WO1998026202A1 - Joint d'etancheite sollicite par ressort - Google Patents

Joint d'etancheite sollicite par ressort Download PDF

Info

Publication number
WO1998026202A1
WO1998026202A1 PCT/US1997/022453 US9722453W WO9826202A1 WO 1998026202 A1 WO1998026202 A1 WO 1998026202A1 US 9722453 W US9722453 W US 9722453W WO 9826202 A1 WO9826202 A1 WO 9826202A1
Authority
WO
WIPO (PCT)
Prior art keywords
shield
seal
edge
groove
mounting portion
Prior art date
Application number
PCT/US1997/022453
Other languages
English (en)
Inventor
Dennis L. Otto
Original Assignee
The Timken Company
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 The Timken Company filed Critical The Timken Company
Priority to AU78489/98A priority Critical patent/AU7848998A/en
Publication of WO1998026202A1 publication Critical patent/WO1998026202A1/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
    • F16C33/72—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
    • F16C33/7883—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 mounted to the inner race and of generally L-shape, the two sealing rings defining a sealing with box-shaped cross-section
    • 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
    • F16C33/7803—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members suited for particular types of rolling bearings
    • F16C33/7813—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members suited for particular types of rolling bearings for tapered roller bearings
    • 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
    • F16J15/326—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 with means for detecting or measuring relative rotation of the two elements
    • 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
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/38—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers
    • F16C19/383—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F16C19/385—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings
    • F16C19/386—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings in O-arrangement

Definitions

  • This invention relates in general to seals and more particularly to a seal having a resilient element for effectively biasing edges of the seal element against sealing surfaces.
  • Automotive wheel bearings and the seals which protect them have diminished in size over the years. Better steels have made smaller bearings possible, whereas improved seal designs reduced the size of the seals. The smaller bearings and seals left room for additional components, such as rotors and sensors for antilock braking systems and constant velocity joints. Installing the seals in the bearings themselves instead of in the hubs or housings that contain the bearings produced a further reduction in size. This practice contributed to the wide-spread use of unitary or package bearings.
  • the seals should provide an extra measure of protection, and this generally requires that they provide multiple fluid barriers and that the fluid barriers remain effective for extended periods of time.
  • the present invention resides in a seal having an elastomeric seal element that closes an annular space between two machine components, one of which rotates relative to the other about an axis of rotation.
  • One of the machine components carries axially directed and radially directed surfaces.
  • the seal element has a mounting portion that is fixed in position with respect to the other machine component and a contact lip portion provided with radially and axially presented edges.
  • the seal element contains a groove which opens away from the axis of rotation and generally separates the mounting portion from the contact lip portion.
  • a resilient element fits into the groove, but does not bottom out in the groove, and it acts upon the lip portion such that the axially presented edge is urged against the radially directed surface and the radially presented edge is urged against the axially directed surface.
  • the invention also consists in the parts and in the arrangements and combinations of parts hereinafter described and claimed.
  • FIG. 1 is a sectional view of a bearing fitted with a seal constructed in accordance with and embodying the present invention
  • Fig. 2 is an enlarged sectional view of the seal
  • Fig. 3 is a fragmentary sectional view of the seal taken along line 3-3 of Fig. 2;
  • Fig. 4 is a sectional view of a modified seal;
  • Fig. 5 is a sectional view of another modified seal.
  • Fig. 6 is a sectional view of still another modified seal.
  • a seal B thus confining a lubricant, which is normally grease, to the interior of the bearing A, and excluding contaminants, such as water and dust, from that interior.
  • the bearing A fits between two machine components and enables one of those components to rotate relative to the other about an axis X with minimum frictional resistance.
  • the seal B may fit between and close an annular space that exists between any two machine components, one of which rotates relative to the other, but the closure of an antifriction bearing represents the primary utility for the seal B, and in that sense the two machine components may be races of the bearing itself.
  • the bearing A which is conventional, includes (Fig.
  • the bearing A has cages 8 which are integrated into the two rows of rollers 6 and serve to maintain the proper spacing between the rollers 6 as well as to retain the rollers 6 around the cones 4 when the cones 4 are withdrawn from the cup 2.
  • the rollers 6 of the two rows contact the cup 2 and the cone 4 along opposed raceways 10, there being two raceways 10 on the cup 2 and a single raceway 10 on each cone 4. Basically, line contact exists between the side faces of the rollers 6 and the raceways 10.
  • the raceways 10 of the cup 2 taper downwardly toward each other, and hence their smallest diameters lie generally midway between the ends of the cup 2. At their large ends the cup raceways 10 merge into end bores 12 which open out of ends of the cup 2.
  • Each cone 4 in addition to its raceway 10, has a thrust rib 14 at the large diameter end of its raceway 10.
  • the large ends of the tapered rollers 6 bear against the thrust rib 14, and indeed the thrust rib 14 prevents the rollers 6 from being expelled from the bearing A.
  • the thrust rib 14 for each cone 4 has a cylindrical mounting surface 18 that is presented outwardly away from the axis X and ends at a back face 20 which is squared off with respect to the axis X.
  • the raceways 10 of the cup 2 and the cones 4 define an annular space 22
  • the seals B close the ends of the annular space 22 (Fig. 1), and they retain the lubricant for the bearing A in the space 22 and exclude contaminants from it. Actually, the seals B fit into the end bores 12 of the cup 2 and around the thrust ribs 14 of the cones 4, providing live or dynamic barriers in these regions.
  • Each seal B includes (Figs. 1 and 2) a case 26 which fits into the end bore 12 at that end of the bearing A closed by the seal B, another case or shield 28 which fits around the cone thrust rib 14 at the same end of the bearing B, a primary seal element 30 which is bonded to the case 26 and contacts the shield 28, establishing three dynamic barriers along the shield 28, and a secondary seal element 32 which is bonded to the shield 28 and establishes yet another dynamic fluid barrier along the case 26.
  • Both of the seal elements 30 and 32 are molded from an elastomer and as such have a measure of resiliency.
  • each seal B includes a garter spring 33 which acts upon the primary seal element 30 to ensure the effectiveness of two of the fluid barriers established by it.
  • the case 26 includes (Fig. 2) an axial wall 34 which fits within and along the end bore 12 in which the seal B is housed and a radial wall 36 which is directed radially inwardly from the axial wall 34.
  • the diameter of the axial wall 34 slightly exceeds that of the end bore 12, so that an interference fit exists between the case 26 and the cylindrical surface of the end bore 12. Hence, one must press the case 26 into the end bore 12. Indeed, the case 26 is advanced through the bore 12 until the free end of its axial wall 34 lies flush with the end face of the cup 2. The interference fit creates a static fluid barrier between the case 26 and the cup 2.
  • the radial wall 36 while being directed toward the cone thrust rib 14 which lies within the end bore 12, terminates short of that thrust rib 14, so that a space of moderate size exists between the inner end of the radial wall 34 and the mounting surface 18 on the thrust rib 14.
  • That mounting surface 18 serves to position and support the shield 28.
  • the shield 28 includes (Fig. 2) an axial wall 38 and a radial wall 40.
  • the axial wall 38 lies along the mounting surface 18 of the thrust rib 14, and indeed an interference fit exists between the two. That interference fit creates a static fluid barrier between the shield 28 and the cone 4.
  • the axial wall 38 of the shield 28 is pressed over the mounting surface 18 of the cone thrust rib 14.
  • the radial wall 40 projects outwardly from the axial wall 38 toward the axial wall 34 of the case 26 and obscures the radial wall 36 of the case 26.
  • the radial wall 40 of the shield 28 forms the exposed end of the seal B and generally lies flush with the end of the cup 2 and the back face 20 of the cone 4. It is separated from the radial wall 36 of the case 26, and the space between the two radial walls 36 and 40 forms an annular cavity. At its opposite end the axial wall 38 of the shield 28 merges into a slight flange 42 which is directed radially outwardly slightly beyond the inner edge of the radial wall 36 on the case 26, so that the case 26 is captured between the ends of the shield 28.
  • the shield 28 has another axial wall 44 (Fig 2) which extends from the radial wall 40 at the periphery of that wall such that the axial wall 44 encircles the inner axial wall 38.
  • the outer axial wall 44 lies within the axial wall 34 of the case 26, and it projects toward the radial wall 36 of the case 26, terminating short of it.
  • the primary seal element 30 is attached to the case 26 and includes a mounting portion 46 which is bonded to the radial wall 36 of case 26 on both faces of that wall as well as along the end edge of wall 36.
  • the seal element 30 also includes a contact lip portion 48, which projects generally axially from mounting portion 46.
  • the mounting portion 46 does not actually contact the shield 28, but even so, it creates a labyrinth which serves as a barrier to the movement of the bearing lubricant along the inner axial wall 38 of the shield 28.
  • the contact lip portion 48 on the other hand, actually contacts the shield 28 along both the inner axial wall 38 and the radial wall 40 and at those regions of contact establishes more dynamic fluid barriers.
  • the mounting portion 46 has an inner surface that is presented toward, yet spaced from the axial wall 38 of the shield 28.
  • the spacing between the wall 38 and the inner surface 52 is small enough to create a labyrinth that serves as barrier to the movement of lubricant along the axial wall 38.
  • the space between the inner surface 52 on the mounting portion 46 and the axial wall 38 of the shield should be between 0.005 and 0.030 inches to produce an effective labyrinth.
  • the inner surface 52 ends at an edge which is presented toward the flange 42 on the shield 28.
  • the labyrinth created by the inner surface 52 on the mounting portion 46 is enhanced by wedge-shaped cavities 54 (Figs.
  • the cavities 54 being wedge-shaped, have surfaces that lie oblique to the direction of relative movement between the mounting portion 46 and the axial wall 38 of the shield 28, and as a consequence, grease which enters the cavities 54 is deflected back into the annular space 22 between the cup 2 and cone 4.
  • the contact lip portion 48 lies axially beyond the mounting portion 46 where the outer axial wall 44 of the shield 28 encircles it. It projects toward both the inner axial wall 38 and the radial wall 40 of the shield 28 and has edges 56 and 58 which contact those walls, the former the wall 38 and the latter the wall 40. To this end, the lip portion 48 has a slight curved inner face 60 which lies oblique to the axis and leads away from the inner surface 52 of the mounting portion 46. In addition, the lip portion 48 has an end face 62 which likewise lies oblique to the axis X, although at a greater angle. The end face 62 is presented toward the corner where the inner axial wall 38 and the radial wall
  • the lip portion 48 has another end face 64 which likewise lies oblique to the axis X, but is presented generally away from the axis X.
  • the inner face 60 and end face 62 converge toward the edge 56 which bears against the inner axial wall 38 of the shield 28.
  • the two end faces 62 and 64 converge toward the edge 58 which bears against the radial wall 36 of the shield 28.
  • the primary seal element 30 also has an annular groove 66 (Fig. 2) which opens away from the axis X and generally separates the mounting portion 46 from the lip portion 48. Indeed, it is in the region of the groove 66 that the seal element 30 has its smallest cross-section, and this imparts a good measure of flexibility to the lip portion 48, enabling it to flex easily with respect to the mounting portion 46.
  • the groove 66 has an oblique side face 70 that lies along the lip portion 48, a radial side face 72 that lies along the mounting portion 46, and a curved face 74 that joins the two side faces 70 and 72.
  • the oblique side face 70 lies behind end face 62, but is oriented at a slightly lesser angle to the axis X.
  • the radial side face 72 lies immediately beyond and parallel to the radial wall 36 of the case 26.
  • the side faces 70 and 72 converge - indeed, toward the curved face 74 which joins them.
  • the center of curvature for the curved face 74 is offset axially from the radial edge 56 toward the mounting portion 46.
  • the annular groove 66 receives the garter spring 33 which urges the contact lip portion 48 against both the inner axial wall 38 and the radial wall 40 of the shield 28. More specifically, the garter spring 33 lodges in the groove 66, but does not actually seat against the curved face 74 at the bottom of the groove 66. It cannot inasmuch as its cross-sectional radius is somewhat greater than the radius of the curved face 74. Instead, the garter spring 33 bears against the radial side face 72 and the oblique side face 70 of the groove 66 with a void between the convolutions of the spring 33 and the curved face 74 of the groove 66.
  • the spring 33 urges the contact lip portion 48 axially away from the radial wall 36 of the case 26 and also radially toward the axis X. It thus ensures that the contact lip portion 48 at its radial edge 56 remains against the axial wall 38 of the shield 28 and at its axial edge 58 remains against the radial wall 36 of the shield 28. Even so, the spring 33 has a positive offset R, meaning that the cross- sectional center around which its convolutions spiral is displaced laterally from the radial edge 56 toward the mounting portion 46.
  • the secondary seal element 32 is bonded to outer axial wall 44 of the shield 28 and establishes a dynamic fluid barrier along the axial wall 34 of the case 26 (Fig. 2). To this end, it is provided with a lip 80 which projects obliquely toward the axial wall 34 of the case 26 and contacts the inner surface of the axial wall 34 near the free end of that wall. As such the lip 80 projects generally away from the radial wall 36 of the case 26.
  • the secondary seal element 32 also extends along the free end of the outer axial wall 44 of the shield 28, it being bonded to wall 44 along this end edge as well.
  • the seal element 32 has bumper segments 82 which project beyond the end of the wall 44 toward the radial wall 36 of the case 26.
  • the bumper segments 82 form an axial extension of the outer axial wall 44 on the shield 28.
  • the radial wall 40 of the shield 28 lies generally flush with the free end of the axial wall 34 for the case 26.
  • the bumper segments 82 serve to axially position the shield 28 with respect to the case 26, and this ensures that the contact lip portion 48 assumes the correct position with respect to the radial wall 40 of the shield 28.
  • the shield 28 rotates within the case 26 or the case 26 rotates around the shield 28, depending on whether the cup 2 or the cone 4 is the rotating component of the bearing A.
  • grease within the annular space 22 that represents the interior of the bearing A will migrate toward and against the mounting portion 46, but the labyrinth created by the relatively small gap between the inner surface 52 of the mounting portion 46 and the axial wall 38 of the shield 28 retards further migration along the axial wall 38.
  • the wedge-shaped cavities 54 enable the mounting portion 46 to actually drive the grease back into the annular space 22.
  • the surfaces of the cavities 54 lie oblique to the direction of relative movement between the case 26 and shield 28 and deflect the grease generally axially into the annular space 22. So the labyrinth formed by the mounting portion 46 establishes the initial fluid barrier insofar as the grease is concerned.
  • the contact lip portion 48 under the natural bias of the elastomer from which it is molded bears against the axial wall 38 of the shield 28 along the radial edge 56 and also bears against the radial wall 40 along the axial edge 58.
  • the former creates a fluid barrier in the form of a radial lip seal, while the latter creates another fluid barrier in the form of a face seal.
  • face seals are more difficult to sustain with the natural bias of an elastomer than are radial seals.
  • the garter spring 33 urges the end of the contact lip portion 48 both axially away from the radial wall 36 of the case 26 and radially inwardly toward the axis X.
  • the spring 33 bears against the oblique side face 70 of the groove 66 radially outwardly from the axial edge 58, so even if the elastomer looses some of its resiliency, the spring 33 will continue to urge the axial edge 58 against the radial wall 40 of the shield 28 and the radial edge 56 against the axial wall 38 as well.
  • the lip portion 48 at its radial edge 56 and axial edge 58 remains in contact with the axial wall 38 and radial wall 40, respectively, of the shield 28, even after the lip portion 48 has experienced considerable wear in the region of the two edges 56 and 58.
  • the lip portion 48 along the edges 56 and 58 establishes two more dynamic fluid barriers between the case 26 and shield 28.
  • the oblique lip 80 of the secondary seal element 32 establishes still another dynamic fluid barrier between the shield 28 and case 26. It serves primarily to exclude contaminants from the annular space 22 within the bearing A and is indeed exposed to the exterior of the bearing A where it is the first of the several fluid barriers contaminants must pass before reaching the annular space 22 within the bearing A.
  • the bumper segments 82 while serving primarily to position the shield 28 in the proper axial location with respect to the case 26, also function as a labyrinth and in that sense form yet another dynamic fluid barrier between the case 26 and the shield 28.
  • a modified seal C (Fig. 4) is quite similar to the seal B, in that it has a case 26, a shield 28, a primary seal element 30 and a secondary seal element 32. While the primary seal element 30 possesses a mounting portion 46, having an inner surface 52 that is close to axial wall 38 of the shield 28, it does not contain pumping cavities 54 and thus lacks the capacity to pump grease toward the annular space 22 in which the tapered rollers 6 are located. Even so, the inner surface 52 of the mounting portion 46 creates a labyrinth along the axial wall 38 of the shield 28. Also, the shield 28 lacks an outer axial wall 44, but instead outwardly terminates at a free edge on the radial wall 40.
  • the outer seal element 32 is bonded to the radial wall 40 in this region, and does not possess bumper segments 82. Owing to the absence of the pumping cavities 54, the primary seal element 30 for the seal C in the region of its mounting portion 46 need not be as long as the mounting portion 46 for the seal B, and as a consequence, the seal C may be somewhat shorter than the seal B, that is to say it may be manufactured with a lesser axial dimension.
  • FIG. 5 Another modified seal D (Fig. 5) is likewise quite similar to the seal B. As such, it includes a case 26, a shield 28 and a elastomeric seal element 30. It does not have a secondary seal element 32. Instead, the outer axial wall 44 of the shield 28 is formed out-of-round or eccentric to the inner axial wall 38 and to the axial wall 34 of the case 26 as well. The out-of-round or eccentric character of the outer axial wall 44 enables it to pump contaminants, primarily water, both into and out of the space generally enclosed by the case 26 and shield 28. The water that is pumped into the space eventually fills it.
  • the first seal barrier formed along the axial edge 58 of the contact lip 48 prevents the water from advancing further through the seal D, and all water which encounters the seal afterwards is simply directed away. When the bearing A comes to rest, the water held in the space between the case 26 and shield 28 drains from that space.
  • the construction and operation of a seal with an out-of-round or eccentric outer axial wall 44 on its shield 28 are explained in greater detail in U.S. Patent Application 08/719,723 filed September 25, 1996 for the invention of Dennis L. Otto entitled Seal with Pumping Capabilities.
  • the seal element 30 for the seal D resembles the seal element 30 for the seal B, and in addition includes a rib 84 which projects from the radial wall 36 of the case 26 and lies within the outer axial wall 44 of the shield 28. It serves to create a labyrinth and in that sense establishes another dynamic barrier for contaminants. But the rib 84 may be omitted to reduce the radial dimension of the seal D.
  • Still another modified seal E (Fig. 6) closely resembles the seal C, except that the primary seal element 30 in its lip portion 48 has distinct contact lips 86 and 88. The lip 86 projects radially toward the axial wall 38 of the shield 28 and the radial edge 56 exists on it. Here the lip 86 actually contacts the axial wall 38 of the shield 28.
  • the lip 88 projects axially toward the radial wall 40 and carries the edge 58 along which it contacts the radial wall 40.
  • the groove 66 in the seal element 30 of the seal positions the spring 33 that it retains such that the spring 33 has a positive offset R and also such that the spring 33 bears against the side faces 70 and 72 of the groove 66 radially outwardly from axial edge 58 on the axial lip 88.
  • the garter spring 33 is conventional and as such constitutes a wire wound into convolutions and joined together at its ends so that the spring 33 assumes a circular configuration. It may be expanded to greater diameters, but always seeks to revert to its smallest diameter.
  • Other resilient elements may be used in lieu of the spring 33.
  • a resilient band formed from an elastomer may be substituted for the spring 33.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sealing Of Bearings (AREA)

Abstract

Cette invention se rapporte à un joint d'étanchéité servant à fermer un espace annulaire compris entre deux éléments mécaniques, tels que les chemins de roulement d'un palier antifriction. Ce joint d'étanchéité comprend un boîtier (26) qui est comprimé dans l'élément mécanique extérieur et un blindage (28) qui est comprimé sur l'élément mécanique intérieur et possède des parois axiales (38, 44) et radiales (40, 42). Le boîtier (26) porte un élément d'étanchéité élastomère (30) qui établit de multiples barrières antifluides le long du blindage (28). A cet effet, l'élément d'étanchéité (30) comporte une partie de montage (46) qui repose le long de la paroi axiale (42) du blindage (28), créant ainsi un labyrinthe dont la fonction est améliorée par des cavités de pompage en forme de coin (54). L'élément d'étanchéité (30) comporte également une partie lèvre de contact (48) fixée à la partie de montage au niveau d'une rainure (66) qui débouche généralement à l'opposé de l'axe. Cette partie lèvre possède deux bords, à savoir un premier bord orienté radialement le long de la paroi axiale du blindage et un second bord orienté axialement le long de la paroi radiale. La rainure (66) contient un ressort cylindrique en anneaux (33) qui s'appuie contre les parois latérales (70, 72) de la rainure (66) tout en restant à distance de la paroi inférieure. Ce ressort (33), dont le centre de la section transversale est décalé par rapport au bord radial en direction de la partie de montage, pousse le bord orienté axialement contre la paroi radiale du blindage et le bord orienté radialement contre la paroi axiale, établissant ainsi deux barrières antifluides dynamiques supplémentaires. Un autre élément d'étanchéité élastomère (32) peut être lié au blindage (28) et possède une lèvre (80) en contact avec le boîtier (26), formant ainsi une autre barrière antifluide dynamique supplémentaire.
PCT/US1997/022453 1996-12-10 1997-12-09 Joint d'etancheite sollicite par ressort WO1998026202A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU78489/98A AU7848998A (en) 1996-12-10 1997-12-09 Spring-biased seal

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US76322096A 1996-12-10 1996-12-10
US08/763,220 1996-12-10

Publications (1)

Publication Number Publication Date
WO1998026202A1 true WO1998026202A1 (fr) 1998-06-18

Family

ID=25067209

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US1997/022453 WO1998026202A1 (fr) 1996-12-10 1997-12-09 Joint d'etancheite sollicite par ressort

Country Status (2)

Country Link
AU (1) AU7848998A (fr)
WO (1) WO1998026202A1 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005019192A1 (de) * 2004-05-21 2005-12-08 Aktiebolaget Skf Dichtvorrichtung für ein Wälzlager
US8061903B2 (en) 2010-01-28 2011-11-22 Rexnord Industries, Llc Bearing assembly with extended maintenance interval
CN102562817A (zh) * 2012-02-28 2012-07-11 洛阳轴研科技股份有限公司 轴承低速重载工况下所使用的组合式密封装置设计方法
US8740464B2 (en) 2011-11-02 2014-06-03 Rexnord Industries, Llc Bearing assembly having a floating seal
FR3039865A1 (fr) * 2015-08-05 2017-02-10 Ntn-Snr Roulements Assemblage a roulement, essieu de vehicule comprenant un tel assemblage a roulement et procede pour monter un assemblage a roulement
CN110410503A (zh) * 2018-07-13 2019-11-05 河南蒲瑞精密机械有限公司 一种自调弹簧压紧力的减压油封
CN110410503B (zh) * 2018-07-13 2024-05-17 河南蒲瑞精密机械有限公司 一种自调弹簧压紧力的减压油封

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3739513A1 (de) * 1987-11-21 1989-06-01 Kaco Gmbh Co Dichtung
EP0508013A1 (fr) * 1988-12-27 1992-10-14 The Timken Company Eléments d'étanchéité pour paliers
US5553870A (en) * 1994-02-16 1996-09-10 The Timken Company Lip seal separating oil and grease
WO1997016662A1 (fr) * 1995-10-31 1997-05-09 The Timken Company Joint a cloisons multiples

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3739513A1 (de) * 1987-11-21 1989-06-01 Kaco Gmbh Co Dichtung
EP0508013A1 (fr) * 1988-12-27 1992-10-14 The Timken Company Eléments d'étanchéité pour paliers
US5553870A (en) * 1994-02-16 1996-09-10 The Timken Company Lip seal separating oil and grease
WO1997016662A1 (fr) * 1995-10-31 1997-05-09 The Timken Company Joint a cloisons multiples

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005019192A1 (de) * 2004-05-21 2005-12-08 Aktiebolaget Skf Dichtvorrichtung für ein Wälzlager
DE102005019192B4 (de) * 2004-05-21 2015-05-13 Aktiebolaget Skf Dichtvorrichtung für ein Wälzlager
US8061903B2 (en) 2010-01-28 2011-11-22 Rexnord Industries, Llc Bearing assembly with extended maintenance interval
US8740464B2 (en) 2011-11-02 2014-06-03 Rexnord Industries, Llc Bearing assembly having a floating seal
CN102562817A (zh) * 2012-02-28 2012-07-11 洛阳轴研科技股份有限公司 轴承低速重载工况下所使用的组合式密封装置设计方法
FR3039865A1 (fr) * 2015-08-05 2017-02-10 Ntn-Snr Roulements Assemblage a roulement, essieu de vehicule comprenant un tel assemblage a roulement et procede pour monter un assemblage a roulement
CN110410503A (zh) * 2018-07-13 2019-11-05 河南蒲瑞精密机械有限公司 一种自调弹簧压紧力的减压油封
CN110410503B (zh) * 2018-07-13 2024-05-17 河南蒲瑞精密机械有限公司 一种自调弹簧压紧力的减压油封

Also Published As

Publication number Publication date
AU7848998A (en) 1998-07-03

Similar Documents

Publication Publication Date Title
US4799808A (en) Compact seal
US5024449A (en) Seal assembly for use with an overhang
EP0303359B1 (fr) Joint d'étanchéité
US5022659A (en) Seal assembly for antifriction bearings
US5129744A (en) Two component bearing seal with bumpers
JPH0663541B2 (ja) 軸受シール装置
US6485185B1 (en) Bearing seal
US4497495A (en) Unitized wheel bearing seal with multiple lips
US5908249A (en) Bearing assembly having compact and efficient seal arrangement
MX2010011142A (es) Sello de cojinete de rodillos.
US4502739A (en) Roller bearing seal
US5944161A (en) End cap assembly for a roller tube of a conveyor roller
US7628541B2 (en) Sealing device for a wheel hub unit
US5207436A (en) Low friction unitized seal
US5722664A (en) Seal with pumping capabilities
US4960335A (en) Unitary enclosure and cover therefor
US4304412A (en) Contoured double-lip bearing seal
JP2018054095A (ja) 密封装置
WO1998026202A1 (fr) Joint d'etancheite sollicite par ressort
US4664538A (en) Sealed bearing assembly
JPS60231015A (ja) 自動調心ころがり軸受のシール装置
US6913264B2 (en) Sealing arrangement
US4932796A (en) Thrust bearing sealing collar assembly
US3838898A (en) Combined grease seal-dirt shield
KR20170126528A (ko) 수분 유입 방지용 고무가 부착된 플링거가 구비된 휠 베어링

Legal Events

Date Code Title Description
AK Designated states

Kind code of ref document: A1

Designated state(s): AL AM AT AU AZ BA BB BG BR BY CA CH CN CU CZ DE DK EE ES FI GB GE GH HU ID IL IS JP KE KG KP KR KZ LC LK LR LS LT LU LV MD MG MK MN MW MX NO NZ PL PT RO RU SD SE SG SI SK SL TJ TM TR TT UA UG US UZ VN YU ZW AM AZ BY KG KZ MD RU TJ TM

AL Designated countries for regional patents

Kind code of ref document: A1

Designated state(s): GH GM KE LS MW SD SZ UG ZW AT BE CH DE DK ES FI FR GB GR IE IT LU

DFPE Request for preliminary examination filed prior to expiration of 19th month from priority date (pct application filed before 20040101)
121 Ep: the epo has been informed by wipo that ep was designated in this application
REG Reference to national code

Ref country code: DE

Ref legal event code: 8642

122 Ep: pct application non-entry in european phase