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WO2011160657A1 - Joint à lèvre - Google Patents

Joint à lèvre Download PDF

Info

Publication number
WO2011160657A1
WO2011160657A1 PCT/EP2010/003802 EP2010003802W WO2011160657A1 WO 2011160657 A1 WO2011160657 A1 WO 2011160657A1 EP 2010003802 W EP2010003802 W EP 2010003802W WO 2011160657 A1 WO2011160657 A1 WO 2011160657A1
Authority
WO
WIPO (PCT)
Prior art keywords
sealing
seal
protection
lip seal
lip
Prior art date
Application number
PCT/EP2010/003802
Other languages
English (en)
Inventor
Stellario Barbera
Original Assignee
Aktiebolaget Skf
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 Aktiebolaget Skf filed Critical Aktiebolaget Skf
Priority to PCT/EP2010/003802 priority Critical patent/WO2011160657A1/fr
Publication of WO2011160657A1 publication Critical patent/WO2011160657A1/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
    • F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • F16J15/3248—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports
    • F16J15/3252—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports with rigid casings or supports
    • F16J15/3256—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports with rigid casings or supports comprising two casing or support elements, one attached to each surface, e.g. cartridge or cassette seals
    • F16J15/3264—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports with rigid casings or supports comprising two casing or support elements, one attached to each surface, e.g. cartridge or cassette seals the elements being separable from each other
    • 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
    • F16J15/164—Sealings between relatively-moving surfaces the sealing action depending on movements; pressure difference, temperature or presence of leaking fluid
    • 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
    • F16C33/7869—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward
    • F16C33/7879—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward with a further sealing ring

Definitions

  • the present invention relates to a lip seal for sealing a gap between relatively rotatable components.
  • seals adapted to seal the gap between e.g. a housing and a rotatable member such as a shaft.
  • One purpose of the seal is to prevent lubricant from escaping the shaft bearing or the axle drive.
  • Another purpose is to prevent contaminants from entering into the shaft bearing.
  • the bearing may often comprise an integrated seal, but for larger applications, it is common to use a separate sealing arrangement.
  • a seal arrangement that is often used is a radial shaft seal, which is inserted into the housing bore and contacts the periphery of the shaft with a flexible lip seal. Such a seal is less suited to seal an axle drive because it prevents the penetration of contaminants only to a limited extent. The arrangement of one or a plurality of additional radial protective lips is also not completely satisfactory.
  • cassette seals may be used.
  • a cassette seal normally comprises two sealing parts, one outer part that is mounted to the housing and one inner part that is mounted to the shaft.
  • a cassette seal is often adapted to be mounted to a fixed outer housing, where the shaft rotates, but there are types available that are adapted to be mounted on a fixed shaft with a rotating housing.
  • a typical cassette seal comprises a sleeve which is placed on the shaft and is provided with a radial flange as a baffle plate.
  • the primary lip seal which is mounted to the housing and which is in contact with the circumferential surface of the sleeve at the sealing lip, may be provided with a secondary lip which comes into contact with the radial flange. This axially oriented secondary lip is adapted to prevent the penetration of contaminants.
  • GB 2369413 A discloses a sealing arrangement comprising both dynamic sealing means and static sealing means, where the dynamic sealing means prevents flow outwardly through the gap when the shaft is rotating and the static seal seals the gap when the shaft is stationary.
  • the static seal engages the contact surface with less force when the shaft begins to rotate and may lose contact with the contact surface when the shaft rotates at sufficient speed, wear of the static seal and friction losses are reduced.
  • the static seal is arranged to lose contact with the contact surface at a rotational speed of the shaft which is sufficient to bring the dynamic seal of the sealing arrangement into operation.
  • EP 0489604 A1 discloses a seal which is provided for use with a machinery housing and a rotatable shaft protruding through the housing.
  • the seal comprises a stator ring affixed to the housing and a rotor ring which is attached to the shaft and which nests within the stator.
  • the stator and rotor are so shaped that the stator has a male cylindrical surface, and the rotor has a female cylindrical surface located radially outwardly of the stator male surface.
  • a solid, deformable annular seal member is mounted on the rotor female surface and engages the stator male surface when the rotor and seal member are at rest.
  • US 6,474,653 B1 discloses a seal arrangement for a shaft having a broad rpm range, supported in a housing, in particular for axle drives.
  • a radial shaft seal arranged in the housing bore, seals the shaft bearing space from loss of lubricant.
  • a baffle plate joined to the shaft, and having a lip seal, is aligned radially to the inside, which under the effect of centrifugal force lifts off from its sealing surface at higher rotational speeds of the shaft.
  • US 4,348,031 A discloses a rotary fluid seal, especially an oil seal for a rotary shaft, which comprises a sealing ring between axially-opposed divergent frusto- conical counterfaces of relatively rotatable members.
  • the sealing ring has a pair of divergent sealing lips with frusto-conical contact faces to the counterfaces and floats freely between the relatively rotatable members.
  • the contact faces bear frictionally on the counterfaces so that, on relative rotation of the members, the sealing ring is frictionally driven into rotation by one or the other of the members.
  • the effect of centrifugal force which tends to cause the sealing lips to flex angularly outwardly, reduces the bearing load of the contact faces on the counterfaces.
  • US 4,572,516 A discloses a low friction dynamic seal assembly in which a seal body is selectively bonded to certain portions of a seal case fixable to a rotatable member.
  • the selected bonding creates a hinge with the seal case of controllable resistance to the initial deflection of the seal body caused when the seal case is fixed rotatable member.
  • the seal body is selectively bonded substantially only to that portion of the seal case toward which the seal body is deflected. Therefore, reduced frictional loads are provided at low speed of rotation. Additionally, the hinge provided by the selected bonding allows further deflection of the seal body at higher speeds of rotation to further reduce seal friction.
  • US 5,979,903 A discloses a slinger for use between a housing and a rotatable member passing there through, which includes an engaging member for mounting on the rotatable member, a slinger portion extending radially outward from the engaging portion, and a sealing portion generally axially extending from the slinger portion.
  • the sealing portion extends radially outward when subjected to centrifugal force caused by rotation of the rotatable member to form a secondary seal.
  • An object of the invention is to provide a seal arrangement that delivers excellent static and dynamic sealing, and which enables reduced friction torque under dynamic conditions.
  • the invention resides in a lip seal for sealing a gap between a housing and a rotatable member, the seal comprising a sealing body adapted to be fixedly positioned in the housing and a protection member adapted to be mounted on the rotatable member.
  • the protection member comprises a cylindrical sleeve and a protection disc that extends from the sleeve in a radially outward direction.
  • the sealing body comprises at least one sealing lip that is adapted to bear on the protection disc when the rotatable member is standing still.
  • the object of the invention is achieved in that the protection disc is adapted to move away from the sealing lip due to centrifugal forces when the protection disc rotates with a speed above a predetermined rotational speed.
  • a seal arrangement is provided that will be less subject to friction losses and to wear. Since the sealing lip and the corresponding counterface will part at higher rotational speeds, the wear will be reduced significantly. Further, the wear at high rotational speeds is more severe than at low speeds. More heat is created between the surfaces at higher speeds which also add to the wear. By using a protection disc that moves away from the corresponding sealing lip above a predefined rotational speed, the wear of the sealing lip is thus reduced. In a development of the inventive radial lip seal, an angle a between the mounting sleeve and the protection disc is less than 90 degrees.
  • the protection member may have different shapes and may be made from different materials.
  • the protection disc may be flat or may comprise a first inner section and a second outer section, where the first inner section and the second outer section are angled with respect to each other.
  • the protection disc may be provided with a weight at an outer edge, which will help the protection disc to deflect outwards under rotational conditions.
  • the protection member may be made from one and the same material in one piece, such as steel.
  • the protection member may also comprise a hinge between the mounting sleeve and protection disc, where the hinge is made from an elastic material or from the same, but thinner, material as the mounting sleeve and the protection disc are made from.
  • the lip seal is supplied as one unit that is prefilled with grease. This simplifies the assembly of the radial seal.
  • the sealing body of the radial lip seal may be is made from an elastomer and may comprise an inner rigid frame contained in the elastomer.
  • the sealing body may also be made from a metal insert and an elastomer member fixedly attached to the metal insert.
  • Fig. 1 shows a first embodiment of a radial lip seal in a stationary state according to the invention
  • Fig. 2 shows the first embodiment of a radial lip seal during rotation according to the invention
  • Fig. 3 shows a further example of the radial lip seal according to the invention.
  • Fig. 4 shows a second embodiment of the radial lip seal according to the invention.
  • Fig. 1 shows a first embodiment of a seal arrangement 1 according to the invention comprising a sealing body 2 and a protection member 3 that is adapted to be mounted between a stationary housing 12 and a rotatable shaft 11.
  • the housing may be a stationary machine part or the wheel suspension of a vehicle, or a bearing outer ring.
  • the shaft may be any shaft or axle suspended with bearings to the housing, or may be also be a bearing inner ring. Due to the nature of the inventive seal arrangement, it is well adapted for harsh environments, and may be used throughout production plants and for the automotive industry.
  • the seal arrangement comprises a sealing body 2 which is mounted with a press fit in a cylindrical bore in the housing.
  • the sealing body 2 is made from an elastomer with a metallic frame 13.
  • the metallic frame runs axially in an outer axial sleeve 14 and in a radially inwards directed radial wall 15.
  • the sealing body 2 further comprises an axial part 16 and a first sealing lip 4.
  • the axial part 16 may be part of a labyrinth seal comprised in the seal arrangement which may be formed between the axial part 16 and an opposite sleeve 5 of the protection member 3.
  • the axial part may thus be provided with different sealing protrusions pointing inwards towards the sleeve 5.
  • the first sealing lip is in the shown example angled about 45 degrees towards the outer axial sleeve 14.
  • a sealing body 2 is shown in Fig. 4, where the sealing body 2 comprises a metal insert 30 and an elastomeric sealing member 31.
  • the metal insert runs axially with an outer axial sleeve 32 and in a radially inwards directed radial wall 33.
  • the sealing member 31 is fixedly attached to the end region of the radial wall 33.
  • the elastomeric sealing member 31 comprises an axial part 34 and a sealing lip 35.
  • the axial part 34 may also form a labyrinth seal as described above or may be urged against the mounting sleeve 5 of the protection member 3 by the use of a garter spring 36 as shown in Fig. 4.
  • the sealing lip 35 is in the shown example angled about 45 degrees towards the outer axial sleeve 32.
  • the protection member 3 is adapted to be mounted on a rotatable member, such as an axle or shaft 11.
  • the protection member comprises a mounting sleeve 5 which is axial and adapted to be mounted with a press fit to the shaft.
  • the protection member further comprises a protection disc 6, also known as a flinger, which extends radially outwards from the mounting sleeve 5 and which is angled with an angle a with respect to the mounting sleeve 5.
  • the angle a is less than 90 degrees.
  • the shape of the protection disc is preferably substantially flat, but a slightly curved shape is also possible.
  • the angle a is dependent on the design of the seal arrangement but is preferably in the interval between 60 and 80 degrees. The angel a depends on the available space and also on the required deflection of the protection disc.
  • the protection disc comprises an inner section 7 and an outer section 8 which are angled with respect to one another.
  • the outer section 8 of the protection disc may comprise a weight 9 that will help to increase the deflection of the protection disc during rotation.
  • the weight may be a ring-shaped element that is mounted to an axially outer surface of the outer section 8 of the protection disc.
  • the seal arrangement comprises a first sealing contact region 17 between the sealing body 2 and the protection member 3.
  • the sealing lip 4 will bear against a mid-section of the protection disc 6 when the seal arrangement is in a steady state, i.e. stands still.
  • the sealing lip 4 will also bear against the mid-section of the protection disc when the shaft rotates with a speed below a predefined rotational speed, even though the force between the sealing lip and the bearing surface will reduce with the rotational speed.
  • the seal arrangement shown in Fig. 1 is in a stationary state. In Fig.
  • the seal arrangement is shown during rotation of the rotatable shaft 11 with a predefined rotational speed.
  • the protection member 3 is designed such that the protection disc 6 will move away from the sealing lip 4 by the centrifugal force created by a specific rotational speed.
  • the protection disc is designed to be in contact with the sealing lip at a speed below approximately 1000 rpm.
  • the working speed of the system is between 1500 - 2500 rpm, which means that the protection disc will not bear against the sealing lip during most of the use.
  • a seal arrangement with two contact regions is shown in a steady state.
  • a second contact region 18 is provided between an end section of the outer axial sleeve 14 and an axially inner surface of the outer section 8 of protection disc 6.
  • the end section of the outer axial sleeve 14 is provided with a second sealing lip 19 which will bear against the outer section of the protection disc when the shaft rotates with a speed below a predefined rotational speed.
  • the contact regions may also be designed such that the force acting on the sealing body by the protection member differs. In this way, it is possible to design the contact regions such that the protection disc will leave one of the contact regions before the other when it deflects.
  • the contact region 18 may open at a first rotational speed, e.g. at 1000 rpm, and the contact region 17 may open at a higher rotational speed, e.g. 2000 rpm. This is advantageous since the peripheral speed is higher at the contact region 18. By opening this region first, the wear in this region is reduced but the seal at the contact region 17 is still closed. When the rotational speed increases, and thus the peripheral speed at the contact region 17, the contact region 17 will also open, reducing the wear in this region as well.
  • the surface of the protection disc in the contact regions may also be treated with a low-friction treatment in order to reduce the wear further.
  • the advantage of the inventive seal arrangement is that during still-stand and low rotational speeds, the seal arrangement will be closed and will thus seal the area behind the seal arrangement.
  • the seal arrangement provides an environmental seal against both liquids and gases.
  • the rigid protection disc that is positioned as the outermost protection provides a mechanical protection that prevents particles and the like to enter the seal arrangement.
  • the wear of the sealing lip due to friction is relatively low because the wear is dependent on the rotational speed. At higher speeds, the wear caused by friction will disappear due to the deflection of the protection disc.
  • the seal arrangement is used on a vehicle, the requirements of the seal arrangement, e.g.
  • the vehicle may drive in difficult conditions, e.g. in mud, which requires a tight seal of the bearings, but at higher speeds, the requirements on the seal are reduced since the possible contaminations are reduced considerably when driving on a highway.
  • the rigid protection member deflects due to centrifugal forces.
  • the elastic sealing body By mounting the sealing body on the stationary part, the elastic sealing body can be designed without any restrictions as to deflections due to the centrifugal force. Instead, the sealing body can be designed in order to provide optimal sealing characteristics.
  • the protection member is relatively simple, and provides a flat outer surface without any prongs or grooves where dirt can accumulate.
  • the protection member 3 is in the shown example produced from a thin metal sheet that is formed with a somewhat V-shaped cross section, i.e. the angle a is acute.
  • the seal arrangement is intended for a vehicle having a shaft with a diameter of 35 mm and with a bearing having an outer diameter of 100 mm.
  • the thickness of the protection member is suitable in the range of 0.7 - 1.0 mm. Depending on the material used and the size of the protection member, this measure may of course vary considerably.
  • the sheet material may have the same thickness over the complete surface. It is also possible to let the thickness be thinner in a hinge region 10, in order to facilitate the deflection of the protection member.
  • the protection member is also possible to manufacture from other materials, depending on the requirements.
  • An injection-molded plastic part is e.g. plausible for some applications.
  • the protection member is manufactured from different materials, with the mounting sleeve 5 and the protection disc 6 made from metal and the hinge section 10 made from an elastic material.

Landscapes

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

Abstract

L'invention concerne un joint à lèvre (1) destiné à obturer un espacement entre un logement (12) et un organe rotatif (11), le joint comportant un corps de scellage (2) conçu pour être positionné fixement dans le logement et un organe de protection (3) conçu pour être monté sur l'organe rotatif. L'organe de protection comprend un manchon cylindrique (5) et un disque de protection (6) qui s'étend à partir du manchon dans une direction vers l'extérieur dans le sens radial. Le corps de scellage comprend au moins une lèvre de scellage (4) conçue pour appuyer sur le disque de protection lorsque l'organe rotatif se trouve à l'arrêt. Selon l'invention, le disque de protection (6) est conçu pour s'éloigner de la lèvre de scellage en raison des forces centrifuges lorsque le disque de protection tourne à une vitesse supérieure à une vitesse de rotation prédéterminée.
PCT/EP2010/003802 2010-06-25 2010-06-25 Joint à lèvre WO2011160657A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/EP2010/003802 WO2011160657A1 (fr) 2010-06-25 2010-06-25 Joint à lèvre

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP2010/003802 WO2011160657A1 (fr) 2010-06-25 2010-06-25 Joint à lèvre

Publications (1)

Publication Number Publication Date
WO2011160657A1 true WO2011160657A1 (fr) 2011-12-29

Family

ID=43629533

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2010/003802 WO2011160657A1 (fr) 2010-06-25 2010-06-25 Joint à lèvre

Country Status (1)

Country Link
WO (1) WO2011160657A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
TWI610859B (zh) * 2015-03-10 2018-01-11 特瑞勒伯爾葛密封問題解決方法美國公司 罐頭密封總成
WO2018130611A1 (fr) * 2017-01-11 2018-07-19 Parker Hannifin Manufacturing Germany GmbH & Co. KG Ensemble d'étanchéité

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4348031A (en) 1980-03-18 1982-09-07 George Angus & Company Limited Rotary fluid seals with floating sealing rings
US4553762A (en) * 1982-10-11 1985-11-19 Firma Carl Freudenberg Shaft seal ring
US4572516A (en) 1985-06-12 1986-02-25 General Motors Corporation Low friction dynamic seal assembly with centrifugal deflection
EP0489604A1 (fr) 1990-12-05 1992-06-10 Inpro Companies, Inc. Assemblage d'étanchéité d'arbres statique et dynamique
EP0766016A2 (fr) * 1995-09-26 1997-04-02 RFT S.p.A. Joint d'étanchéité et anneau de garde pour paliers à roulement
US5979903A (en) 1997-12-04 1999-11-09 Sanford Acquisition Company Translucent slinger with centrifugal seal
GB2369413A (en) 2000-11-28 2002-05-29 Federal Mogul Technology Ltd Static and dynamic sealing arrangement
US6474653B1 (en) 1999-05-07 2002-11-05 Firma Carl Freudenberg Seal arrangement
US20040062461A1 (en) * 2002-09-30 2004-04-01 Johnson James P. Roller bearing having high performance bearing seal and cartridge
DE102008030710A1 (de) * 2008-06-27 2009-12-31 Schaeffler Kg Kassettendichtung

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4348031A (en) 1980-03-18 1982-09-07 George Angus & Company Limited Rotary fluid seals with floating sealing rings
US4553762A (en) * 1982-10-11 1985-11-19 Firma Carl Freudenberg Shaft seal ring
US4572516A (en) 1985-06-12 1986-02-25 General Motors Corporation Low friction dynamic seal assembly with centrifugal deflection
EP0489604A1 (fr) 1990-12-05 1992-06-10 Inpro Companies, Inc. Assemblage d'étanchéité d'arbres statique et dynamique
EP0766016A2 (fr) * 1995-09-26 1997-04-02 RFT S.p.A. Joint d'étanchéité et anneau de garde pour paliers à roulement
US5979903A (en) 1997-12-04 1999-11-09 Sanford Acquisition Company Translucent slinger with centrifugal seal
US6474653B1 (en) 1999-05-07 2002-11-05 Firma Carl Freudenberg Seal arrangement
GB2369413A (en) 2000-11-28 2002-05-29 Federal Mogul Technology Ltd Static and dynamic sealing arrangement
US20040062461A1 (en) * 2002-09-30 2004-04-01 Johnson James P. Roller bearing having high performance bearing seal and cartridge
DE102008030710A1 (de) * 2008-06-27 2009-12-31 Schaeffler Kg Kassettendichtung

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
TWI610859B (zh) * 2015-03-10 2018-01-11 特瑞勒伯爾葛密封問題解決方法美國公司 罐頭密封總成
US10337617B2 (en) 2015-03-10 2019-07-02 Trelleborg Sealing Solutions Us, Inc. Canned seal assembly
WO2018130611A1 (fr) * 2017-01-11 2018-07-19 Parker Hannifin Manufacturing Germany GmbH & Co. KG Ensemble d'étanchéité

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