WO2004053364A1 - Gleitringdichtungsanordnung - Google Patents
Gleitringdichtungsanordnung Download PDFInfo
- Publication number
- WO2004053364A1 WO2004053364A1 PCT/EP2003/011500 EP0311500W WO2004053364A1 WO 2004053364 A1 WO2004053364 A1 WO 2004053364A1 EP 0311500 W EP0311500 W EP 0311500W WO 2004053364 A1 WO2004053364 A1 WO 2004053364A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- bellows
- mechanical seal
- axial
- seal arrangement
- ring
- Prior art date
Links
Classifications
-
- 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
- F16J15/36—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member connected by a diaphragm or bellow to the other member
- F16J15/363—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member connected by a diaphragm or bellow to the other member the diaphragm or bellow being made of metal
- F16J15/366—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member connected by a diaphragm or bellow to the other member the diaphragm or bellow being made of metal and comprising vibration-damping means
Definitions
- the invention relates to a mechanical seal arrangement according to the preamble of claim 1.
- the invention relates in particular to a mechanical seal arrangement with a bellows made of metallic material as a pretensioning and secondary sealing means.
- the bellows can be subjected to considerable vibrating and thermal stresses, which can cause damage to the bellows itself (cracking) and can also have a detrimental effect on the mutual alignment of the slide rings and on the conditions in the area between the interacting sealing surfaces of the slide rings.
- bellows with a comparatively large axial length are desired, since they create a good flexibility for the compensation of thermal expansion and, moreover, allow assembly inaccuracies to be handled well.
- dampers made of, for example, structured sheet metal strips have been proposed, which are arranged between the bellows and a surface of a component of the mechanical seal arrangement surrounding it.
- This vibration-damping measure results in undesirable surface damage to the bellows.
- the invention has for its object to provide a mechanical seal assembly of the type mentioned with a bellows assembly as a preload and secondary sealant in which the harmful effects of vibrations on the performance of a mechanical seal pair and on the life of the bellows assembly itself are completely or at least largely eliminated.
- the invention is intended to provide an improved mechanical seal arrangement with a bellows arrangement of enlarged axial dimension for use in steam-powered systems.
- a mechanical seal arrangement with at least one pair of interacting slide rings, one of which is provided for mounting on a stationary component and the other for rotating together with a rotating component, and one of which is arranged to be axially movable and against the other slide ring by means of a
- the bellows arrangement is axially preloaded with a certain axial prestressing force, the bellows arrangement comprising a first bellows supported on one end on the relevant slide ring and on the other end on an annular bellows supported axially movably relative to the relevant component and a second bellows supported on one end on the divider element and at the other end on the relevant component , an axial operating vibration force being superimposed during operation of the determined axial pretensioning force.
- the divider element is movable against an axial friction force relative to the component in question, which is at least substantially equal to a specific maximum operating vibration force. According to a preferred development of the invention, this can be defined by a specific axial deflection of the first bellows.
- the measures according to the invention prevent the vibrations from being transmitted to the second bellows, so that only the first bellows is exposed to vibrational stresses.
- the vibrations in their harmful effects easier to handle than with a large bellows length, in particular in that the vibration system consisting of the first bellows and the interacting slide ring can be adjusted in its natural frequency behavior in such a way that harmful resonance phenomena are avoided.
- the advantages of long bellows in terms of compensating thermal expansion and compensating for inaccuracy in assembly are fully retained.
- the divider element has a stabilizing effect by effectively preventing the bellows from buckling.
- the drawing shows a longitudinally cut, partially schematic view of a mechanical seal arrangement according to an embodiment of the invention.
- the invention preferably offers advantages for sealing gaseous media, including vapors, in an environment in which high thermal loads and high rotational speeds are present, the invention is not limited to this.
- the invention can in particular also be used advantageously in connection with non-gaseous media.
- the mechanical seal arrangement comprises a stationary component 1, for example assembly goggles or the like, with the aid of which the mechanical seal arrangement can be mounted in a bore of a housing, not shown, of a device, for example a turbine.
- the stationary component 1 can also be the housing of the device.
- a rotating component 2, for example a turbine shaft, is passed through a bore in the stationary component 1.
- the mechanical seal arrangement further comprises a pair of interacting slide rings 4, 5, one of which, the slide ring 4, is secured against rotation, but is axially movably mounted on the stationary component 1.
- Pins 9 protrude axially from the stationary component 1, which engage in the axial recesses 10 of the sliding ring 4, so that the sliding ring 4 is prevented on the one hand from rotating relative to the stationary component 1, but on the other hand can perform an axial movement.
- the other slide ring 5 is provided for common rotation with the rotating component 2 and is therefore connected to transmit torque.
- the interacting slide rings 4, 5 have mutually opposite sealing surfaces 6, 7, between which a sealing gap is formed during operation in order to seal a space on the outside against a space on the inside of the slide rings 4, 5.
- structures capable of conveying can be introduced which open to the space around the outside and cause the medium present in the area between the sealing surfaces 6, 7 is pumped to support the formation of a sealing gap. It goes without saying that when the medium to be pumped is in contact with the inner circumference of the pair of slide rings, the structures with a positive effect on the conveyance start from the inner circumference of the relevant slide ring.
- suitable structures with effective support reference can be made to BURGMANN gas-lubricated mechanical seals, Disverlag 1997, pages 16 ff.
- a bellows arrangement bearing the general reference number 11 is provided in order to apply a suitable pretensioning force to the stationary slide ring 4 against the rotating slide ring 5, so that the sealing surfaces 6, 7 are held in sealing engagement with one another in the absence or insufficient sealing gap formation. Furthermore, the bellows arrangement 11 forms a secondary seal for sealing the sliding ring 4 with respect to the stationary component 1. Although other types of bellows can be used for the bellows arrangement 11, it is preferably formed from a metal bellows, which with further details in BURGMANN, Lexicon of mechanical seal, Disverlag 1988, page 153, so that reference can be made here.
- the bellows arrangement 11 has an enlarged axial length, so that it is suitable for being able to absorb correspondingly large thermal expansions, such as can occur during operation of the mechanical seal arrangement.
- the bellows arrangement 11 is axially divided by a dividing ring 12 into a first bellows 13 and a second bellows 14.
- the first bellows 13 is supported with one axial end on the slide ring 4 and with its other axial end on the divider ring 12, while the second bellows 14 is supported with one axial end on the divider ring 12 and with its other axial end on a mounting ring 15 which in a suitable manner, e.g. can be mounted on the stationary component 1 by means of a screw connection, as indicated at 16.
- the second bellows 14 could also be supported directly on the stationary component 1.
- the tight connection of the bellows 13, 14 to the components on which they are supported at the ends can be achieved by welding or other suitable connection techniques.
- the dividing ring 12 has a dimensionally stable, disc-shaped design and, in its outer circumference, contains a circumferentially extending groove or holder in which an annular friction element 17 is arranged.
- the annular friction element 17 can be a spring ring or a ring made of a resilient material, e.g. an O-ring.
- Preferred designs of spring washers are those in which the spring windings are placed in such a way that a spring action is obtained not only in the longitudinal but also in the radial direction. Such spring washers can be obtained under the name BAL SEAL-FEDERN from Plasticellmaschines GmbH, Radolfzell, Germany.
- the radial force with which the friction element 17 is prestressed against the circumferential surface 18 is selected such that an axial frictional force arises which is sufficiently high that, under normal operating conditions, the dividing ring 12 is exerted by the first and second bellows 13, 14 axial biasing forces remains in the axial position into which the divider ring 12 has been displaced due to thermal expansion of the bellows arrangement 11 or due to other macro movements.
- the frictional force causes the divider ring 12 to remain immobile in the event of micro-vibration movements in the first bellows 13 during operation, to which the bellows 13 can be excited when the rotating component 2 rotates. These micro-oscillatory movements are thereby prevented from being forwarded to the second bellows 14.
- micro-vibration movements cause axial operating vibration forces in the first bellows 13 in accordance with its spring constants, which overlap the specific static preload force which is applied by the bellows arrangement 11.
- the frictional force under which the dividing ring 12 is held in its axial position is to be selected such that it is an operating vibration force caused by the micro-oscillatory movements with a maximum axial deflection of the first bellows 13 of not more than + 0.5 mm, preferably ⁇ 0.4 mm, most preferably ⁇ 0.3 mm.
- the first bellows 13 and the second bellows 14 can have the same or different axial dimensions. In some applications it is preferred that the axial dimension of the first bellows 13 is smaller than that of the second bellows 14.
- the first bellows 13 and the associated slide ring 4 represent an oscillation system with a certain natural frequency.
- the mass of the slide ring 4 as well as a possibly added pressure ring (not shown) and the spring constant of the first bellows 13 should be matched to the estimated highest operating speed of the rotating component so that the resulting excitation frequency always remains below the natural frequency of the vibration system.
- the bellows arrangement is assigned to the rotationally fixed slide ring.
- it could also be associated with the rotating slide ring.
- the friction element of the partial ring can interact with a rotating peripheral surface, for example the surface of the rotating component.
- a tandem or twin pairing can be provided.
- a divider ring with a separate friction element could alternatively be replaced by a divider ring made of a suitable tribologically active material.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mechanical Sealing (AREA)
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AU2003283274A AU2003283274A1 (en) | 2002-12-06 | 2003-10-16 | Slide ring seal assembly |
EP03775195A EP1567794A1 (de) | 2002-12-06 | 2003-10-16 | Gleitringdichtungsanordnung |
US10/537,060 US20060232015A1 (en) | 2002-12-06 | 2003-10-16 | Slide ring seal assembly |
JP2004557866A JP2006509164A (ja) | 2002-12-06 | 2003-10-16 | スライドリングシールアセンブリ |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE20218878.7 | 2002-12-06 | ||
DE20218878U DE20218878U1 (de) | 2002-12-06 | 2002-12-06 | Gleitringdichtungsanordnung |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2004053364A1 true WO2004053364A1 (de) | 2004-06-24 |
Family
ID=7977681
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2003/011500 WO2004053364A1 (de) | 2002-12-06 | 2003-10-16 | Gleitringdichtungsanordnung |
Country Status (6)
Country | Link |
---|---|
US (1) | US20060232015A1 (de) |
EP (1) | EP1567794A1 (de) |
JP (1) | JP2006509164A (de) |
AU (1) | AU2003283274A1 (de) |
DE (1) | DE20218878U1 (de) |
WO (1) | WO2004053364A1 (de) |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE202007016406U1 (de) * | 2007-11-23 | 2008-01-31 | Burgmann Industries Gmbh & Co. Kg | Vorrichtung zur Drehsicherung eines axial beweglich an einem Montagebauteil gehaltenen Gleitringes einer Gleitringdichtungsanordnung |
CN103282621B (zh) * | 2011-01-07 | 2016-05-25 | 博格华纳公司 | 用于致动轴的弹簧偏置的密封结构和方法 |
CN103403321A (zh) * | 2011-03-17 | 2013-11-20 | 博格华纳公司 | 用于致动轴的气体压力偏置的密封方法 |
GB2511476A (en) * | 2012-12-07 | 2014-09-10 | Thomas Andreas Guenther | Device and system for hydrocarbon conversion |
CN109296752B (zh) * | 2018-11-15 | 2024-02-27 | 广州维港环保科技有限公司 | 一种回转圆筒体设备密封装置 |
CN112081923B (zh) * | 2020-09-01 | 2022-05-20 | 扬州船用电子仪器研究所(中国船舶重工集团公司第七二三研究所) | 一种机械密封组件结构 |
CN112879570B (zh) * | 2021-04-19 | 2022-08-26 | 重庆胤合石油化工机械制造有限公司 | 一种弹簧机械密封补偿环组件 |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB1098235A (en) * | 1965-09-07 | 1968-01-10 | Sealol | Improvements in mounting devices |
US5983738A (en) * | 1996-03-22 | 1999-11-16 | Mouvex | Eccentric sealed rotary drive device, particularly for a positive displacement pump |
FR2787851A1 (fr) * | 1998-12-24 | 2000-06-30 | Snecma | Amortisseur de joint dynamique |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB601296A (en) | 1945-11-24 | 1948-05-03 | Crane Packing Ltd | Improvements in and relating to sealing devices between relatively rotating members |
US3515394A (en) | 1964-06-05 | 1970-06-02 | Sealol | Vibration damping means for resilient convoluted members |
US3336034A (en) | 1964-10-27 | 1967-08-15 | Robert J Smith | Force adaptive dynamic face seal |
US3318604A (en) | 1964-12-31 | 1967-05-09 | Borg Warner | Self-adjusting mechanical seal with bellows control |
FI71824C (fi) * | 1985-04-12 | 1987-02-09 | Safematic Ltd Oy | Mekanisk taetning. |
GB2208412B (en) * | 1987-06-05 | 1991-01-23 | Eg & G Ltd | Bellows seal arrangement |
-
2002
- 2002-12-06 DE DE20218878U patent/DE20218878U1/de not_active Expired - Lifetime
-
2003
- 2003-10-16 US US10/537,060 patent/US20060232015A1/en not_active Abandoned
- 2003-10-16 WO PCT/EP2003/011500 patent/WO2004053364A1/de active Application Filing
- 2003-10-16 EP EP03775195A patent/EP1567794A1/de not_active Withdrawn
- 2003-10-16 JP JP2004557866A patent/JP2006509164A/ja active Pending
- 2003-10-16 AU AU2003283274A patent/AU2003283274A1/en not_active Abandoned
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB1098235A (en) * | 1965-09-07 | 1968-01-10 | Sealol | Improvements in mounting devices |
US5983738A (en) * | 1996-03-22 | 1999-11-16 | Mouvex | Eccentric sealed rotary drive device, particularly for a positive displacement pump |
FR2787851A1 (fr) * | 1998-12-24 | 2000-06-30 | Snecma | Amortisseur de joint dynamique |
Non-Patent Citations (2)
Title |
---|
"BURGMANN gaseschmierte Gleitringdichtungen", 1997, SELBSTVERLAG, pages: 16 |
"BURGMANN Lexikon der Gleitringdichtung", 1988, SELBSTVERLAG, pages: 153 |
Also Published As
Publication number | Publication date |
---|---|
US20060232015A1 (en) | 2006-10-19 |
EP1567794A1 (de) | 2005-08-31 |
AU2003283274A1 (en) | 2004-06-30 |
JP2006509164A (ja) | 2006-03-16 |
DE20218878U1 (de) | 2003-02-13 |
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