WO2012022615A1 - Palier, en particulier pour une utilisation sous l'eau - Google Patents

Palier, en particulier pour une utilisation sous l'eau Download PDF

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Publication number
WO2012022615A1
WO2012022615A1 PCT/EP2011/063328 EP2011063328W WO2012022615A1 WO 2012022615 A1 WO2012022615 A1 WO 2012022615A1 EP 2011063328 W EP2011063328 W EP 2011063328W WO 2012022615 A1 WO2012022615 A1 WO 2012022615A1
Authority
WO
WIPO (PCT)
Prior art keywords
bore
bearing
pressure compensation
compensation element
piston
Prior art date
Application number
PCT/EP2011/063328
Other languages
German (de)
English (en)
Inventor
Wolfgang Braun
Original Assignee
Schaeffler Technologies Gmbh & Co. Kg
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Schaeffler Technologies Gmbh & Co. Kg filed Critical Schaeffler Technologies Gmbh & Co. Kg
Publication of WO2012022615A1 publication Critical patent/WO2012022615A1/fr

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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
    • F16C33/664—Retaining the liquid in or near the bearing
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/52—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/768—Sealings of ball or roller bearings between relatively stationary parts, i.e. static seals
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members

Definitions

  • the invention relates to a bearing according to claim 1, in particular a bearing for use in a liquid environment, especially for use under water.
  • the invention is explained in more detail in the following for the case that the liquid environment of the camp is water, in particular seawater at a depth of about 100 meters. It is understood that the invention is to be transferred to other liquid environments, in particular liquids other than seawater or other static pressures.
  • the sealing lip of the seal In order to prevent ingress of water into the bearing, the sealing lip of the seal is kept pressed under a high mechanical stress against the mounted shaft or one of the two bearing rings. During operation of the bearing then occur high mechanical friction losses on the sealing lip, so that the seal fails at short notice.
  • Special seals designed for high pressures which comprise several chambers, in each of which an intermediate pressure is set, are complex and require a large amount of space. Furthermore, the chambers gradually fail during prolonged operation.
  • a pressure compensation element is provided, which is arranged via a line in a bore in one of the two bearing rings outside the bore.
  • the pressure compensation element comprises a rolling diaphragm which is arranged at one end of a carrier element, which merges into the line.
  • the storage room is filled with air, and the warehouse is operated with air as ambient medium.
  • the rolling diaphragm is impermeable to air, but permeable to water vapor, which can escape from the storage room to the storage environment.
  • the rolling diaphragm expands as the temperature of the storage room increases relative to the temperature of the environment of the bearing.
  • the rolling diaphragm takes up a considerable space outside of the bearing rings.
  • DE 202 13 600 U1 describes a bearing with two bearing rings and a seal, which enclose a storage space, wherein between the bearing cavities and an environment of the bearing a bore is provided, which is completed with a membrane of a semi-permeable material that allows moisture from the storage room in the vicinity of the camp leak, but does not allow moisture to enter the storage room.
  • the interior of the bearing is filled with a gas, ie humid air, and the storage environment consists of moist air.
  • DE 199 35 014 B4 describes a bearing with two bearing rings and a seal, which form a storage space, wherein in one of the bearing rings, a bore is provided, which can be closed or opened by means of an actuatable sealing element to discharge air from the storage space.
  • This object is achieved in that the storage space is filled with a liquid, and that the pressure compensation element is movably disposed in the bore.
  • the liquid in the storage space together with the fluid of the storage environment causes only a slight movement of the pressure compensation element when the pressure is increased.
  • the pressure compensation element is in contact with both the liquid in the Bearing inside as well as with the liquid of the storage environment.
  • the movement of the pressure compensation element ensures that the same pressure occurs outside of the bearing and in the storage space, so that the seal of the bearing is only slightly loaded.
  • An estimate shows that for a volume of about 1 liter for the storeroom, which is filled with a lubricating oil, for a camp that is operated at a depth of about 100 meters under water, a displacement of the pressure compensation element of about some Millimeters may be sufficient to compensate for the pressure balance between the storage room and the water of the storage environment. Due to the fact that this is not required deformation of the pressure compensation element, it is possible to receive the pressure compensation element on or in the bore itself displaceable, so that the bearing can be designed with the pressure compensation element substantially space neutral.
  • the movable arrangement of the pressure compensation element in the bore allows the pressure equalization by the movement of the pressure compensation element, which is guided and received in the bore, in particular not substantially emerges from the bore and, for example, completely absorbed in the bore.
  • the sealing of the storage space is ensured with respect to the environment of the bearing;
  • the pressure compensation element with the wall of the bore form an additional seal;
  • the pressure compensation element may have sealing lips which bear against the wall of the bore and which are carried along with the pressure compensation element.
  • the pressure compensation element comprises a piston, wherein the piston is fastened by means of a sealing bellows to the bore.
  • the piston is the movably guided in the bore part of the pressure compensation element.
  • the piston has a distance from the wall of the bore for easy displaceability.
  • the sealing bellows is attached both to the piston and to the wall of the bore. consolidates and seals the storage room from the environment of the warehouse.
  • the concertina-like sealing bellows made of an elastic material such as a plastic allows movement of the piston in the bore.
  • the piston is designed as a solid solid component, in particular as a solid cylinder.
  • the weight of the solid component rests on the closed storage space and causes a constant slight overpressure of the storage space relative to the storage environment.
  • the weight of the solid part and the arrangement of the bore in the direction of gravity allows adjusting the pressure prevailing in the storage space pressure; This pressure can be set before the assembly of the bearing, so for example under atmospheric conditions, as an overpressure, wherein the excess pressure is such that it corresponds to the hydrostatic pressure in the depth of the water in which the bearing should be mounted.
  • the pressure compensation element is then mechanically relieved and is located within the bore, for example in a central position, between the ends of the bore in order to respond to pressure fluctuations can.
  • the overpressure that can be set by the weight of the solid component or the angle of the bore relative to the direction of gravity may also be such that it is slightly greater than the hydrostatic pressure corresponding to the intended depth.
  • the bearing in the mounted position has a slight overpressure in the storage space, so that in case of leakage of the seal in any case ensures that no polluted ambient water penetrates into the camp.
  • the seals are preferably designed as a double lip seal, which can permanently absorb a slight overpressure relative to the environment.
  • the liquid in the storage space comprises a lubricating oil, in particular a biodegradable lubricating oil.
  • the Lubricating oil then causes lubrication of the sealed by the pressure compensation element bearing in addition to the pressure compensation.
  • the lubricating oil can be, for example, a biodegradable vegetable oil, which causes only minor environmental damage in the event of leakage.
  • the storage space filling liquid can be acted upon in the storage room with an overpressure;
  • the overpressure can be adjusted so that the overpressure corresponds to the expected in the intended depth of hydrostatic pressure, so that in the intended depth the pressure compensation element no significant pressure difference between the storage room and the surroundings of the warehouse.
  • the overpressure can be adjusted, for example, by a weight of the piston or by a spring element and, if necessary, tracked, the spring element acting on the pressure compensation element.
  • the bore, within which the pressure compensation element is arranged, may be provided in one of the bearing rings of the bearing; In particular, a plurality of bores can be provided, each with a pressure compensation element. It is understood in this case that the bore can also enforce a bearing seat on which the bore having bearing ring is arranged. Also, multiple pressure compensation elements can be provided within a single bore.
  • FIG. 1 a shows a sectioned schematic view of an embodiment of a bearing according to the invention, before assembly, at atmospheric pressure
  • FIG. 1 b shows an enlarged detail of FIG. 1 a
  • Fig. 2a shows a sectional schematic view of the embodiment of Fig. 1 a and 1 b after assembly, with water as the surrounding medium, and
  • Fig. 2b shows an enlarged detail of Fig. 2a.
  • Fig. 1a shows a bearing comprising as bearing rings a two-part inner ring 1, a one-piece outer ring 2, two rows of rolling elements 3 and two seals 4, 5 on both sides of the bearing rings 1, 2.
  • the seals 4, 5 form with the bearing rings 1, 2 a storage room. 6
  • a pressure compensation element 8 is provided, which closes the bore 7.
  • the bearing rings 1, 2 and the seals 4, 5 form the closed storage space 6, which is closed in the region of the bore 7 by the pressure compensation element 8.
  • the completed storage space 6 is filled with a liquid 9, in the present embodiment with a biodegradable lubricating oil.
  • the pressure compensation element 8 is shown enlarged in Fig. 1 b.
  • the pressure compensation element 8 comprises a piston 10, which is designed as a unilaterally open, substantially dimensionally stable hollow cylinder, wherein the hollow cylinder maintains a distance from the wall of the bore 7, so that the piston 10 is slidably received within the bore 7.
  • the piston 10 of the pressure compensation element 8 is thus arranged to be movable in the bore 7.
  • the piston 10 is fastened by means of a sealing bellows 1 1 to the wall of the bore 7, so that the unit of the piston 10 and the sealing bellows 1 1 prevents penetration of the medium of the environment of the bearing, ie seawater, into the storage space 6.
  • the sealing bellows 1 1 is attached to a first peripheral edge at the open end of the hollow cylindrical piston 10 and with a second peripheral edge at a stage of the bore 7; between the two marginal edges of the sealing bellows 1 1 folded accordion-like.
  • the bore 7 has at the first, radially, with respect to the axis of rotation of the bearing inner opening, a first stage 1 1, to which the sealing bellows 1 1 is attached, and a second stage 13 at the second, radially outer opening.
  • a first stage 1 1 to which the sealing bellows 1 1 is attached
  • a second stage 13 at the second, radially outer opening.
  • the cross section of the bore 7 tapers such that the piston 10 can not escape from the bore 7.
  • the two stages 12, 13 form a stop for the piston 10, which limits its mobility within the bore 7.
  • the steps 12, 13 may be formed as cutouts with reduced cross-section, here is the bore 7 between a split bearing ring; alternatively, a single free cut may be provided, and the second free cut step is formed by an additional element, for example a reduced diameter cross-section annular disc, which is inserted at one of the openings of the bore 7 and secured secured by screws, for example.
  • an additional element for example a reduced diameter cross-section annular disc, which is inserted at one of the openings of the bore 7 and secured secured by screws, for example.
  • the bearing shown in Fig. 1 a, b and Fig. 2a, b is provided for mounting under water.
  • Fig. 1 a, b the bearing is shown prior to assembly, with air of substantially atmospheric pressure (1 bar, about 1013 hPa) as ambient medium.
  • the pressure of the liquid 9 in the storage space 6 is adjusted so that the piston 10 of the pressure compensation element 8 is shifted to the second stage 13, so that the sealing bellows 1 1 is stretched.
  • Fig. 2a, b the bearing is shown after assembly, in a water depth, the hydrostatic pressure is about 10 bar (about 10130 hPa).
  • the lager is surrounded by water in this case.
  • the pressure compensation element 8 with the piston 10 communicates both with the surrounding medium, namely the water, and with the liquid 9 of the storage space 6 and causes the same pressure to be set in the storage space 6 as outside the bearing, namely one of the depths corresponding hydrostatic pressure.
  • the piston 10 as part of the pressure compensation element 8 shifts within the bore, towards the first stage 12, so that the sealing bellows is transferred to a more folded, relaxed position.
  • the displacement of the piston 10 within the bore is due to the low compressibility of both water and the liquid 9 in the storage space 6 only a small amount, for example, a few millimeters.
  • This is the substantially dimensionally stable Piston 10 is displaced in the bore 7 to the storage room 6, but not significantly deformed, and remains completely within the bore. 7
  • a spring element can be provided which mechanically biases the pressure compensation element 8, in particular the piston 10, and in the mounted position of the bearing (FIGS. 2 a, b) a slight overpressure of the liquid in the storage space 6 to the storage environment.
  • the spring element may for example comprise a plate spring which is mechanically tensioned, in particular compressed, mounted and fixed in the cocked position before sinking the bearing. After sinking the bearing in the intended depth, the pressure equalization between the storage space 6 and the storage environment is formed, namely by moving the piston 10 in the bore 7. Then the fixation of the plate spring is released, this can relax and cover a spring travel, so that the piston 10 additionally undergoes a displacement in the bore 7 and the storage space 6 is acted upon by a slight overpressure.
  • the bore 7 was arranged in the outer ring 2. It is understood that the bore 7 can also be provided in one of the seals 4, 5.
  • the seals 4, 5 may be formed as lip seals and comprise a rigid, such as metallic insert, which is surrounded by an elastic coating.
  • the bore can in this case the seal 4, 5 pass through, while the bore may have a circular or square cross-section.
  • the bore may also follow the annular contour of the seal 4, 5 and, for example, have a circular cross section in plan view of the bore.
  • a plurality of holes are arranged, each having a circular arc in plan view in cross-section, so that the remaining insert of the seal comprises an outer and an inner ring member, the two ring parts of the insert see through the between Bores remaining webs are connected.
  • the piston 10 was formed as a hollow cylinder open on one side. It is understood that the piston may also be formed as a solid cylinder, the weight of which is loaded on the liquid in the storage space 6, so that the solid cylinder causes a slight overpressure of the storage space 6 relative to the storage environment. It is further understood that instead of a hollow or fully cylindrical piston 10 with a circular cross section, the piston can also have an angular cross section, for example a rectangular cross section.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sealing Devices (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

L'invention concerne un palier, notamment pour une utilisation dans un environnement liquide, plus particulièrement pour une utilisation sous l'eau, comprenant un espace de palier (6) compris entre une garniture d'étanchéité (4, 5) et une bague de palier (1, 2) ainsi qu'un trou (7) muni d'un élément de compensation de pression (8) qui ferme ledit trou (7). L'invention vise à mettre au point une solution permettant de compenser la pression, qui ne nécessite sensiblement pas d'espace supplémentaire, pour un palier conçu notamment pour fonctionner dans un environnement liquide. A cet effet, l'espace de palier (6) est rempli avec un liquide (9) et l'élément de compensation de pression (8) est monté de manière à pouvoir se déplacer dans le trou (7).
PCT/EP2011/063328 2010-08-20 2011-08-03 Palier, en particulier pour une utilisation sous l'eau WO2012022615A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010034941.0 2010-08-20
DE102010034941.0A DE102010034941B4 (de) 2010-08-20 2010-08-20 Lager, speziell zur Verwendung unter Wasser

Publications (1)

Publication Number Publication Date
WO2012022615A1 true WO2012022615A1 (fr) 2012-02-23

Family

ID=44503818

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2011/063328 WO2012022615A1 (fr) 2010-08-20 2011-08-03 Palier, en particulier pour une utilisation sous l'eau

Country Status (2)

Country Link
DE (1) DE102010034941B4 (fr)
WO (1) WO2012022615A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013206141A1 (de) 2013-04-08 2014-10-09 Schaeffler Technologies Gmbh & Co. Kg Mediengeschmiertes Wälzlager
DE102013215468A1 (de) 2013-08-06 2015-02-12 Schaeffler Technologies Gmbh & Co. Kg Tauchlageranordnung und Verfahren zur Abdichtung derselben

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB676731A (en) * 1950-07-20 1952-07-30 Roulements A Billes Miniatures Lubricating device for shaft bearings
US3299973A (en) * 1964-07-27 1967-01-24 Smith Ind International Inc Lubrication and sealing of well drilling bit
FR2320457A1 (fr) * 1975-08-06 1977-03-04 Gutehoffnungshuette Sterkrade Carter de roulement ou de palier lisse
US4254838A (en) * 1979-07-24 1981-03-10 Eduardo Barnetche Automatic depth compensating device
GB2058244A (en) * 1979-07-20 1981-04-08 Blohm Voss Ag A bearing assembly
EP0040847A2 (fr) * 1980-05-27 1981-12-02 Eduardo Barnetche Gonzalez Dispositif de compensation de pression
DE20213600U1 (de) 2002-09-04 2002-12-05 AB SKF, Göteborg/Gotenburg Lageranordnung
DE19935014B4 (de) 1998-07-29 2005-03-17 Nsk Ltd. Abgedichtetes Wälzlager
DE102007038604A1 (de) 2007-08-16 2009-02-26 Ab Skf Lager

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE7524907U (de) 1975-12-18 Gutehoffnungshuette Sterkrade Ag Gehäuse für Wälz- und Gleitlager
EP1223359A1 (fr) 2001-01-10 2002-07-17 Dipl.Ing. Hitzinger Gesellschaft m.b.H. Manchon étanche pour le palier d'un générateur sub-aquatique

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB676731A (en) * 1950-07-20 1952-07-30 Roulements A Billes Miniatures Lubricating device for shaft bearings
US3299973A (en) * 1964-07-27 1967-01-24 Smith Ind International Inc Lubrication and sealing of well drilling bit
FR2320457A1 (fr) * 1975-08-06 1977-03-04 Gutehoffnungshuette Sterkrade Carter de roulement ou de palier lisse
GB2058244A (en) * 1979-07-20 1981-04-08 Blohm Voss Ag A bearing assembly
US4254838A (en) * 1979-07-24 1981-03-10 Eduardo Barnetche Automatic depth compensating device
EP0040847A2 (fr) * 1980-05-27 1981-12-02 Eduardo Barnetche Gonzalez Dispositif de compensation de pression
DE19935014B4 (de) 1998-07-29 2005-03-17 Nsk Ltd. Abgedichtetes Wälzlager
DE20213600U1 (de) 2002-09-04 2002-12-05 AB SKF, Göteborg/Gotenburg Lageranordnung
DE102007038604A1 (de) 2007-08-16 2009-02-26 Ab Skf Lager

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013206141A1 (de) 2013-04-08 2014-10-09 Schaeffler Technologies Gmbh & Co. Kg Mediengeschmiertes Wälzlager
WO2014166487A1 (fr) 2013-04-08 2014-10-16 Schaeffler Technologies Gmbh & Co. Kg Palier à roulement lubrifié par une substance
DE102013215468A1 (de) 2013-08-06 2015-02-12 Schaeffler Technologies Gmbh & Co. Kg Tauchlageranordnung und Verfahren zur Abdichtung derselben

Also Published As

Publication number Publication date
DE102010034941B4 (de) 2018-09-13
DE102010034941A1 (de) 2012-02-23

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