CA2102472C - Seal arrangement - Google Patents
Seal arrangement Download PDFInfo
- Publication number
- CA2102472C CA2102472C CA002102472A CA2102472A CA2102472C CA 2102472 C CA2102472 C CA 2102472C CA 002102472 A CA002102472 A CA 002102472A CA 2102472 A CA2102472 A CA 2102472A CA 2102472 C CA2102472 C CA 2102472C
- Authority
- CA
- Canada
- Prior art keywords
- seal arrangement
- ring
- leg
- shaft
- stiffening
- Prior art date
- Legal status (The legal status 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 status listed.)
- Expired - Fee Related
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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
- F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
- F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
- F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
- F16C35/07—Fixing them on the shaft or housing with interposition of an element
- F16C35/077—Fixing them on the shaft or housing with interposition of an element between housing and outer race ring
-
- 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
- F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
- F16C27/06—Elastic or yielding bearings or bearing supports, for exclusively rotary movement by means of parts of rubber or like materials
- F16C27/066—Ball or 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/72—Sealings
- F16C33/76—Sealings of ball or roller bearings
- F16C33/768—Sealings of ball or roller bearings between relatively stationary parts, i.e. static seals
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/72—Sealings
- F16C33/76—Sealings of ball or roller bearings
- F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
- F16C33/7886—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted outside the gap between the inner and outer races, e.g. sealing rings mounted to an end face or outer surface of a race
-
- 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
- F16J15/3204—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip
- F16J15/3224—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip capable of accommodating changes in distances or misalignment between the surfaces, e.g. able to compensate for defaults of eccentricity or angular deviations
-
- 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
-
- 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
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
- F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
Abstract
Seal arrangement for the sealing of a rotatable shaft extending through a bore in a housing wall includes a seal ring which has at least one sealing lip of elastomeric material for sealingly engaging the shaft along its outer circumference, first and second stiffening rings, an elastic intermediate coating and an anti-friction bearing. The first stiffening ring is L-shaped in cross-section with a radially outwardly directed first leg and an axially extending second leg. The anti-friction bearing is fitted in radial direction between the shaft and the second leg.
The sealing lip is fixed to the first leg. The second leg at least partly overlaps and tightly engages an outer ring of the anti-friction bearing and is surrounded on the side directed towards the bore wall by the second stiffening ring. The inner ring of the anti-friction bearing is supported on the shaft and the outer ring is retained by the second leg. The coating is made of an elastic, rubbery material which extends intermediate the first and second stiffening rings and over the second leg extends in radial and axial direction beyond the second stiffening ring subsequent to manufacture for improved sealing at the bore wall. That portion of the coating which extends in radial direction beyond the second stiffening ring subsequent to manufacture is compressed upon insertion of the seal arrangement into the bore.
The second stiffening ring is radially stressed so that it forces against the bore wall to retain the seal arrangement in the bore by friction during the intended use. The seal arrangement has improved operating characteristics over a long service period, improves the guiding of the shaft in the region of the seal and provides for the insulation/damping of vibrations of the rotating shaft during use.
The sealing lip is fixed to the first leg. The second leg at least partly overlaps and tightly engages an outer ring of the anti-friction bearing and is surrounded on the side directed towards the bore wall by the second stiffening ring. The inner ring of the anti-friction bearing is supported on the shaft and the outer ring is retained by the second leg. The coating is made of an elastic, rubbery material which extends intermediate the first and second stiffening rings and over the second leg extends in radial and axial direction beyond the second stiffening ring subsequent to manufacture for improved sealing at the bore wall. That portion of the coating which extends in radial direction beyond the second stiffening ring subsequent to manufacture is compressed upon insertion of the seal arrangement into the bore.
The second stiffening ring is radially stressed so that it forces against the bore wall to retain the seal arrangement in the bore by friction during the intended use. The seal arrangement has improved operating characteristics over a long service period, improves the guiding of the shaft in the region of the seal and provides for the insulation/damping of vibrations of the rotating shaft during use.
Description
51 a . j .5 id ~:l ~ s,I
SEAL ARRANGEMENT
The invention relates to seal arrangements for the sealing of a rotatable shaft extending through a bore in a housing wall.
One class of conventional shaft seal arrangements include a radially sealing seal ring and a first stiffening ring of essentially L-shaped cross-section.
The seal ring has at least one sealing lip which is made of elastic, rubbery material and sealingly engages the circumference of the shaft to be sealed under radial pretension. The first stiffening ring is L-shaped in cross-section with a first leg which extends radially inward and a second leg which extends parallel to the axis of the shaft. The second leg at least partly overlaps and engages the outer ring of an anti-friction bearing positioned between the shaft and the second leg. The seal ring is fixed to the first leg. The second leg is enclosed by elastic material at least on the side facing the bore wall and is fixable in the bore by radial prestressing.
A seal of that type is known from German Utility Model DE-GM 19 17 623. That seal arrangement is constructed as a tolerance ring for the mounting of anti-friction bearings in seal receiving housings. If, for example, the housing is made of aluminum and the anti-friction bearing is made of steel, variations in the clearance between the housing and the bearing ring, for example due to heat, are compensated by the elastic, rubbery material. The dimensions and type of the elastic material are thereby selected according to the clearance range which is to be compensated. However, sealing problems are observed with this type of seal especially when used in conjunction with shafts which do not rotate optimally round, for example drive shafts of automative transmissions. Thus, the sealing of shafts which are vibrating or rotate out of round is not satisfactory. Furthermore, although the elastic, rubbery coating of the tolerance ring is radially prestressed and, thus, is radially forced against the bore in the housing, the bore wall is provided with a specific surface structure to reliably prevent displacements of the tolerance ring in axial direction, which surface structure interlocks with the coating. However, the manufacture of a bore of such construction is not economical.
It is now an object of the present invention to provide a further 9~ ~ t ~ .:l ~J ~~it 0 N
SEAL ARRANGEMENT
The invention relates to seal arrangements for the sealing of a rotatable shaft extending through a bore in a housing wall.
One class of conventional shaft seal arrangements include a radially sealing seal ring and a first stiffening ring of essentially L-shaped cross-section.
The seal ring has at least one sealing lip which is made of elastic, rubbery material and sealingly engages the circumference of the shaft to be sealed under radial pretension. The first stiffening ring is L-shaped in cross-section with a first leg which extends radially inward and a second leg which extends parallel to the axis of the shaft. The second leg at least partly overlaps and engages the outer ring of an anti-friction bearing positioned between the shaft and the second leg. The seal ring is fixed to the first leg. The second leg is enclosed by elastic material at least on the side facing the bore wall and is fixable in the bore by radial prestressing.
A seal of that type is known from German Utility Model DE-GM 19 17 623. That seal arrangement is constructed as a tolerance ring for the mounting of anti-friction bearings in seal receiving housings. If, for example, the housing is made of aluminum and the anti-friction bearing is made of steel, variations in the clearance between the housing and the bearing ring, for example due to heat, are compensated by the elastic, rubbery material. The dimensions and type of the elastic material are thereby selected according to the clearance range which is to be compensated. However, sealing problems are observed with this type of seal especially when used in conjunction with shafts which do not rotate optimally round, for example drive shafts of automative transmissions. Thus, the sealing of shafts which are vibrating or rotate out of round is not satisfactory. Furthermore, although the elastic, rubbery coating of the tolerance ring is radially prestressed and, thus, is radially forced against the bore in the housing, the bore wall is provided with a specific surface structure to reliably prevent displacements of the tolerance ring in axial direction, which surface structure interlocks with the coating. However, the manufacture of a bore of such construction is not economical.
It is now an object of the present invention to provide a further 9~ ~ t ~ .:l ~J ~~it 0 N
developed seal arrangement of the above described general type which has substantially improved sealing characteristics over a long service period, provides for the installation/damping of vibrations of the rotating shaft, and reliably prevents axial displacement of the seal in relation to the housing.
S This object is achieved with a seal arrangement in accordance with the invention wherein the coating of the first stiffening ring on the side facing the housing is surrounded at least in a portion of its extent parallel to the shaft's axis (axial portion) by a second stiffening ring made of tough and hard material and an intermediate coating, which second stiffening ring is at least partly radially prestressed and forces against the bore wall during use. The coating outside the axial portion extends in radial direction beyond the second stiffening ring subsequent to manufacture. The type of elastic, rubbery material used and its thickness depend on the parameters of the respective application.
Accordingly, the invention provides a seal axrangement for the sealing of 1 S a shaft extending through a shaft receiving bore in a housing wall, including a radially sealing seal ring, first and second stiffening rings with an intermediate elastic coating and an anti-friction bearing. The seal ring has an annular main sealing lip made of elastic, rubbery material which is radially biased by the shaft during use to sealingly engage the outer circumference of the shaft. The first stiffening ring is L-shaped in cross-section and has a radially inwardly directed first leg and a second leg extending parallel to the axis of the shaft.
The sealing lip is fixed to the first leg of the first stiffening ring. The second leg at least partly overlaps and engages the outer ring of the anti-friction bearing, and is surrounded in at least a portion of its axial extent (axial portion) and on the side directed toward the bore wall by the second stiffening ring.
The seal is fixable in the bore by radial prestressing. The anti-friction bearing . .
is positioned in radial direction between the shaft and the second leg of the first stiffening ring. Outside the axial portion, the coating extends in axial and radial direction beyond the second stiffening zing subsequent to manufacture.
When the shaft to be sealed is rotating out of round, a significant reduction in acoustically prominent vibrations of the shaft is achieved and propagation of this unwanted noise is substantially prevented. The seal ring preferably a t.J ~ ~ ~~ ~ N
S This object is achieved with a seal arrangement in accordance with the invention wherein the coating of the first stiffening ring on the side facing the housing is surrounded at least in a portion of its extent parallel to the shaft's axis (axial portion) by a second stiffening ring made of tough and hard material and an intermediate coating, which second stiffening ring is at least partly radially prestressed and forces against the bore wall during use. The coating outside the axial portion extends in radial direction beyond the second stiffening ring subsequent to manufacture. The type of elastic, rubbery material used and its thickness depend on the parameters of the respective application.
Accordingly, the invention provides a seal axrangement for the sealing of 1 S a shaft extending through a shaft receiving bore in a housing wall, including a radially sealing seal ring, first and second stiffening rings with an intermediate elastic coating and an anti-friction bearing. The seal ring has an annular main sealing lip made of elastic, rubbery material which is radially biased by the shaft during use to sealingly engage the outer circumference of the shaft. The first stiffening ring is L-shaped in cross-section and has a radially inwardly directed first leg and a second leg extending parallel to the axis of the shaft.
The sealing lip is fixed to the first leg of the first stiffening ring. The second leg at least partly overlaps and engages the outer ring of the anti-friction bearing, and is surrounded in at least a portion of its axial extent (axial portion) and on the side directed toward the bore wall by the second stiffening ring.
The seal is fixable in the bore by radial prestressing. The anti-friction bearing . .
is positioned in radial direction between the shaft and the second leg of the first stiffening ring. Outside the axial portion, the coating extends in axial and radial direction beyond the second stiffening zing subsequent to manufacture.
When the shaft to be sealed is rotating out of round, a significant reduction in acoustically prominent vibrations of the shaft is achieved and propagation of this unwanted noise is substantially prevented. The seal ring preferably a t.J ~ ~ ~~ ~ N
includes a garter spring which evenly forces the sealing lip against the shaft for improved sealing results. The second stiffening ring which, for example, may be made of metal provides for a reliable fixing of the seal arrangement in the housing wall since it is radially prestressed, which means that the second stiffening ring is forced in radial direction against the bore wall, which results in friction between the second stiffening ring and the bore wall. Axial displacements of the whole seal arrangement in the bore are prevented with this construction even when the shaft to be sealed moves in axial direction during rotation and/or is subject to heat expansion. Thus, the seal arrangement is first pressed into the bore in the housing wall during installation and the frictionally retained therein during the intended use. For the achievement of an excellent sealing of the housing, the coating of the first stiffening ring autside the axial portion extends in radial direction around and beyond the second stiffening ring and is compressed between the housing wall to be sealed and the first stiffening ring in the installed condition of the seal. It is an advantage of such a construction that an excellent guiding of the shaft to be sealed is achieved by the supported anti-friction bearing, that, simultaneously, vibrations of the shaft are insulated/dampened and that an excellent spatial positioning of the seal between the bore wall and the shaft is achieved even over a long service period. The propagation of vibration noise to the surrounding structures is minimized. The coating may be vulcanized onto the second stiffening ring or adhesively connected thereto. Such a fastening of the two parts to each other is exceptionally reliable and generally remains intact even over a long service period. The second stiffening ring is preferably L-shaped in cross-section, which is advantageous from a manufacturing technology standpoint and simplifies installation. The second stiffening ring has a radially protruding flange for engagement with a radially extending surface of the housing. The manufacture is simplified especially when the coating is vulcanized onto the second stiffening ring. The installation and exact positioning of the seal in the bore is simplified by the radially protruding flange, since the seal is simply pressed in axial direction into the bore until the radial flange of the second stiffening ring comes to rest against the housing wall.
H~ ~x ~~
H~ ~x ~~
Depending on the parameters of the respective application, the radial flange of the second stiffening ring may be enclosed by an elastic material which may be an integral part of the coating and may have an axially protruding annular sealing lip on the side facing the wall. Leakage between the seal and the bore wall is practically prevented with this construction. The annular sealing lip and/or radially protruding sealing ridges provided on a portion of the coating engaging the bore wall reliably retain the liquid to be sealed in the space to be sealed. The second stiffening ring and the first stiffening ring are preferably concentrical, whereby the coating extends therebetween. Vibration insulation or damping is optimized and noise propagation minimized when the coating between the two stiffening rings has a radial thickness of 0.7 to 3 millimeters, preferably 0.8 to L5 millimeter.
This coating thickness is especially well suited for most applications and provides a good compromise between a small seal diameter and an effective vibration insulation/damping.
In another preferred embodiment, the second leg has an offset profile with a portion of relatively larger diameter and a portion of relatively smaller diameter. The portion of larger diameter at least partly surrounds the outer ring of the anti-friction bearing, and the portion of smaller diameter is positioned radially inwardly of the second stiffening ring, whereby the intermediate layer of elastic coating extends between that portion and the second stiffening ring. It is an advantage of this embodiment that the seal arrangement has an especially small diameter. In addition, a coating around the first stiffening ring of substantially constant thickness is achieved, so that unwanted accumulations of material are avoided. Furthermore, the portion of smaller diameter is used for improved support of the outer bearing ring in axial direction so that an exact positioning of the anti-friction bearing within the seal is achieved.
The coating preferably includes at least two axially spaced apart sealing ridges on the surface facing the bore wall. These sealing ridges provide for a static sealing. Depending on the pressure and the viscosity of 'the medium to be sealed, a large number of sealing ridges may be positioned in series parallel hl to the shaft's axis to form a labyrinth, so that a good static seal is reliably achieved. The seal ring may be provided with an auxiliary sealing lip which is axially spaced apart from the main sealing lip, surrounds the shaft and is located on that side of the main sealing lip which is remote from the medium 5 to be sealed so that the main sealing lip, the auxiliary sealing lip and the shaft define a hollow chamber. This chamber may be filled with grease during use of the seal for improvement of its operating characteristics over an extended period of time. The auxiliary sealing lip which acts as serial seal and the grease filled chamber keep dirt away from the main sealing lip which dirt would otherwise reduce the service period of the main sealing lip. It is especially advantageous that a shaft seal in accordance with the invention may be used even under extremely tough operating conditions.
The invention will now be further described by way of example only and with reference to the attached drawings, wherein:
Figure 1 shows a seal arrangement which includes a first stiffening ring having a straight, axially extending second leg and a flange which is coated at its radial end by an elastic material, whereby the elastic material is an integral part of the coating;
Figure 2 illustrates a seal similar to the embodiment shown in Figure 1, whereby the second leg has an offset profile, the second stiffening ring is not completely coated at its radial end, and the overall diameter of the seal is smaller; and Figure 3 shows a seal arrangement which includes some features of both seal arrangements illustrated in Figures 1 and 2. The radial flange of the second ring is at its outer end coated with an elastic, rubbery material, whereby the elastic material includes an annular sealing lip which protrudes towards the housing. Furthermore, the second stiffening ring has an offset profile in axial direction.
Figures 1 and 2 show preferred embodiments of a seal arrangement for the sealing of a shaft 2 which extends through a bore 1.1 in a housing 1. The seal arrangement essentially includes a radially sealing seal ring 3, first and second stiffening rings 6 and 11 and an integrated anti-friction bearing 9 s1 t ;~~~~!~ a having inner and outer rings 8 and 22. The seal ring 3 statically seals the bore 1.1 and dynamically seals the shaft 2 which rotates relatively to the housing I.
Static sealing at the bore wall is achieved by sealing ridges 15, 16 (see Fig.
2).
In the depicted embodiments, the dynamic sealing of the shaft 2 is achieved with a main sealing lip 4, and an auxiliary sealing lip 19 which sealingly engage the shaft 2 to be sealed along its circumference. The auxiliary sealing lip 19 is axially spaced apart from the main sealing lip 4 and positioned on that side of the main sealing lip remote from the medium to be sealed 20. The main sealing lip 4, the shaft 2 and the auxiliary sealing lip 19 together define a hollow chamber 21 which may be filled with grease for protection of the main sealing lip 4. A garter spring 25 is provided which evenly forces the main sealing lip 4 against the shaft 2 for improved sealing results. In both embodiments, the first stiffening ring 6 is L-shaped in cross-section with a radially extending first leg 5 and an axially extending second leg 7 which overlaps and tightly engages the outer ring 8 of the bearing 9. The inner ring 22 of the anti-friction bearing 9 is xetained on the shaft and the outer ring 8 is held by the second flange 7 of the first stiffening ring 6. A coating 10 of elastic, rubbery material is provided between the first and second stiffening rings 6, 11, which coating is constructed so that heat generated clearance variations observed during the intended use of the seal arrangement are compensated. Simultaneously, the seal arrangement in accordance with the invention provides good support for the rotating shaft 2 and a vibration insulation/damping with simultaneous reduction in noise propagation. To achieve a reliable spatial fixation of the seal arrangement in the gap between the bore wall 1.1 and the shaft 2, the second stiffening ring 11 is made of a ;.
tough, hard material and is constructed so that it is radially stressed when inserted into the housing and, thus, radially outwardly forces against the bore wall along its outer circumference. Consequently, the second stiffening ring and with it the whole seal arrangement is frictionally retained in the bore 1.1.
The sealing in this region is achieved in that the coating extends in radial direction beyond the second stiffening ring subsequent to manufacture and is radially compressed between the bore wall and the first stiffening ring 6 upon n f.':
~'1.',:' insertion of the seal into the bore 1.1. The axially extending second leg 7 of the first stiffening ring 6 shown in Figure 1 is straight. The second stiffening ring 11 and the first stiffening ring 6 are of substantially the same axial length.
At the axial end 23 of the second leg 7 the coating 10 extends in radial direction around and slightly beyond the second stiffening ring 11 so that a ~ reliable sealing of the medium to be sealed 20 in the space to be sealed is guaranteed in that region during the intended use. In addition, the radially outwardly projecting flange 12 of the second stiffening ring 11 is surrounded by a coating of elastic, rubbery material which forms an integral part of the coating 10 in this embodiment. The seal arrangement is reliably retained in the bore 1.1 by friction between the outer circumferential surface of the second stiffening ring 11 and the wall of the bore 1.1. The annular sealing lip 14 provides additional safety with respect to the sealing of the housing and seals the gap between the radially projecting flange 12 of the second stiffening ring 11 and the radial surface 13 of the housing 1.
In Figure 2, the second leg 7 of the first stiffening ring 6 has an offset profile and first and second portions 17 and 18. The first portion 17 is of relatively larger diameter and overlaps and tightly engages the outer ring 8 of the anti-friction bearing 9. The second portion 18 is of relatively small diameter and is positioned radially inward from the second stiffening ring 11 with the radially intermediate coating 10 extending therebetween. It is an advantage that the thickness of coating 10 is substantially constant, so that undesired accumulations of material are prevented. This is especially advantageous from a production technology standpoint. As in the embodiment of Figure 1, the friction connection for the retaining of the seal arrangement is formed between the wall of, the bore 1.1 and the second stiffening ring 11 which is shorter in axial direction than the second stiffening ring shown in Figure 1. In this embodiment, the coating 10 also extends in radial direction beyond the second stiffening ring 11 so that reliable sealing of the medium to be sealed 20 is achieved. The coating in that region is provided with spaced apart parallel sealing ribs 15, 16 which form a labyrinth. The integral radial flange 12 of the second stiffening ring 11 provides for an exact positioning of ~ ~ , ,, , .
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the seal arrangement in the bore 1.1 and directly engages the housing 1 with no intermediate coating.
The embodiment of Figure 3 incorporates a combination of the advantageous features of the embodiments shown in Figures 1 and 2. The radial flange 12 is surrounded by an elastic coating having an integral annular sealing lip 14 which sealingly engages the radially extending surface 13 of the housing 1. Because the second stiffening ring 11 has an offset profile, the diameter of this seal arrangement is smaller than the one shown in Figure I.
As in the other embodiments, the seal is retained in the bore 1.1 by friction between the second stiffening ring and the bore wall.
This coating thickness is especially well suited for most applications and provides a good compromise between a small seal diameter and an effective vibration insulation/damping.
In another preferred embodiment, the second leg has an offset profile with a portion of relatively larger diameter and a portion of relatively smaller diameter. The portion of larger diameter at least partly surrounds the outer ring of the anti-friction bearing, and the portion of smaller diameter is positioned radially inwardly of the second stiffening ring, whereby the intermediate layer of elastic coating extends between that portion and the second stiffening ring. It is an advantage of this embodiment that the seal arrangement has an especially small diameter. In addition, a coating around the first stiffening ring of substantially constant thickness is achieved, so that unwanted accumulations of material are avoided. Furthermore, the portion of smaller diameter is used for improved support of the outer bearing ring in axial direction so that an exact positioning of the anti-friction bearing within the seal is achieved.
The coating preferably includes at least two axially spaced apart sealing ridges on the surface facing the bore wall. These sealing ridges provide for a static sealing. Depending on the pressure and the viscosity of 'the medium to be sealed, a large number of sealing ridges may be positioned in series parallel hl to the shaft's axis to form a labyrinth, so that a good static seal is reliably achieved. The seal ring may be provided with an auxiliary sealing lip which is axially spaced apart from the main sealing lip, surrounds the shaft and is located on that side of the main sealing lip which is remote from the medium 5 to be sealed so that the main sealing lip, the auxiliary sealing lip and the shaft define a hollow chamber. This chamber may be filled with grease during use of the seal for improvement of its operating characteristics over an extended period of time. The auxiliary sealing lip which acts as serial seal and the grease filled chamber keep dirt away from the main sealing lip which dirt would otherwise reduce the service period of the main sealing lip. It is especially advantageous that a shaft seal in accordance with the invention may be used even under extremely tough operating conditions.
The invention will now be further described by way of example only and with reference to the attached drawings, wherein:
Figure 1 shows a seal arrangement which includes a first stiffening ring having a straight, axially extending second leg and a flange which is coated at its radial end by an elastic material, whereby the elastic material is an integral part of the coating;
Figure 2 illustrates a seal similar to the embodiment shown in Figure 1, whereby the second leg has an offset profile, the second stiffening ring is not completely coated at its radial end, and the overall diameter of the seal is smaller; and Figure 3 shows a seal arrangement which includes some features of both seal arrangements illustrated in Figures 1 and 2. The radial flange of the second ring is at its outer end coated with an elastic, rubbery material, whereby the elastic material includes an annular sealing lip which protrudes towards the housing. Furthermore, the second stiffening ring has an offset profile in axial direction.
Figures 1 and 2 show preferred embodiments of a seal arrangement for the sealing of a shaft 2 which extends through a bore 1.1 in a housing 1. The seal arrangement essentially includes a radially sealing seal ring 3, first and second stiffening rings 6 and 11 and an integrated anti-friction bearing 9 s1 t ;~~~~!~ a having inner and outer rings 8 and 22. The seal ring 3 statically seals the bore 1.1 and dynamically seals the shaft 2 which rotates relatively to the housing I.
Static sealing at the bore wall is achieved by sealing ridges 15, 16 (see Fig.
2).
In the depicted embodiments, the dynamic sealing of the shaft 2 is achieved with a main sealing lip 4, and an auxiliary sealing lip 19 which sealingly engage the shaft 2 to be sealed along its circumference. The auxiliary sealing lip 19 is axially spaced apart from the main sealing lip 4 and positioned on that side of the main sealing lip remote from the medium to be sealed 20. The main sealing lip 4, the shaft 2 and the auxiliary sealing lip 19 together define a hollow chamber 21 which may be filled with grease for protection of the main sealing lip 4. A garter spring 25 is provided which evenly forces the main sealing lip 4 against the shaft 2 for improved sealing results. In both embodiments, the first stiffening ring 6 is L-shaped in cross-section with a radially extending first leg 5 and an axially extending second leg 7 which overlaps and tightly engages the outer ring 8 of the bearing 9. The inner ring 22 of the anti-friction bearing 9 is xetained on the shaft and the outer ring 8 is held by the second flange 7 of the first stiffening ring 6. A coating 10 of elastic, rubbery material is provided between the first and second stiffening rings 6, 11, which coating is constructed so that heat generated clearance variations observed during the intended use of the seal arrangement are compensated. Simultaneously, the seal arrangement in accordance with the invention provides good support for the rotating shaft 2 and a vibration insulation/damping with simultaneous reduction in noise propagation. To achieve a reliable spatial fixation of the seal arrangement in the gap between the bore wall 1.1 and the shaft 2, the second stiffening ring 11 is made of a ;.
tough, hard material and is constructed so that it is radially stressed when inserted into the housing and, thus, radially outwardly forces against the bore wall along its outer circumference. Consequently, the second stiffening ring and with it the whole seal arrangement is frictionally retained in the bore 1.1.
The sealing in this region is achieved in that the coating extends in radial direction beyond the second stiffening ring subsequent to manufacture and is radially compressed between the bore wall and the first stiffening ring 6 upon n f.':
~'1.',:' insertion of the seal into the bore 1.1. The axially extending second leg 7 of the first stiffening ring 6 shown in Figure 1 is straight. The second stiffening ring 11 and the first stiffening ring 6 are of substantially the same axial length.
At the axial end 23 of the second leg 7 the coating 10 extends in radial direction around and slightly beyond the second stiffening ring 11 so that a ~ reliable sealing of the medium to be sealed 20 in the space to be sealed is guaranteed in that region during the intended use. In addition, the radially outwardly projecting flange 12 of the second stiffening ring 11 is surrounded by a coating of elastic, rubbery material which forms an integral part of the coating 10 in this embodiment. The seal arrangement is reliably retained in the bore 1.1 by friction between the outer circumferential surface of the second stiffening ring 11 and the wall of the bore 1.1. The annular sealing lip 14 provides additional safety with respect to the sealing of the housing and seals the gap between the radially projecting flange 12 of the second stiffening ring 11 and the radial surface 13 of the housing 1.
In Figure 2, the second leg 7 of the first stiffening ring 6 has an offset profile and first and second portions 17 and 18. The first portion 17 is of relatively larger diameter and overlaps and tightly engages the outer ring 8 of the anti-friction bearing 9. The second portion 18 is of relatively small diameter and is positioned radially inward from the second stiffening ring 11 with the radially intermediate coating 10 extending therebetween. It is an advantage that the thickness of coating 10 is substantially constant, so that undesired accumulations of material are prevented. This is especially advantageous from a production technology standpoint. As in the embodiment of Figure 1, the friction connection for the retaining of the seal arrangement is formed between the wall of, the bore 1.1 and the second stiffening ring 11 which is shorter in axial direction than the second stiffening ring shown in Figure 1. In this embodiment, the coating 10 also extends in radial direction beyond the second stiffening ring 11 so that reliable sealing of the medium to be sealed 20 is achieved. The coating in that region is provided with spaced apart parallel sealing ribs 15, 16 which form a labyrinth. The integral radial flange 12 of the second stiffening ring 11 provides for an exact positioning of ~ ~ , ,, , .
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the seal arrangement in the bore 1.1 and directly engages the housing 1 with no intermediate coating.
The embodiment of Figure 3 incorporates a combination of the advantageous features of the embodiments shown in Figures 1 and 2. The radial flange 12 is surrounded by an elastic coating having an integral annular sealing lip 14 which sealingly engages the radially extending surface 13 of the housing 1. Because the second stiffening ring 11 has an offset profile, the diameter of this seal arrangement is smaller than the one shown in Figure I.
As in the other embodiments, the seal is retained in the bore 1.1 by friction between the second stiffening ring and the bore wall.
Claims (11)
1. A seal arrangement for the sealing of a shaft having an axis and extending through a bore in a housing wall, the seal arrangement comprising:
a radially sealing seal ring having an annular elastic main sealing lip for sealing the engaging the shaft under pretension;
first and second stiffening rings;
an elastic coating extending intermediate the first and second stiffening rings;
and an anti-friction bearing;
the first stiffening ring having an L-shaped cross section with a radially inwardly directed first leg and a second leg extending parallel to the axis of the shaft, the sealing ring being fixed to the first leg and the anti-friction bearing having an inner ring for engaging the shaft in an installed condition of the seal arrangement and an outer ring for engaging the second leg;
the second stiffening ring directly engaging a wall of the bore in the installed condition and radially outwardly surrounding at least an axial portion of the second leg, and the intermediate coating being made of an elastic, rubbery material, extending in axial and radial direction beyond the axial portion of the second leg subsequent to manufacture for sealing engagement with the bore wall in the installed condition.
a radially sealing seal ring having an annular elastic main sealing lip for sealing the engaging the shaft under pretension;
first and second stiffening rings;
an elastic coating extending intermediate the first and second stiffening rings;
and an anti-friction bearing;
the first stiffening ring having an L-shaped cross section with a radially inwardly directed first leg and a second leg extending parallel to the axis of the shaft, the sealing ring being fixed to the first leg and the anti-friction bearing having an inner ring for engaging the shaft in an installed condition of the seal arrangement and an outer ring for engaging the second leg;
the second stiffening ring directly engaging a wall of the bore in the installed condition and radially outwardly surrounding at least an axial portion of the second leg, and the intermediate coating being made of an elastic, rubbery material, extending in axial and radial direction beyond the axial portion of the second leg subsequent to manufacture for sealing engagement with the bore wall in the installed condition.
2. A seal arrangement as defined in claim 1, wherein the second stiffening ring and the coating are adhesively connected.
3. A seal arrangement as defined in claim 1, wherein the second stiffening ring is L-shaped in cross-section with a radially projecting flange that is engageable with the housing wall.
4. A seal arrangement as defined in claim 3, wherein the flange at least at its radially outer end is surrounded by an elastic, rubbery material which on the side facing the housing wall includes an axially projecting annular sealing lip.
5. A seal arrangement as defined in claim 1, 2, 3 or 4, wherein the first and second stiffening rings are concentrical.
6. A seal arrangement as defined in claim 1, wherein the intermediate coating provided in radial direction between the first stiffening ring and the second stiffening ring has a thickness of 0.7 to 3 millimeters.
7. A seal arrangement as defined in claim 1, wherein the second leg of the first stiffening ring has an offset profile including a first portion of relatively larger diameter and a second portion of relatively smaller diameter, the first portion overlapping and tightly engaging the outer ring of the anti-friction bearing and the second portion being positioned radially inward of the second stiffening ring with the radially intermediate coating extending therebetween.
8. A seal arrangement as defined in claim 7, wherein that portion of the coating radially and axially extending beyond the second stiffening ring includes at least two spaced apart radially outwardly protruding annular sealing ribs.
9. A seal arrangement as defined in claim 1, further including an auxiliary sealing lip which sealingly engages the shaft, the auxiliary sealing lip being located on that side of the main sealing lip remote from the medium to be sealed, and being spaced apart from the main sealing lip, the main sealing lip, the auxiliary sealing lip and the shaft together defining a hollow chamber.
10. A seal arrangement as defined in claim 9, wherein the hollow chamber is filled with grease during use of the seal arrangement.
11. A seal arrangement as defined in claim 1, wherein the seal ring includes a garter spring for evenly forcing the main sealing lip against the shaft.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DEP4237190.2-12 | 1992-11-04 | ||
| DE4237190A DE4237190C1 (en) | 1992-11-04 | 1992-11-04 | Sealing arrangement |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CA2102472A1 CA2102472A1 (en) | 1994-05-05 |
| CA2102472C true CA2102472C (en) | 2001-01-09 |
Family
ID=6472053
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA002102472A Expired - Fee Related CA2102472C (en) | 1992-11-04 | 1993-11-04 | Seal arrangement |
Country Status (5)
| Country | Link |
|---|---|
| EP (1) | EP0596196B1 (en) |
| JP (1) | JP2513986B2 (en) |
| BR (1) | BR9303655A (en) |
| CA (1) | CA2102472C (en) |
| DE (2) | DE4237190C1 (en) |
Families Citing this family (16)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19513098C2 (en) * | 1995-04-07 | 1997-05-22 | Freudenberg Carl Fa | Sealing arrangement |
| DE19648602C2 (en) * | 1996-11-23 | 2000-01-05 | Freudenberg Carl Fa | Sealing arrangement |
| US6186507B1 (en) | 1997-09-25 | 2001-02-13 | Michael R. Oldenburg | Retrofittable severe duty seal for a shaft |
| US20020011710A1 (en) | 1997-09-25 | 2002-01-31 | Oldenburg Michael R. | Retrofittable severe duty seal for a shaft |
| DE19925121A1 (en) * | 1999-06-01 | 2000-12-21 | Freudenberg Carl Fa | Sealing arrangement |
| DE59901264D1 (en) | 1999-08-31 | 2002-05-23 | Ford Global Tech Inc | Bearing and sealing arrangement for a shaft in a housing bore |
| US6692007B2 (en) | 2001-10-31 | 2004-02-17 | Transcom, Inc. | Seal for a shaft |
| GB2393765A (en) * | 2002-10-01 | 2004-04-07 | Nsk Steering Sys Europ Ltd | Composite bearing seal for a steering column universal joint |
| DE102005004323A1 (en) * | 2005-01-31 | 2006-09-28 | Robert Bosch Gmbh | Sealing element and drive unit containing a sealing element |
| JP2007078108A (en) * | 2005-09-15 | 2007-03-29 | Nok Corp | Sealing device |
| EP2039967B1 (en) * | 2006-07-07 | 2013-02-13 | Eagle Industry Co., Ltd. | Shaft sealing device |
| FR2926247A1 (en) * | 2008-01-14 | 2009-07-17 | Corima Sa | Rear wheel hub for bicycle, has ball bearing forming elastic sliding pivot connection between rotational axle and cassette body via elastomer O-rings, and another ball bearing forming swivel connection between axle and cassette body |
| CN102727119B (en) * | 2011-04-02 | 2016-09-14 | 上海泽生科技开发股份有限公司 | The brush head assembly connection system of appliance for personal care |
| EP2535607B1 (en) * | 2011-06-17 | 2014-04-23 | Aktiebolaget SKF | Turbocharger, notably for a combustion engine |
| ITTO20120651A1 (en) * | 2012-07-25 | 2014-01-26 | Skf Ab | BEARING-HUB ASSEMBLY FOR A DISC FOR WORKING THE EARTH |
| CN111998001A (en) * | 2020-07-13 | 2020-11-27 | 人本股份有限公司 | Shaft coupling bearing seal assembly |
Family Cites Families (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2834616A (en) * | 1955-03-29 | 1958-05-13 | Federal Mogul Bower Bearings | Shaft seals |
| DE1861326U (en) * | 1962-09-01 | 1962-10-31 | Goetzewerke | OIL SEAL WITH DUST PROTECTION LIP. |
| DE1981048U (en) * | 1968-01-05 | 1968-03-14 | Goetzewerke | WHEEL BEARING SEAL. |
| DE1917623A1 (en) * | 1969-04-05 | 1970-10-08 | Hans Guentner | Air-cooled freezing mixture condenser |
| US3961829A (en) * | 1972-09-20 | 1976-06-08 | Dunlop Limited | Improvements in or relating to resilient mountings |
| FR2254241A5 (en) * | 1973-12-05 | 1975-07-04 | Leduc & Fils Rene | Seal for rotating and laterally vibrating shafts - additional flexible seal surrounds needle roller outer race |
| JPS57165850U (en) * | 1981-04-14 | 1982-10-19 | ||
| FR2567981B1 (en) * | 1984-07-20 | 1989-02-03 | Hutchinson | IMPROVEMENTS ON LIPSTICK SEALS |
| JPH0448368Y2 (en) * | 1987-04-18 | 1992-11-13 | ||
| JPH0464664U (en) * | 1990-10-18 | 1992-06-03 | ||
| IT223159Z2 (en) * | 1991-03-22 | 1995-06-13 | Skf Ind Spa | SUPPORT AND HOLDING COMPLEX FOR THE INCLUSION BETWEEN TWO BODIES IN RELATIVE ROTATION |
| JP3077863U (en) * | 2000-09-25 | 2001-06-08 | 植杉 昭光 | Oil leakage prevention structure at flange joint |
-
1992
- 1992-11-04 DE DE4237190A patent/DE4237190C1/en not_active Expired - Lifetime
-
1993
- 1993-06-16 DE DE59307492T patent/DE59307492D1/en not_active Expired - Lifetime
- 1993-06-16 EP EP93109576A patent/EP0596196B1/en not_active Expired - Lifetime
- 1993-08-31 BR BR9303655A patent/BR9303655A/en not_active IP Right Cessation
- 1993-11-02 JP JP5274144A patent/JP2513986B2/en not_active Expired - Lifetime
- 1993-11-04 CA CA002102472A patent/CA2102472C/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| EP0596196A2 (en) | 1994-05-11 |
| JPH06201055A (en) | 1994-07-19 |
| CA2102472A1 (en) | 1994-05-05 |
| JP2513986B2 (en) | 1996-07-10 |
| DE59307492D1 (en) | 1997-11-13 |
| DE4237190C1 (en) | 1994-01-05 |
| EP0596196B1 (en) | 1997-10-08 |
| BR9303655A (en) | 1994-05-10 |
| EP0596196A3 (en) | 1995-06-14 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| EEER | Examination request | ||
| MKLA | Lapsed |