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WO1995020115A1 - Garniture d'etancheite d'arbre - Google Patents

Garniture d'etancheite d'arbre Download PDF

Info

Publication number
WO1995020115A1
WO1995020115A1 PCT/EP1995/000161 EP9500161W WO9520115A1 WO 1995020115 A1 WO1995020115 A1 WO 1995020115A1 EP 9500161 W EP9500161 W EP 9500161W WO 9520115 A1 WO9520115 A1 WO 9520115A1
Authority
WO
WIPO (PCT)
Prior art keywords
sealing ring
sealing
shaft
ring
housing
Prior art date
Application number
PCT/EP1995/000161
Other languages
German (de)
English (en)
Inventor
Heinz K. MÜLLER
Original Assignee
Mueller Heinz K
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 Mueller Heinz K filed Critical Mueller Heinz K
Publication of WO1995020115A1 publication Critical patent/WO1995020115A1/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
    • 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
    • F16J15/3436—Pressing means
    • F16J15/3456—Pressing means without external means for pressing the ring against the face, e.g. slip-ring with a resilient lip
    • 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
    • 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
    • F16J15/3436—Pressing means
    • F16J15/344—Pressing means the pressing force being applied by means of an elastic ring supporting the slip-ring

Definitions

  • the invention relates to a shaft seal for preventing the escape of a liquid from a liquid space into an outer space through a gap between a housing and a rotatable shaft, consisting of a rotor sealing ring which is tightly connected to the shaft and a stator sealing ring which is tightly connected to the housing, and an intermediate sealing ring with two flat end faces, the sealing rings being arranged next to one another in the direction of the shaft axis such that the intermediate sealing ring lies between the rotor sealing ring and the stator sealing ring and the axes of symmetry of the sealing rings essentially coincide with the shaft axis, wherein the rotor sealing ring with a closed end sealing edge lies sealingly against one flat end face of the intermediate sealing ring and the stator sealing ring with a closed end sealing edge lies against the other flat end face of the intermediate sealing ring.
  • the rotor sealing ring and the stator sealing ring consist of polymer plastic
  • the intermediate sealing ring consists of a hard material, in particular of silicon carbide
  • mechanical seals with a rotating slide ring and a stationary counter ring are mainly used to seal pressurized liquids at shaft passage points, the end faces of which are pressed against one another by sliding seals.
  • Mechanical seals are relatively expensive compared to radial shaft seals or V-rings made of elastomer materials, which, however, can only be used without pressure or with a very small overpressure.
  • These simple shaft seals also have the disadvantage that the counter sliding surface is a surface of the machine to be sealed and is not provided by the manufacturer of the sealing ring, which creates problems in ensuring the reliability of the shaft sealing system.
  • the sliding surfaces of the carbon rings of mechanical seals are very sensitive to damage and larger leaks often occur due to wear.
  • structurally simpler and thus more economical solutions for pressure-resistant shaft seals have become known.
  • a shaft seal in which the ring edge of a lip ring made of synthetic polymer material on the polished end face of a hard, preferably ceramic counter ring slides.
  • a sliding pairing in particular polymer / silicon carbide - has the advantage that the polymer sealing ring is relatively insensitive to damage and wearing particles, and on the other hand, in the case of embedded particles, the hard silicon carbide sliding surface has an extremely high wear resistance to abrasion.
  • the extraordinary chemical resistance of silicon carbide on the one hand and the availability of chemically resistant polymers speak in favor of this sliding pairing.
  • the relatively high axial stiffness of the sealing rings used allows only a preload of a few tenths of a millimeter, the observance of which during assembly and maintenance during operation results in a relatively high outlay in terms of the permissible component tolerances.
  • cassette-like shaft seals are known in which the sliding speed at the sealing point and thus the local heating are reduced by means of a floating arrangement of a sealing ring.
  • at least one elastically deformable, usually V-shaped sealing ring is arranged between a stationary housing part and a rotating housing part in a floating manner and touches them in opposite directions with a sealing edge in each case.
  • the sliding surfaces of the housing part or the shaft part are conical or radially flat.
  • a radial shaft seal according to DE 38 33 690, two or more floating sealing rings arranged in parallel are separated by a floating disk, which is also floating, whereby the local sliding speed between the sealing rings, the housing parts and the sliding disk is reduced even further shall be.
  • shaft seals are practically not pressure-resistant, since the contact pressure on the sliding surfaces and therefore also the frictional power increase drastically with the pressure due to the design.
  • a dressing of at least three floating sealing rings that lie axially loosely against one another with at least four potential sliding surfaces is extremely unstable. At a high speed of the shaft, such an arrangement tends to uncontrolled radial vibrations and thus to damaging dynamic stress on the deformable sealing rings.
  • both slide rings and the intermediate slide ring are made of hard materials, which is why relatively large average gap widths can arise during operation due to uneven wear, heat distortion and deposits, which can result in larger leakage rates than in the case of conventional slide ring seals.
  • the slots which are obviously rectified on the circumference of the intermediate slide ring cause a different pressure to prevail on the two opposite end faces of the intermediate slide ring, because when the intermediate slide ring rotates relative to the housing, liquid in the from the intermediate slide ring, the slide ring and the space formed in the housing is pumped in or, if the direction of rotation is different, is pumped out of it.
  • the task was to create stable running, inexpensive to produce and possibly pressure-loaded shaft seals when using the known low-cost combination polymer / silicon carbide, in which as little frictional heat is generated on the sliding surfaces and at the same time with good heat transfer and with the least possible heating of the polymer sealing body is dissipated.
  • a shaft seal consisting of a rotor sealing ring which is tightly connected to the shaft and a stator sealing ring which is tightly connected to the housing, and an intermediate sealing ring, the sealing rings being arranged next to one another in the direction of the shaft axis such that The intermediate sealing ring is located between the rotor sealing ring and the stator sealing ring and the axes of symmetry of the sealing rings essentially coincide with the shaft axis, the rotor sealing ring having a self-contained end sealing edge which bears sealingly on a flat end face of the intermediate sealing ring and the stator Sealing ring has a self-contained front-side sealing edge which lies sealingly on a flat end face of the intermediate sealing ring, the rotor sealing ring and the stator sealing ring being made of polymeric plastic and the intermediate sealing ring being made of a hard one in relation to the material of the sealing rings , preferably consists of ceramic material, and the sealing edges in the manufacturing state of the sealing rings
  • the rotor sealing ring rotating with the shaft transmits a torque to the hard intermediate sealing ring, which is preferably made of silicon carbide, due to friction, and as a result usually sets this in rotation.
  • the flattened sealing edge of the stator sealing ring transmits braking torque due to friction on the intermediate sealing ring.
  • the moving liquid transfers forces to the intermediate sealing ring.
  • the intermediate sealing ring can therefore assume a speed between zero and shaft speed. The heat of friction is distributed over two sealing edges, both of which bear against the intermediate sealing ring.
  • the rotor sealing ring is fastened to surfaces connected to the shaft, the stator sealing ring to surfaces connected to the stator in a known manner in a frictionally locking manner by means of a radial or axial oversize press fit or cohesively by means of gluing, vulcanization or the like.
  • the rotor sealing ring rotates both the liquid to be sealed and the excellent heat-conducting intermediate sealing ring, which is preferably made of silicon carbide.
  • the frictional heat generated on the sliding sealing surfaces is optimally dissipated, particularly in the regions of the surface of the intermediate sealing ring which are generally turbulently flowed around by the liquid to be sealed.
  • the rotating, good heat-conducting intermediate sealing ring dissipates the frictional heat even better in areas of its surface around which air flows than a stationary ceramic ring which is largely encapsulated.
  • the shaft seal according to the invention is less sensitive to deviations in the installation dimensions and has more reserve with regard to maintaining the sealing surface pressure in the event of wear of the sealing edges.
  • This property can be further improved in a manner known per se, in that, in addition to the elasticity of the polymer, the tension of spring elements is used to compress the sealing edges.
  • Metal tongues are preferably used as springs in the sealing ring or firmly connected to them by vulcanization, which are also preloaded when the sealing rings are installed.
  • identical parts are used as the rotor sealing ring and the stator sealing ring.
  • These sealing rings are preferably made of wear-resistant, heat-resistant polymer materials which are resistant to chemical attack by the liquid to be sealed, for example fluoropolymer, fluoroethylene polymer, ethylene-propylene rubber or high-temperature-resistant nitrile-butadiene rubber.
  • the intermediate sealing ring is preferably slidably mounted or guided within the space filled with the liquid to be sealed.
  • a guide part forms a radial guide gap with an outer peripheral surface of the intermediate sealing ring, preferably with a radial gap width between 50 micrometers and 500 micrometers.
  • the intermediate sealing ring is slidably guided on an inner circumferential surface by means of a guide part, which preferably consists of a dry-running material and forms a narrow guide gap with the intermediate sealing ring.
  • both the rotor sealing ring and the stator sealing ring are made of a harder plastic, preferably on the basis of reinforced polytetrafluoroethylene. Because of the higher axial rigidity of the sealing rings in this case, according to the invention, for the purpose of static sealing and to increase the flexibility of the sealing arrangement between the rotor sealing ring and the shaft, a shaft ring made of a polymer plastic which is softer in relation to the rotor sealing ring and at the same time between the Stator sealing ring and the housing additionally arranged a housing ring made of a polymer plastic which is softer in relation to the stator sealing ring.
  • the sealing edges of the stator sealing ring and the rotor sealing ring are preferably circular in the initial direction and the diameter of the sealing edge of the rotor sealing ring is approximately the same size as the diameter of the sealing edge of the stator sealing ring.
  • the hydrodynamic lubrication of the sealing surfaces formed by the flattened sealing edges is preferably improved in that a radial component is superimposed on the tangential sliding movement that occurs when the shaft rotates between the sealing rings and the intermediate sealing ring.
  • this is preferably done in that at least one of the sealing edges has an alternating distance from the shaft axis along its circumference, that is to say is “wavy” when viewed in the circumferential direction.
  • a superimposed radial wiping movement can also be generated in that the center of a circular sealing edge deviates slightly from the shaft axis, that is to say the sealing edge is arranged eccentrically.
  • a changing distance of the sealing edge from the shaft axis is also generated, for example, by the sealing ring being clamped onto a non-circular surface with a radial press fit, the entire sealing ring including its sealing edge deforming out of round.
  • the hydrodynamic return effect is favored in that the surface of the sealing ring adjoining the flattened sealing edge is designed in such a way that it forms an angle ⁇ with the end face of the intermediate sealing ring on the side facing the liquid space, which angle is greater than the angle ⁇ forms the surface of the sealing ring with the end face of the intermediate sealing ring on the side which faces the air-filled outer space.
  • the shaft seal is preferably arranged so that the one to be sealed Liquid is located on the larger diameter of the sealing rings, so that the rotational movement of the liquid induced by the rotation of the shaft, due to the centrifugal force, exerts a returning effect on the liquid penetrating into the gaps between the sealing rings and the intermediate sealing ring.
  • the shaft seal is preferably designed in such a way that the axial thrust acting on the sealing rings from the excess pressure of the liquid to be sealed is largely balanced.
  • the sealing edges of both sealing rings are preferably circular and their diameter is the same.
  • the area enclosed by a sealing edge in the rotor sealing ring is the same size as in the stator sealing ring.
  • the shaft ring lies radially on one with the Shaft-connected cylinder surface and the housing ring radially on a cylinder surface connected to the housing, the two cylinder surfaces having approximately the same diameter and with each sealing ring the ratio of the diameter of its sealing edge to the diameter of the associated cylinder surface has a value between 0 , 8 and 1.2, preferably has the value 1.
  • stator sealing ring in which, due to structural requirements, the stator sealing ring lies in a partial space of the liquid space shielded from the liquid space, good cooling of the stator sealing ring is achieved according to the invention in that a between the stator sealing ring and the rotor sealing ring arranged guide part and or the intermediate sealing ring is provided in a manner known per se with slots directed obliquely to the direction of the shaft axis, which connect the liquid space to the partial space.
  • the intermediate sealing ring rotates relative to the guide part, the liquid carried as a result of the viscosity is axially deflected and is thereby conveyed from the liquid space into the partial space. Additional channels allow the liquid to flow back from the partial space into the liquid space.
  • FIGS. 1 to 4 each show a radial longitudinal section of a basic embodiment of a shaft seal with features according to the invention
  • FIGS. 5 and 6 each show a radial longitudinal section of an embodiment of the shaft seal as a ready-to-install pump sealing system.
  • the shaft seal 1 shows a radial longitudinal section of the shaft seal, which prevents the passage of liquid into the outer space 3 from the liquid space 1 enclosed by a housing 2 through the gap 4 formed by the surface 56 of the shaft 5 rotatable about the shaft axis 51.
  • the rotor sealing ring 6 is connected to the shaft on the circumferential surface 66, for example by an oversize press fit, and its flattened sealing edge 61 lies against the end face 81 of the intermediate sealing ring 8.
  • the stator sealing ring 7 is on the peripheral surface 77, for example connected to the housing by an interference fit and lies with the flattened sealing edge
  • the peripheral surfaces 66, 77 are preferably out of round, as a result of which the sealing ring together with its sealing edge deforms non-round during assembly.
  • a circumferentially variable distance of the sealing edges from the shaft axis and thus an improved hydrodynamic lubrication is achieved particularly advantageously and in a simple manner by the circumferential surfaces 66, 77 being arranged eccentrically to the shaft axis 51.
  • the guide part 21 connected to the housing forms the guide gap 211 within the liquid space with the outer cylindrical peripheral surface of the intermediate sealing ring.
  • Fig. 2 shows a radial longitudinal section of the shaft seal with the liquid space 1, the housing 2, the outer space 3, the shaft 5 with the shaft axis 51, the rotor sealing ring 6, the stator sealing ring 7 and the intermediate sealing ring 8. That with the housing Connected guide part 22 forms the guide gap 221 with the inner cylindrical peripheral surface of the intermediate sealing ring.
  • the surface of the sealing ring adjoining the flattened sealing edge of the rotor sealing ring 6 forms the angle ⁇ and on the end face of the intermediate sealing ring 8 on the side facing the liquid space 1 the side facing the outside 3 the angle ß.
  • FIG. 3 shows in a radial longitudinal section of the shaft seal the liquid space 1, the housing 2, the outer space 3, the shaft 5 with the shaft axis 51, the rotor sealing ring 6, the stator sealing ring 7 and the intermediate sealing ring 8.
  • a shaft ring 62 is arranged, which is radially pressed against the cylinder surface 55 with the diameter D 55.
  • a housing ring is located between the stator sealing ring 7 and the housing 2
  • the sealing edge of the rotor sealing ring 6 has the diameter D61.
  • the sealing edge of the stator sealing ring 7 has the diameter D71.
  • FIG. 4 shows in a radial longitudinal section of the shaft seal the liquid space 1, the housing 2, the outer space 3, the shaft 5 with the shaft axis 51, the rotor sealing ring 6, the stator sealing ring 7 and the intermediate sealing ring 8.
  • a shaft ring 62 is arranged, which is radially pressed against the cylinder surface 55 with the diameter D 55.
  • the rotor sealing ring 6 lies axially on a shaft collar and has channels 63 which allow the passage of liquid from the liquid space 1 to the shaft ring 62.
  • a housing ring 72 is arranged between the stator sealing ring 7 and the housing 2 and is pressed radially against the cylinder surface 77 with the diameter D 77.
  • the stator sealing ring 7 bears axially on a housing surface and has channels 73 which allow the passage of liquid from the sub-space 11 to the housing ring 72.
  • the sealing edge of the rotor sealing ring 6 has the diameter D61.
  • the sealing edge of the stator sealing ring 7 has the diameter D71.
  • the guide part 21 connected to the housing forms within the Liquid space with the outer cylindrical peripheral surface of the intermediate sealing ring, the guide gap 211.
  • the guide part has on its inner side facing the intermediate sealing ring 8 a plurality of slots 212 which connect the liquid space 1 with the partial space 11 of the liquid space in which the stator sealing ring 7 is located.
  • the slots 212 run obliquely to the direction of the shaft axis 51, so that when the intermediate sealing ring 8 rotates relative to the guide part 21, the liquid carried as a result of the viscosity is axially deflected and is thereby conveyed from the liquid space 1 into the partial space 11.
  • the liquid conveyed by the slits flows back into the liquid space through further channels 214, which connect the partial space 11 to the liquid space.
  • FIG. 5 shows in a radial longitudinal section a sealing system for a centrifugal pump with the shaft seal according to the invention.
  • the figure shows the liquid space 1, the seal housing 2 of the sealing system to be attached to the pump, the outer space 3, the shaft axis 51, a shaft sleeve 54 which can be connected to the pump shaft by means of the conical clamping ring 9, and an O-ring which seals the shaft sleeve on the shaft surface.
  • the guide part 21 connected to the housing forms the guide gap 211 with the outer cylindrical peripheral surface of the intermediate sealing ring.
  • the sealing housing is Provided with a feed line 10, through which, as a rule branched off from the pressure line of the pump, a liquid stream which cools and rinses the sealing space is fed. This liquid flow flows through the guide gap 211 into the liquid space 1.
  • FIG. 6 shows a radial longitudinal section through a structural unit with a shaft bearing and the shaft seal according to the invention for the cooling water pump of a motor vehicle.
  • the figure shows the liquid chamber 1, the bearing housing 22, which also accommodates the shaft seal, the rotor sealing ring 6, the stator sealing ring 7 and the intermediate sealing ring 8.
  • FIG. 7 finally shows an enlarged longitudinal section through the shaft seal shown in FIG. 6.
  • 7 shows the liquid space 1, the housing 2 of the shaft seal connected to the bearing housing 22 by means of a press fit, the stator sealing ring 7 connected to the housing, the shaft 5 with the shaft axis 51, and a shaft sleeve connected to the shaft 5 by means of a press fit 54 to which the rotor sealing ring 6 is connected, and the intermediate sealing ring 8.
  • the guide part 21 connected to the housing forms the guide gap 211 with the outer cylindrical peripheral surface of the intermediate sealing ring 8.
  • the guide part 21 has slots 212.
  • the slots extend obliquely to the direction of the shaft axis 51 from the liquid space 1 to the partial space 11 in which the stator sealing ring 7 is located.
  • the intermediate sealing ring 8 rotates relative to the guide part 21, the liquid to be sealed is entrained in the circumferential direction (v) from the outer circumferential surface of the intermediate sealing ring, also within the cavity formed by a slot, and is thereby deflected in the longitudinal direction on the side surface of the slot ( w).
  • liquid is conveyed in this slot either from the liquid space 1 into the partial space 11 or in the opposite direction.

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

Abstract

L'invention concerne une garniture d'étanchéité d'arbre qui rend étanche une chambre de liquide (1) formée par un carter (2) et par un arbre, et qui comprend deux bagues d'étanchéité (6, 7) en polymère, de préférence similaires, une étant reliée à l'arbre (5), l'autre au carter (2). Les arêtes d'étanchéité (61, 71) desdites bagues (6, 7) s'appliquent alternativement de manière étanche sur les faces (81, 82) d'une bague d'étanchéité intermédiaire (8) en carbure de silicium. La bague d'étanchéité intermédiaire (8) est guidée rotative et peut accepter une vitesse de rotation comprise entre zéro et la vitesse de rotation de l'arbre. De manière générale, la chaleur de friction se répartit de ce fait sur les deux arêtes d'étanchéité (61, 71). Un flux turbulent entoure en outre une zone importante de la bague d'étanchéité intermédiaire (8), permettant ainsi d'évacuer complètement la chaleur de friction à des températures basses. Cette garniture d'arbre s'utilise pour l'étanchéité aux liquides de toutes sortes, à condition qu'ils soient chimiquement et thermiquement compatibles avec le matériau polymère constituant les bagues d'étanchéité (6, 7).
PCT/EP1995/000161 1994-01-20 1995-01-17 Garniture d'etancheite d'arbre WO1995020115A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DEP4401567.4 1994-01-20
DE19944401567 DE4401567C1 (de) 1994-01-20 1994-01-20 Wellendichtung

Publications (1)

Publication Number Publication Date
WO1995020115A1 true WO1995020115A1 (fr) 1995-07-27

Family

ID=6508307

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1995/000161 WO1995020115A1 (fr) 1994-01-20 1995-01-17 Garniture d'etancheite d'arbre

Country Status (2)

Country Link
DE (1) DE4401567C1 (fr)
WO (1) WO1995020115A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2415020A (en) * 2004-06-07 2005-12-14 Aesseal Plc A mechanical seal with a central component

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19923530A1 (de) * 1999-05-21 2000-11-23 Univ Dresden Tech Wellendichtring zum Abdichten von Maschinenteilen
DE102004035658B4 (de) * 2003-07-25 2016-06-02 Ceramtec Gmbh Axialwellendichtung
WO2005010412A2 (fr) * 2003-07-25 2005-02-03 Ceramtec Ag Dispositif d'etancheification axiale d'arbre
DE102022105003A1 (de) * 2022-03-03 2023-09-07 Carl Freudenberg Kg Axialdichtring

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3025947C2 (de) * 1979-08-13 1982-12-16 Borg-Warner Corp., 60604 Chicago, Ill. Gleitringdichtung
US4560174A (en) * 1983-12-02 1985-12-24 Berco S.P.A. Multi lip seal
FR2600741A1 (fr) * 1986-06-24 1987-12-31 Jade Sa Garniture d'etancheite pour axes et pivots
US4721311A (en) * 1986-11-07 1988-01-26 Durametallic Corporation Mechanical seal assembly with coolant circulation tube
WO1992007207A1 (fr) * 1990-10-11 1992-04-30 Rotoflex, Inc. Dispositif d'etancheite pour joint rotatif

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3616689C1 (de) * 1986-05-16 1987-11-19 Mueller Heinz Konrad Prof Dr I Dichtung
WO1988004379A1 (fr) * 1986-12-03 1988-06-16 Sealing Devices Pty. Limited Joint d'etancheite rotatif
DE3833690A1 (de) * 1988-10-04 1990-04-12 Acla Werke Gmbh Radialwellendichtung

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3025947C2 (de) * 1979-08-13 1982-12-16 Borg-Warner Corp., 60604 Chicago, Ill. Gleitringdichtung
US4560174A (en) * 1983-12-02 1985-12-24 Berco S.P.A. Multi lip seal
FR2600741A1 (fr) * 1986-06-24 1987-12-31 Jade Sa Garniture d'etancheite pour axes et pivots
US4721311A (en) * 1986-11-07 1988-01-26 Durametallic Corporation Mechanical seal assembly with coolant circulation tube
WO1992007207A1 (fr) * 1990-10-11 1992-04-30 Rotoflex, Inc. Dispositif d'etancheite pour joint rotatif

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2415020A (en) * 2004-06-07 2005-12-14 Aesseal Plc A mechanical seal with a central component
GB2415020B (en) * 2004-06-07 2009-08-26 Aesseal Plc Mechanical seal with central Component

Also Published As

Publication number Publication date
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