WO2021259656A1 - Bague d'étanchéité d'arbre, en particulier bague d'étanchéité d'arbre à deux étages - Google Patents

Bague d'étanchéité d'arbre, en particulier bague d'étanchéité d'arbre à deux étages Download PDF

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Publication number
WO2021259656A1
WO2021259656A1 PCT/EP2021/065633 EP2021065633W WO2021259656A1 WO 2021259656 A1 WO2021259656 A1 WO 2021259656A1 EP 2021065633 W EP2021065633 W EP 2021065633W WO 2021259656 A1 WO2021259656 A1 WO 2021259656A1
Authority
WO
WIPO (PCT)
Prior art keywords
seal
sealing ring
shaft sealing
ring according
seals
Prior art date
Application number
PCT/EP2021/065633
Other languages
German (de)
English (en)
Inventor
Luis HERRLING
Ferdinand Müller
Jakob Schnitzer
Original Assignee
Nidec Gpm Gmbh
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 Nidec Gpm Gmbh filed Critical Nidec Gpm Gmbh
Publication of WO2021259656A1 publication Critical patent/WO2021259656A1/fr

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16JPISTONS; CYLINDERS; SEALINGS
    • F16J15/00Sealings
    • F16J15/16Sealings between relatively-moving surfaces
    • F16J15/32Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • F16J15/3268Mounting of sealing rings
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16JPISTONS; CYLINDERS; SEALINGS
    • F16J15/00Sealings
    • F16J15/002Sealings comprising at least two sealings in succession
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16JPISTONS; CYLINDERS; SEALINGS
    • F16J15/00Sealings
    • F16J15/002Sealings comprising at least two sealings in succession
    • F16J15/004Sealings comprising at least two sealings in succession forming of recuperation chamber for the leaking fluid
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16JPISTONS; CYLINDERS; SEALINGS
    • F16J15/00Sealings
    • F16J15/16Sealings between relatively-moving surfaces
    • F16J15/32Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • F16J15/3204Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16JPISTONS; CYLINDERS; SEALINGS
    • F16J15/00Sealings
    • F16J15/16Sealings between relatively-moving surfaces
    • F16J15/32Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • F16J15/3248Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports
    • F16J15/3252Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports with rigid casings or supports

Definitions

  • the invention relates to a shaft sealing ring, in particular a 2-stage shaft sealing ring according to the preamble of claim 1.
  • EP 0 030 619 B1 uses the example of a rotor compressor to explain a shaft sealing system which has at least two shaft seals, between which a drainage space is provided. The two seals interact axially one after the other in the axial direction of a shaft to be sealed.
  • a shaft seal arrangement is known from EP 0999364 A2, which is formed axially in two stages one after the other in an axial direction of a shaft to be sealed. A first seal and a second seal are provided. A drainage space is formed between these seals which opens into a drainage channel, the drainage channel leading into the environment.
  • the shaft seal mentioned above has two seals which are each fixed radially on the outside and the shaft to be sealed performs a relative movement with respect to the seals. With such a shaft sealing system, relatively high frictional torques must be expected. Furthermore, wear of at least one of the seals can lead to an undesirably severe leak.
  • the object of the invention is to provide a shaft sealing ring, in particular a 2-stage shaft sealing ring, which is optimized with regard to the friction losses between sealing elements and the shaft to be sealed and also has a high sealing effect even with long use. Furthermore, a shaft sealing ring is to be created which provides at least two static seals for a stationary shaft or for a shaft that moves at a relatively low speed.
  • a shaft sealing ring according to the invention according to a first aspect is designed in particular as a 2-stage shaft sealing ring with a first seal and a second seal, which are arranged one behind the other in an axial direction A.
  • the shaft sealing ring has an outer sleeve which surrounds the seals on the outside in a radial direction R; there is an inner sleeve, which is surrounded by the seals in a radial direction R outside, one of the seals being rotationally fixedly coupled to the outer shell in a radial direction R outside and the other seal being rotationally fixedly coupled to the inner sleeve in a radial direction inside.
  • a shaft sealing ring concept can be implemented in a particularly simple manner, which - as shown below - can be easily influenced with regard to its frictional moments via a deformation caused by centrifugal force.
  • a second seal on the inner sleeve that is non-rotatable, i.e. rotates with the shaft speed, automatically creates a centrifugal force-based seal in the manner of a centrifugal disk, since leakage fluid that reaches such a seal is forced radially outwards due to centrifugal force as the seal rotates.
  • one of the seals is designed in the manner of a Simmerring with a sealing lip and the other seal is designed as a flinger. Furthermore, one of the seals is expediently designed as a primary seal and the other seal of the seals is designed as a secondary seal. In particular, it is advantageous to design the primary seal in the manner of a Simmerring, since such a configuration of a seal for sealing off a rotating shaft from a housing has proven itself very well.
  • any leakage fluid that may pass through is then caught by the other seal, which is arranged axially downstream, that is to say acts as a secondary seal, and, due to its effect as a centrifugal disk, is pushed radially outwards.
  • the centrifugal disk is of course non-rotatably connected to the rotating shaft, possibly non-rotatably connected to the sleeve, e.g. B. vulcanized, encapsulated or welded, which also provides a complete seal between the secondary seal and the sleeve.
  • seal which has the sealing lip interacts statically and dynamically with an outside of an inner sleeve or is designed for direct sealing with an outside of a shaft to be sealed.
  • These two variants represent possibilities of either prefabricating the shaft sealing ring as a prefabricated unit with a suitable counter-sleeve (inner sleeve), the latter being attached to a shaft to be sealed. This saves machining effort on the shaft.
  • the other variant if necessary, simplifies the design / manufacture of the shaft sealing ring per se, because the inner sleeve only serves as a carrier for the centrifugal disk which rotates with it and is non-rotatably connected to it.
  • the primary seal in the manner of a Simmerring can interact with a suitably prepared shaft surface. This simplifies the construction of the shaft seal as such.
  • the seal which is designed as a centrifugal disk, forms a radial gap to the inside of the outer sleeve at least during operation at a certain relative speed, in particular a radial gap to the inside of the outer sleeve both during standstill and during operation forms.
  • the centrifugal disk is designed in the manner of a disk spring and is made in particular from an elastomer or an elastic plastic or an elastic, metallic material or composite material.
  • a centrifugal disk made of plastic can, on the one hand, be applied tightly and non-rotatably to the inner sleeve by means of vulcanization or overmolding.
  • the three-dimensional shape of a disc spring which corresponds to a three-dimensional shape in the form of a truncated cone, in conjunction with a correspondingly elastic material, is well suited to realizing deformations of the centrifugal disk caused by centrifugal forces.
  • a contact surface of the seal which is designed as a slinger, is pre-tensioned in the axial direction or at least with an axial direction component on a corresponding mating contact surface, in particular resiliently pre-tensioned, is applied, the mating contact surface being non-rotatably and fluid-tightly coupled to the outer sleeve.
  • Such an embodiment can easily form a static seal through the secondary seal in interaction with the mating contact surface when the shaft is at a standstill, that is, when no centrifugal forces act on the centrifugal disk.
  • the shaft sealing ring has a drainage space in an intermediate space between the seals for receiving leakage fluid which the primary seal has overcome for whatever reasons.
  • a drainage space is used to collect leakage fluid.
  • the outer sleeve has at least one drainage opening, which the gap, d. H. the drainage space communicating with an external environment of the outer sleeve. In this way, accumulated leakage fluid can be removed from the drainage space in a preferred manner and, if necessary, fed to a collecting container or again to a place of origin of the leakage fluid.
  • a guide surface 34 of the centrifugal disk facing the drainage space between the seals is oriented as required during operation such that leakage fluid in the drainage space can be fed to the at least one drainage opening due to centrifugal forces.
  • Such a geometric alignment of the inner surface of the secondary seal facing the drainage space contributes to a particularly effective supply of the leakage fluid to the drainage space or the drainage openings, so that the drainage space can be prevented from filling the drainage space with leakage fluid.
  • the slinger is set up and designed in such a way that it lifts with its contact surface due to centrifugal forces from the counter contact surface at the intended relative speeds between the centrifugal disk and the outer sleeve or the counter contact surface and an axial gap can be formed between these surfaces.
  • Such a configuration which thus forms a static seal in the idle state, can in the dynamic state due to deformation caused by centrifugal forces Experienced axial deformation, so that an axial gap is formed and the friction between the static sealing partners is dynamically canceled.
  • the sealing effect in dynamic use is achieved by using the centrifugal force-related sealing effect of the centrifugal disc, which will be described below.
  • a shaft sealing ring according to the invention can use that seal which has the sealing lip, that is to say that seal which is designed in the manner of a Simmerring, as a primary seal or as a secondary seal.
  • the primary seal is the seal that is closer to the fluid-filling space.
  • the secondary seal is that seal which axially follows the drainage space in a sealing manner with respect to the outside environment.
  • the seal that is designed as a centrifugal disk is complementary to the seal that has the sealing lip, the primary seal or secondary seal.
  • the axial stop is expediently formed by at least one inward bending of the outer sleeve in the radial direction.
  • Fig.l shows a longitudinal section through a shaft sealing ring according to the invention mounted in a housing and interacting with a shaft to be sealed in a static state of rest;
  • FIG. 2 shows the shaft sealing ring according to FIG. 1 in a dynamic sealing state with a rotating shaft
  • FIG. 3 shows a detail X from FIG. 2;
  • FIG 4 shows a perspective view of a second seal in the form of the centrifugal disk in a state that has been remounted with respect to an inner sleeve (illustration of individual parts).
  • a shaft sealing ring 1 according to the invention will be described with reference to FIGS. 1 to 4, FIG. 1 showing an operating position in the idle state and FIG. 2 an operating position in a dynamic operating state with a rotating shaft.
  • a longitudinal axis L of a shaft 2 is also defined as the central axis of the shaft sealing ring 1.
  • a radial direction R is orthogonal to the longitudinal axis L.
  • An axial direction A is a direction parallel to the longitudinal axis L.
  • the shaft sealing ring 1 according to the invention is described using an example of use of the shaft sealing ring 1 at a bearing point 3 of the shaft 2, at which the shaft sealing ring 1 is arranged in a sealing ring seat 4.
  • the sealing ring seat 4 is, for example, firmly connected to a housing and is stationary.
  • the shaft can be driven in a circumferential direction U.
  • the shaft sealing ring 1 comprises a first seal 5 and a second seal 6. Both seals 5, 6 are surrounded on the outside in the radial direction R by an outer sleeve 7. In the radial direction R on the inside there is an inner sleeve 8, which for this purpose is set up and designed to sit on the shaft 2 in a rotationally fixed manner and with respect to this in a sealing manner.
  • the inner sleeve 8 has an axial longitudinal extension such that on the one hand it carries the second seal 6 in a rotationally fixed and fluid-tight manner and, on the other hand, preferably but not absolutely necessary, provides a support area for a sealing lip 9 of the first seal 5, which is designed as a sealing ring, for example .
  • the S centrifugal disk 13 is fluid-tight and non-rotatably connected in the contact area of the centrifugal disk 13 with the inner sleeve, for. B. glued, vulcanized or overmolded. If a metallic material or a composite material is used for the centrifugal disk 13, gluing or welding can also be used.
  • first seal 5 and the second seal 6 there is a drainage space 14 which is bounded in the axial direction A by the first seal 5 and the second seal 6, in the radial direction R inward by the inner sleeve 8 and in the radial direction outward by the outer sleeve 7 is.
  • the drainage space 14 preferably has a plurality of drainage openings 15 along its circumferential direction in the outer sleeve 7.
  • the drainage openings 15 serve - as will be described further below - for emptying the drainage space 14, in which leakage fluid 16, which is fluid 11, which has passed from the fluid space 10, overcoming the first seal 5, has passed into the drainage space 14, if necessary.
  • the second seal 6, which is designed as a centrifugal disk 13 is formed, for example, from an elastic material, e.g. B. a plastic, continue z. B. an elastomer or a thermoplastic is formed, which is elastically deformable in such a way that centrifugal forces that are typical for operation and that act on the centrifugal disk 13 when the inner sleeve 8 rotates with the shaft 2 can lead to a centrifugal force-related deformation of the centrifugal disk 13.
  • a corresponding selection of a suitable elastic material is incumbent on the person skilled in the art depending on the application and depending on the rotational speeds occurring here and the diameter of the slinger 13 and deformability.
  • the corresponding elasticity can either be achieved through suitable material properties or through suitable geometric properties. It is essential that at speeds that are typical for operation when using the centrifugal disk 13, the resulting centrifugal forces are sufficient to achieve the deformation of the centrifugal disk desired according to the invention.
  • material-locking connection techniques such as welding can be considered, for example.
  • Adhesives or otherwise suitable mechanically strong and fluid-tight connections can also be provided.
  • the second seal 6, which is designed as a centrifugal disk 13, has a three-dimensional shape in the shape of a truncated cone in the manner of a disc spring.
  • the centrifugal disk 13 is arranged opposite the inner sleeve 8 in such a way that it encloses an acute angle ⁇ .
  • the centrifugal disk 13 is inclined towards the primary seal in such a way that an inside of the centrifugal disk facing the drainage space 14 encloses the acute angle ⁇ with the longitudinal axis L of the shaft 2.
  • centrifugal disk 13 results in the occurrence of centrifugal forces due to a rotation of the inner sleeve 8, that when a sufficiently elastic material is selected for the centrifugal disk 13, the centrifugal forces that occur cause the centrifugal disk 13 to expand in the radial direction R and due to the three-dimensional shape of the truncated cone, this also causes a displacement of an outer edge 17 of the centrifugal disk 13 in the axial direction A.
  • the displacement component is directed away from the first seal 5 in the axial direction A.
  • the centrifugal disk 13 is thus arranged in cross section at the angle ⁇ with respect to the inner sleeve 8 in such a way that it is arranged inclined radially outwards towards the first seal 5.
  • An inside 18 of the centrifugal disk 13 is oriented in such a way that leakage fluid 16 which reaches the inside 18 of the centrifugal disk 13 is thrown towards the drainage openings 15 by the centrifugal forces that occur in the rotation.
  • the centrifugal disk 13 In the area of the radially circumferential edge 17 of the centrifugal disk 13, the centrifugal disk 13 has a radial gap 19 to an inner side 18 of the outer sleeve 7.
  • a circumferential shoulder 20 is molded into the centrifugal disk 13, so that a shoulder surface 21, which points essentially radially outward, and a contact surface 22 are formed.
  • the contact surface 22 preferably points to the first seal 5 in the axial direction A, but is in any case oriented in such a way that it points in the direction opposite to the deformation direction of the centrifugal disk 13 in the case of rotation of the same in the axial direction A.
  • the contact surface 22 is assigned a mating contact surface 23 which is coupled non-rotatably and tightly to the outer sleeve 7.
  • Such a contact surface 22 can be provided, for example, by a sealing ring 24, as in the embodiments according to FIG. 1, or is optionally formed in one piece with the outer sleeve 7.
  • the shoulder surface 21 is dimensioned in such a way that it maintains a radial and axial distance from the sealing ring 24.
  • a static seal is created by the contact surface 22 being resiliently pretensioned against the mating contact surface 23.
  • the outer sleeve 7 has at one end a bend 25 which is directed radially inward, and a further bend which is oriented in the axial direction A and forms an axial stop 26 with a free end.
  • a drainage ring channel 30, which communicates with an axially extending drainage channel 31, is provided radially surrounding the outer sleeve 7 in the area of the drainage openings 15.
  • the drainage channel 31 can be connected to the fluid space 10 via a check valve 32, the flow direction of the check valve 32 being directed from the drainage channel 31 towards the fluid space 10.
  • the latter depends on the use of the shaft sealing ring according to the invention and represents only one of many possible embodiments.
  • a centrifugal force acting radially outwardly acts on a centrifugal disk 13 appropriately adapted with regard to the choice of material and the elasticity that resulting deformations of the centrifugal disk 13 are brought about for an at least slight axial displacement of the contact surface 22 away from the counter-contact surface 23, so that an axial gap 33 is formed.
  • This axial gap 33 thus gives up the static seal between the contact surface 22 and the mating contact surface 23, which is present in the idle state, which has the effect that the friction between these surfaces, which are resiliently set against each other in the rest state, is also eliminated and a braking friction torque between these surfaces in dynamic use with the Lifting off the contact surface 22 from the mating contact surface 23 becomes zero.
  • the centrifugal disk 13 rotates at a corresponding speed, so that leakage fluid 16 which reaches the inside 18 of the centrifugal disk is initially entrained by the centrifugal disk 13 due to adhesive forces and thus carries out a movement in the circumferential direction.
  • Such a movement in the circumferential direction generates centrifugal forces on the entrained fluid droplets, so that they migrate radially outward and are fed via the inner side 18 to the radially outer area of the drainage space 14 in which the drainage openings 15 are provided, and these thus effectively onto the drainage openings 15 be thrown.
  • the sealing ring 24 has a corresponding guide surface 34, which is arranged and oriented in such a way that droplets of leakage fluid 16, which leave the inside 18 of the centrifugal disk 13 radially outwards, are directed onto the guide surface 34 and from are passed there to the drainage openings 15.
  • Such an adapted guide surface 34 prevents leakage fluid droplets 100, which are thrown radially outward from the inside 18 of the centrifugal disk 13, from being able to pass through the axial gap 33 to the outside.
  • a radial inner edge of the guide surface 34 is offset in the axial direction A from a radial outer edge 35 of the inside 18, so that fluid droplets 100 thrown off radially outwardly strike the guide surface 34 safely.
  • the shoulder surface 21 of the shoulder 20 of the centrifugal disk 13 is arranged with regard to its radial position in such a way that, despite axial deformation of the centrifugal disk 13 due to centrifugal forces, the shoulder surface 21 does not come into contact with the sealing ring 24 or a corresponding other structure and thus increases the friction again would be.
  • a radial trajectory of a leakage fluid droplet 100 which leaves the inside 18 of the centrifugal disk 13 due to centrifugal forces is also shown there in the form of a dashed line.
  • the radially inner edge 101 of the guide surface 34 is offset by an amount t in the axial direction A from the radial outer edge 35 such that a radial trajectory of the droplet 100 (dotted line 102) allows the leakage fluid droplet 100 to strike the guide surface 34 safely.
  • FIG. 4 shows a centrifugal disk 13 suitable for forming the shaft sealing ring 1 according to the invention in a perspective view.
  • the centrifugal disk 13 has a disc spring-like, truncated cone-shaped three-dimensional shape and, on the radially outer edge 17, has the shoulder 20 with the contact surface 22, which is designed to interact with the mating contact surface 23 on the sleeve.
  • the shoulder surface 21 is designed in such a way that sufficient clearance for the sealing ring 24 or the corresponding structure of the outer sleeve 7, not shown, is guaranteed both in the static as well as in the dynamic operating case of the slinger 13.
  • shaft sealing ring With the shaft sealing ring according to the invention, it is possible to provide a particularly low-friction, at least two-stage seal which is equipped via a drainage space for any leakage fluid 16 that may get there.
  • the shaft sealing ring 1 according to the invention can be operated in particular in rotary operation with particularly low friction and very high sealing performance.
  • the axial stop 26 is provided, against which the outside of the centrifugal disk 13, ie with a flat side facing away from the drainage space 14, can rest from a certain speed . This is a sensible additional measure, since it enables the amount t to be ensured even if the rotational speed is excessive.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sealing With Elastic Sealing Lips (AREA)

Abstract

L'invention concerne une bague d'étanchéité d'arbre, en particulier une bague d'étanchéité d'arbre à deux étages (19) comprenant un premier joint d'étanchéité (5) et un second joint d'étanchéité (6) qui sont disposés l'un derrière l'autre dans une direction axiale (A), un manchon extérieur (7) qui entoure extérieurement les joints d'étanchéité (5 ; 6) dans une direction radiale (R), un manchon intérieur (8) qui est entouré extérieurement par les joints d'étanchéité (5 ; 6) dans une direction radiale (R), un des joints d'étanchéité (5 ; 6) étant accouplé de manière solidaire en rotation extérieurement au manchon extérieur (7) dans une direction radiale (R) et l'autre joint d'étanchéité (5 ; 6) étant accouplé de manière solidaire en rotation intérieurement au manchon intérieur (8) dans une direction radiale (R).
PCT/EP2021/065633 2020-06-25 2021-06-10 Bague d'étanchéité d'arbre, en particulier bague d'étanchéité d'arbre à deux étages WO2021259656A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102020116771.7A DE102020116771A1 (de) 2020-06-25 2020-06-25 Wellendichtring, insbesondere 2-stufiger Wellendichtring
DE102020116771.7 2020-06-25

Publications (1)

Publication Number Publication Date
WO2021259656A1 true WO2021259656A1 (fr) 2021-12-30

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PCT/EP2021/065633 WO2021259656A1 (fr) 2020-06-25 2021-06-10 Bague d'étanchéité d'arbre, en particulier bague d'étanchéité d'arbre à deux étages

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WO (1) WO2021259656A1 (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1949001U (de) * 1963-12-05 1966-11-03 Grasso S Konink Machf En N V Auswechselbare wellendichtung.
EP0030619B1 (fr) 1979-12-05 1985-01-02 Karl Prof. Dr.-Ing. Bammert Compresseur à rotor, en particulier compresseur à vis avec alimentation en lubrifiant et drainage du lubrifiant des paliers
EP0999364A2 (fr) 1998-11-04 2000-05-10 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Assemblage d'étanchéité d'arbre avec passage de drainage
FR2874671A1 (fr) * 2004-09-02 2006-03-03 Snr Roulements Sa Palier a roulement a passage d'air comprenant une chambre etanche avec deflecteur

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4428586A (en) 1983-04-04 1984-01-31 Chicago Rawhide Manufacturing Company Combination wear sleeve and excluder lip adapted for easy installation
US4848776A (en) 1987-04-27 1989-07-18 Eaton Corporation Exclusion seal assembly
US5018750A (en) 1989-06-02 1991-05-28 Deere & Company Shaft seal assembly
US5015001A (en) 1990-07-23 1991-05-14 Mather Seal Company Low friction seal assembly

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1949001U (de) * 1963-12-05 1966-11-03 Grasso S Konink Machf En N V Auswechselbare wellendichtung.
EP0030619B1 (fr) 1979-12-05 1985-01-02 Karl Prof. Dr.-Ing. Bammert Compresseur à rotor, en particulier compresseur à vis avec alimentation en lubrifiant et drainage du lubrifiant des paliers
EP0999364A2 (fr) 1998-11-04 2000-05-10 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Assemblage d'étanchéité d'arbre avec passage de drainage
FR2874671A1 (fr) * 2004-09-02 2006-03-03 Snr Roulements Sa Palier a roulement a passage d'air comprenant une chambre etanche avec deflecteur

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