angle of inclination diminishes to the downstream gradually along upstream, micropore district.
3. a kind of negative-pressure profiled groove end face mechanical sealing structure according to claim 1 and 2, it is characterized in that: described micropore endless belt radially is provided with a plurality of micropores.
4. a kind of negative-pressure profiled groove end face mechanical sealing structure according to claim 3, it is characterized in that: described micropore endless belt micropore hole depth scope is 10～50 μ m, described dynamic pressure micropore ratio of long axis to short axis scope is 1 ~ 10, dynamic pressure groove depth scope is 2～10 μ m, and described decompressing groove groove depth scope is 2～50 μ m.
5. a kind of negative-pressure profiled groove end face mechanical sealing structure according to claim 4, it is characterized in that: the radial width scope on described ring packing dam is 0.1～10mm.
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| Application Number | Priority Date | Filing Date | Title |
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| CN2010105830829A CN102022542B (en) | 2010-12-11 | 2010-12-11 | Negative pressure groove end face mechanical seal structure |
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| Application Number | Priority Date | Filing Date | Title |
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| CN2010105830829A CN102022542B (en) | 2010-12-11 | 2010-12-11 | Negative pressure groove end face mechanical seal structure |
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| CN102022542A CN102022542A (en) | 2011-04-20 |
| CN102022542B true CN102022542B (en) | 2013-04-03 |
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| CN103732958B (en) * | 2011-09-10 | 2016-09-21 | 伊格尔工业股份有限公司 | Slide unit |
| JP6683630B2 (en) * | 2015-02-14 | 2020-04-22 | イーグル工業株式会社 | Sliding parts |
| US10036474B2 (en) | 2015-09-23 | 2018-07-31 | Hamilton Sundstrand Corporation | Vented lift off seal assemblies |
| CN106015572B (en) * | 2016-07-27 | 2018-05-08 | 浙江工业大学 | Bi-directionally rotatable cross-scale slotted hole combined end face mechanical sealing structure |
| US11708911B2 (en) * | 2017-10-03 | 2023-07-25 | Eagle Industry Co., Ltd. | Sliding component |
| CN111981126B (en) * | 2019-05-23 | 2022-04-19 | 浙江大学宁波理工学院 | Compound sealed end surface structure of three fens of collection micropores and ladder spiral groove |
| CN110578801A (en) * | 2019-09-29 | 2019-12-17 | 西安石油大学 | Anchor-shaped dry gas sealing device |
| US11994216B2 (en) | 2020-04-07 | 2024-05-28 | Eagle Industry Co., Ltd. | Sliding component |
| CN111473115A (en) * | 2020-05-13 | 2020-07-31 | 清华大学 | Mechanical seal end face structure with auxiliary weir area |
| CN111473116A (en) * | 2020-05-25 | 2020-07-31 | 清华大学 | Upstream pumping microtextured mechanical seal end face structure |
| CN113028065B (en) * | 2021-03-23 | 2023-08-04 | 浙大宁波理工学院 | Sealing device |
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|---|---|---|---|---|
| EP0601821A1 (en) * | 1992-12-11 | 1994-06-15 | Nippon Pillar Packing Co., Ltd. | Non-contacting shaft sealing device |
| CN2432391Y (en) * | 2000-06-13 | 2001-05-30 | 石油大学(华东) | Linear fluid dynamic channel upstream pumping machine seal |
| CN1828098A (en) * | 2006-01-27 | 2006-09-06 | 浙江工业大学 | Non-contact mechanical end face sealing structure |
| CN201916486U (en) * | 2010-12-11 | 2011-08-03 | 浙江工业大学 | Negative-pressure profiled groove end face mechanical sealing structure |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH10281300A (en) * | 1997-04-01 | 1998-10-23 | Mitsubishi Heavy Ind Ltd | Mechanical seal device |
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2010
- 2010-12-11 CN CN2010105830829A patent/CN102022542B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0601821A1 (en) * | 1992-12-11 | 1994-06-15 | Nippon Pillar Packing Co., Ltd. | Non-contacting shaft sealing device |
| CN2432391Y (en) * | 2000-06-13 | 2001-05-30 | 石油大学(华东) | Linear fluid dynamic channel upstream pumping machine seal |
| CN1828098A (en) * | 2006-01-27 | 2006-09-06 | 浙江工业大学 | Non-contact mechanical end face sealing structure |
| CN201916486U (en) * | 2010-12-11 | 2011-08-03 | 浙江工业大学 | Negative-pressure profiled groove end face mechanical sealing structure |
Non-Patent Citations (1)
| Title |
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| JP特开平10-281300A 1998.10.23 |
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Effective date of registration: 20191225 Address after: 314415 within huangwan town government, Jiaxing City, Zhejiang Province Patentee after: Haining huangwan town Asset Management Co.,Ltd. Address before: 510000 unit 2414-2416, building, No. five, No. 371, Tianhe District, Guangdong, China Patentee before: GUANGDONG GAOHANG INTELLECTUAL PROPERTY OPERATION Co.,Ltd. Effective date of registration: 20191225 Address after: 510000 unit 2414-2416, building, No. five, No. 371, Tianhe District, Guangdong, China Patentee after: GUANGDONG GAOHANG INTELLECTUAL PROPERTY OPERATION Co.,Ltd. Address before: Hangzhou City, Zhejiang province 310014 City Zhaohui District Six Patentee before: Zhejiang University of Technology |
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