US20050104302A1 - Sealing device, and rolling bearing and hub unit incorporating the sealing unit - Google Patents

Sealing device, and rolling bearing and hub unit incorporating the sealing unit Download PDF

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Publication number
US20050104302A1
US20050104302A1 US10/504,528 US50452805A US2005104302A1 US 20050104302 A1 US20050104302 A1 US 20050104302A1 US 50452805 A US50452805 A US 50452805A US 2005104302 A1 US2005104302 A1 US 2005104302A1
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US
United States
Prior art keywords
peripheral surface
seal lip
race
seal
tip edge
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.)
Abandoned
Application number
US10/504,528
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English (en)
Inventor
Masahito Matsui
Kinji Yukawa
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NSK Ltd
Original Assignee
NSK Ltd
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 NSK Ltd filed Critical NSK Ltd
Assigned to NSK LTD. reassignment NSK LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: MATSUI, MASAHITO, YUKAWA, KINJI
Publication of US20050104302A1 publication Critical patent/US20050104302A1/en
Priority to US11/715,890 priority Critical patent/US7731200B2/en
Priority to US11/715,891 priority patent/US20070152404A1/en
Abandoned legal-status Critical Current

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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
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B60B27/0005—Hubs with ball bearings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B60B27/0073—Hubs characterised by sealing means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B60B27/0094—Hubs one or more of the bearing races are formed by the hub
    • 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
    • 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
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
    • F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
    • F16C19/186—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement with three raceways provided integrally on parts other than race rings, e.g. third generation hubs
    • 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
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • 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
    • F16C2326/00—Articles relating to transporting
    • F16C2326/01—Parts of vehicles in general
    • F16C2326/02—Wheel hubs or castors

Definitions

  • the seal assembly, the rolling bearing and the hub unit in accordance with the present invention are related, for example, to an improvement of the seal assembly for rolling bearing to be incorporated into the rotatable supporting structure of the support device etc. for the wheels of an automobile or the like.
  • the rotatable supporting structures of various types of mechanical devices are assembled with a rolling bearing such as a ball bearing, a cylindrical roller bearing, a tapered roller bearing or the like.
  • a rolling bearing such as a ball bearing, a cylindrical roller bearing, a tapered roller bearing or the like.
  • This kind of a rolling bearing is provided with a seal assembly for the purpose of preventing the grease applied inside of this rolling bearing from leaking out of the rolling bearing, and also preventing various types of foreign objects such as rain water, mud, dust and the like from entering the inside of the rolling bearing.
  • FIGS. 25 to 27 show three exemplary structures of the seal assembly provided at the opening of the end portion of a rolling bearing for this purpose.
  • JP Patent Publication No. Tokukai Hei 10-252762 is composed of a metal core 5 , a slinger 6 and a sealing member 7 .
  • the metal core 5 among these elements is formed as a generally annular ring having an L-shaped cross section, and composed of a radially outer cylindrical portion 9 which can be internally fitted and fixed to the inner peripheral surface of the end portion of an outer race 8 and an inner circular ring portion 10 which is bent inwardly in the radial direction at the inner end edge of this radially outer cylindrical portion 9 in the axial direction (the end edge located near the center of the rolling bearing in the axial direction, i.e., the left end edge as illustrated in FIG.
  • the above slinger 6 is formed as an annular ring having an L-shaped cross section, and composed of a radially inner cylindrical portion 12 which can be externally fitted and fixed to the outer peripheral surface of the end portion of an inner race 11 and an outer circular ring portion 13 which is bent outwardly in the radial direction at the axially outer end edge of this inner cylindrical portion 12 (the end edge located near the opening of the rolling bearing in the axial direction, i.e., the right end edge as illustrated in FIG. 25 ).
  • the above sealing member 7 is made of a resilient member, for example, an elastomer such as a rubber, and provided with three seal lips 14 to 16 , i.e., an outer, an intermediate and an inner seal lip, whose base end portion is fixedly connected to the above metal core 5 .
  • the outer seal lip 14 which is provided in the most outer location, has its tip edge to be in slidable contact with the inner surface of the outer circular ring portion 13 of the slinger 6 .
  • the intermediate seal lip 15 and the inner seal lip 16 which are the remaining two seal lips, have their tip edges to be in slidable contact with the outer peripheral surface of the radially inner cylindrical portion 12 of the above slinger 6 .
  • the thickness of the outer seal lip 14 which is located in the outermost position among these three seal lips 14 to 16 of the above sealing member 7 , is gradually decreasing from the base end portion to the tip edge. Furthermore, the thickness of the inner seal lip 16 , which is located in the most inner position, is gradually decreasing from the base end portion to the tip edge in the same manner. This inner seal lip 16 is tilted in the direction such that it goes outwardly in the axial direction of the rolling bearing toward the tip edge thereof. Also, the intermediate seal lip 15 located in the intermediate position has a thin base end portion, a thin tip edge and a thick intermediate portion.
  • the prior art structure as a second example illustrated in FIG. 26 is approximately similar as that of the above first example illustrated in FIG. 25 .
  • an outer seal lip 14 a which is located in the most outer position among these three seal lips 14 a , 15 a and 16 , has the nearly same thickness throughout the entire length from the base end portion to the tip edge thereof.
  • the intermediate seal lip 15 a located in the intermediate position is designed to have a base end portion thinner than the tip end portion thereof.
  • the thickness of the outer seal lip 14 is gradually decreasing from the base end portion to the tip edge thereof in the same manner as illustrated in FIG. 25 showing the first example.
  • the other structure of the third example is similar as that of the second example as illustrated in FIG. 26 .
  • the opening of the end portion of the rolling bearing is blocked with the slinger 6 slidably contacting the tip edge of the seal lip 14 , 14 a , 15 , 15 a or 16 of the sealing member 7 .
  • This result in preventing the grease applied inside of this rolling bearing from leaking out of the rolling bearing, and also preventing various types of foreign matters such as rain water, mud, dust and the like from entering the inside of the rolling bearing.
  • the above slinger 6 and the metal core 5 move partially close to each other so that the above respective seal lips 14 , 14 a , 15 , 15 a and 16 are excessively compressed. Also, if the inner race 11 is decentered from the outer race 8 for some reason, the above respective seal lips 14 , 14 a , 15 , 15 a and 16 may be excessively compressed. When the respective seal lips 14 , 14 a , 15 , 15 a and 16 are excessively compressed, the so-called pressing force is increased which is a force urging the tip edge of the seal lips 14 , 14 a , 15 , 15 a and 16 against the slinger 6 .
  • the interference between the slinger 6 and the tip edges of the intermediate seal lips 15 and 15 a and the outer seal lips 14 and 14 a is not suitably controlled.
  • this interference is excessive, the tip edges of the above intermediate and outer seal lips 15 , 15 a , 14 and 14 a tend to wear, and therefore the sealing performance is degraded in the long term use at the slidably contacting region between the slinger 6 and the respective the seal lips 15 , 15 a , 14 and 14 a .
  • the rotating torque applied to the rolling bearing increases.
  • the outer seal lip 14 a since the outer seal lip 14 a has the nearly same thickness throughout the entire length from the base end portion to the tip edge, there are the following shortcomings to be improved. Namely, if the outer seal lip 14 a has the nearly same thickness throughout the entire length in this manner, this outer seal lip 14 a tends to excessively bend at the base end portion (the root portion) when this outer seal lip 14 a is urged against the slinger 6 . When the outer seal lip 14 a excessively bends at the base end portion (the root portion), a large strain is generated near the base end portion.
  • the motion following performance of the outer seal lip 14 a responsive to the surface movement of the slinger 6 is degraded by the increasing resistance against the elastic deformation of the sealing member 7 made of a resilient member such as a rubber or the like. Also, in this case, since the stress relaxation occurs in the vicinity of the above base end portion, the pressing force of the above outer seal lip 14 a on the above slinger 6 is decreased with the elapse of time. Accordingly, after long term use, the sealing performance tends to be degraded at the slidably contacting region between this outer seal lip 14 a and the above slinger 6 .
  • the tip end portion of the outer seal lip 14 tends to come into surface contact (surface-to-surface contact) with the inner side surface of the outer circular ring portion 13 constituting the slinger 6 . Then, when the tip end portion of the outer seal lip 14 comes into surface contact in this manner, the surface pressure is greatly decreased at the contact portion between the tip end portion of this outer seal lip 14 and the inner side surface of the outer circular ring portion 13 such that the sealing performance is easily degraded.
  • the slinger 6 rotates with displacement in the axial and radial directions relative to the sealing member 7 in accordance with the misalignment of the respective components, the elastic deformation thereof and so forth. Because of this, even in the case where the outer seal lip 14 a has the nearly same thickness throughout the entire length as illustrated in FIG. 26 showing the above second example, the above outer seal lip 14 a can come into surface contact with the inner surface of the outer circular ring portion 13 when the slinger 6 moves toward the sealing member 7 . Incidentally, if the entire length of the above outer seal lips 14 and 14 a is made small, it is possible to suppress the above surface-to-surface contact. However, in this case, it becomes difficult to secure the sealing performance when the above slinger 6 moves apart from the above sealing member 7 . Taking into consideration the above situation, the above outer seal lips 14 and 14 a cannot be shortened so much.
  • the present invention is made for the purpose of improving the sealing performance of a seal assembly.
  • the seal assemblies according to the present invention are installed in a rolling bearing with an inner raceway provided in the outer peripheral surface of an inner race and an outer raceway provided in the inner peripheral surface of an outer race together with a plurality of rolling members provided therebetween to enable the relative rotation between the above inner and outer races, for the purpose of sealing between the outer peripheral surface of the end portion of the inner race and the inner peripheral surface of the end portion of the outer race.
  • the seal assembly according to a first aspect is provided with a support member and a sealing member.
  • the support member among them is fixed to one of the outer peripheral surface of the end portion of the inner race and the inner peripheral surface of the end portion of the outer race.
  • the above sealing member is made of a resilient member and provided with a plurality of seal lips and a portion which is securely connected to the above support member.
  • the tip edge of the inner seal lip which is located in the innermost position among the plurality of these seal lips, and the tip edge of the intermediate seal lip outwardly located adjacent to this inner seal lip in the axial direction are arranged to come in sliding contact with the radially oriented peripheral surface of the other of the outer peripheral surface of the end portion of the inner race and the inner peripheral surface of the end portion of the outer race or the radially oriented peripheral surface of the member supported by the other peripheral surface.
  • 0.2 ⁇ d1 d2 0.8 ⁇ d1 at least at a location of the base end portion of the above intermediate seal lip and 0.5 ⁇ D1 D2 ⁇ D1 at least at a location of the base end portion of the above inner seal lip
  • d1 is the thicknesses of the base end portion and d2 is the thickness of the tip end portion of the intermediate seal lip
  • D1 is the thicknesses of the base end portion
  • D2 is the thicknesses of the tip end portion of the inner seal lip.
  • the interference is nearly zero with no or very little elastic deformation of the above inner seal lip.
  • all the above plurality of the seal lips are tilted in the direction such that it goes outwardly in the axial direction of the rolling bearing toward the respective tip edges thereof.
  • the seal assembly according to a second aspect is provided with a metal core, an annular member, a sealing member, an axially oriented seal lip and a radially oriented seal lip.
  • the metal core among them is formed as a generally annular ring, and composed of a radially outer cylindrical portion which can be internally fitted and fixed to the inner peripheral surface of the end portion of the outer race and an inner circular ring portion which is bent inwardly in the radial direction from the axially inner end edge of this outer cylindrical portion.
  • the above annular member is formed as a generally annular ring, and composed of a radially inner cylindrical portion which can be externally fitted and fixed to the outer peripheral surface of the end portion of the inner race and an outer circular ring portion which is bent outwardly in the radial direction from the axially outer end edge of this inner cylindrical portion.
  • the above sealing member is made of a resilient member whose portion is fixedly connected to at least one of the above metal core and annular member. Then, the above axially oriented seal lip is formed as part of the above sealing member with its tip edge slidably contacting the axially oriented side surface of a member which ratates relative to the metal core or the annular member to which this sealing member is fixed.
  • the above radially oriented seal lip is formed as part of the above sealing member with its tip edge slidably contacting the radially oriented peripheral surface of a member which ratates relative to the metal core or the annular member to which this sealing member is fixed.
  • the base end portion of the above radially oriented seal lip has a thickness, at least in a location, smaller than that of the tip end portion. Also, it is satisfied that 0.010 L1/R 0.020 and 0.008 L2/R 0.015 wherein L1 is the diametrical interference, in the radial direction of the member having the radially oriented peripheral surface, between the tip edge of the above radially oriented seal lip and the radially oriented peripheral surface of the member which ratates relative to the metal core or the annular member to which this sealing member having the radially oriented seal lip is fixed, L2 is the interference, in the axial direction of the member having the axially oriented side surface, between the tip edge of the above axially oriented seal lip and the axially oriented side surface of the member which ratates relative to the metal core or the annular member to which this sealing member having the axially oriented seal lip is fixed, and R is the diameter of the fitting portion between the outer peripheral surface of the inner race
  • the seal assembly in accordance with any of third to sixth aspects is provided with a support member, a sealing member and an axially oriented seal lip.
  • the support member among them is fixed to one of the outer peripheral surface of the end portion of the inner race and the inner peripheral surface of the end portion of the outer race.
  • the above sealing member is made of a resilient member whose portion is securely connected to the above support member.
  • the above axially oriented seal lip is formed as part of the above sealing member with its tip edge slidably contacting on the axially oriented side surface provided in the other of the outer peripheral surface of the end portion of the inner race and the inner peripheral surface of the end portion of the outer race or on the axially oriented side surface of the member supported by the other peripheral surface.
  • a center point is defined as a position on the phantom line passing through the center in the thickness direction of the above axially oriented seal lip with the length from the tip end to the position being equal to the length from the base end to the position
  • t1 is the thickness of the above axially oriented seal lip at the base end
  • t2 at the center point
  • t3 at the tip end
  • a projection is formed on the side surface of the tip end portion of the above axially oriented seal lip which is radially inwardly oriented in the free state thereof.
  • the tip edge of this projection then comes in slidably contact with the axially oriented side surface provided in the other of the outer peripheral surface of the end portion of the inner race and the inner peripheral surface of the end portion of the outer race or with the axially oriented side surface of the member supported by the other peripheral surface.
  • the thickness of the above axially oriented seal lip is gradually decreasing, except for the tip end portion, from the base end portion to a position of the intermediate portion close to the tip end.
  • the portion (the above tip end portion) from this position of the intermediate portion to the tip edge is gradually increased toward the tip edge. This tip edge then comes in slidably contact with the axially oriented side surface provided in the other of the outer peripheral surface of the end portion of the inner race and the inner peripheral surface of the end portion of the outer race or with the axially oriented side surface of the member supported by the other peripheral surface.
  • the tip edge portion of the above axially oriented seal lip is provided with an auxiliary seal lip projecting from the radially outer end thereof. Then, the tip edge of this auxiliary seal lip and the radially inner end of the tip edge of the above axially oriented seal lip separated from this auxiliary seal lip are arranged to come in slidably contact with the axially oriented side surface provided in the other of the outer peripheral surface of the end portion of the inner race and the inner peripheral surface of the end portion of the outer race or with the axially oriented side surface of the member supported by the other peripheral surface.
  • the rolling bearing according to a seventh aspect is implemented with at least one of the seal assemblies described according to the first to sixth aspects.
  • the hub unit according to an eighth aspect is a hub having an inner race for fixing a wheel and implemented with at least one of the seal assemblies described according to the first to sixth aspects.
  • the sealing performance can be improved.
  • the tip edge of this inner seal lip is fitted onto the peripheral surface of the mating member with substantially zero interference. Because of this, even when the inner race is tilted or decentered relative to the outer race so that the support member and the peripheral surface of the above mating member move close to each other, the tip edges of the above intermediate and inner seal lips can satisfactorily follow the movement of the peripheral surface of the above mating member to suppress the variation of the pressing force of the respective intermediate and inner seal lips. Accordingly, it is possible to obtain a good sealing performance by inhibiting the abrasion of these intermediate and inner seal lips, and inhibit the increase in the rotating torque of the rolling bearing.
  • all of a plurality of seal lips inclusive of the above inner seal lip are tilted outwardly in the axial direction of the above rolling bearing toward the tip edges thereof respectively, and therefore the grease applied inside of this rolling bearing can adequately be supplied to the slidably contacting region between the tip edges of the respective seal lips and the peripheral surface of the mating member. Accordingly, it is possible to maintain the lubrication condition of the respective slidably contacting regions, attain the lower rotating torque of the rolling bearing, and improve the sealing performance of the above respective slidably contacting regions. Furthermore, since the base end portions of all the seal lips are located apart from each other, the movement of each seal lip shall not interfere with the movement of the adjacent seal lip. Accordingly, since the tip edges of the above respective seal lips satisfactorily follow the movement of the peripheral surface of the mating member, it is possible to attain a more satisfactory sealing performance and limit the increase in the rotating torque of the rolling bearing.
  • the sealing performance can be improved and therefore it is possible to prevent the grease applied inside of the rolling bearing from leaking out and prevent various types of matters objects such as rain water, mud, dust and the like from entering the inside of the rolling bearing. Furthermore, the rotating torque of the rolling bearing is prevented from excessively increasing.
  • the strain generated in the axially oriented seal lip can be reduced, and therefore it is possible to maintain the pressing force of this axially oriented seal lip to the side surface of the mating member constant in the long term use. Because of this, the improved sealing performance can be maintained in the long term use. Also, even when the inner race is tilted relative to the outer race, the axially oriented seal lip can satisfactorily follow the movement of a slinger so that the sealing performance can be improved.
  • the axially oriented seal lip is prevented from being in surface-to-surface contact with the side surface of the mating member even if this mating member substantially moves toward this sealing member, so that the sealing performance is further improved.
  • the seal assembly according to the fifth aspect it is possible to prevent the sealing performance from being degraded due to the abrasion between the tip edge of the axially oriented seal lip and the side surface of the mating member to maintain the improved sealing performance in the long term use. Namely, it is considered as the cause of the degradation of the sealing performance that foreign matters enter the slidably contacting region between the tip edge of the axially oriented seal lip and the side surface of the mating member to cause the abrasion between the tip edge of the axially oriented seal lip and the side surface of the mating member and decrease the pressing force (interference) of the above axially oriented seal lip.
  • the strain generated in the axially oriented seal lip can be reduced, and therefore it is possible to maintain the pressing force of this axially oriented seal lip constant in the long term use. Furthermore, in the case of the seal assembly according to the fifth aspect, even when foreign matters enter the slidably contacting region between the tip edge of the axially oriented seal lip and the side surface of the mating member to cause the abrasion between this tip edge of the axially oriented seal lip and the side surface of the mating member, it is possible to inhibit the decrease in the pressing force of the axially oriented seal lip by virtue of the thick tip end portion of this axially oriented seal lip.
  • this axially oriented seal lip becomes gradually thinner from the base end portion to a position of the intermediate portion close to the tip end, and therefore it is possible to reduce the strain generated in the above axially oriented seal lip in its assembled state.
  • this axially oriented seal lip is thicken at the tip end portion thereof, the axially oriented seal lip is hardly weakened even with the abrasion of the tip edge of this axially oriented seal lip, and therefore it is possible to maintain the pressing force constant furthermore in the long term use, as compared with the seal assembly according to the above fourth aspect.
  • the axially oriented seal lip can satisfactorily follow the movement of the side surface of the mating member so that the sealing performance can be satisfactorily maintained.
  • the seal assembly according to the sixth aspect it is possible to prevent foreign matters from entering the slidably contacting region between the radially inner edge of the tip end portion in the axially oriented seal lip and the side surface of the mating member. Because of this, the abrasion of this slidably contacting region can be inhibited by preventing foreign matters from being bitten by this slidably-contacting region. Accordingly, in the case of this structure, the sealing performance can be improved. In addition to this, since the above auxiliary seal lip is formed in order to project from the tip edge of the above axially oriented seal lip, the cost does not substantially rise.
  • the above auxiliary seal lip sufficiently works as long as it prevents the entrance of foreign matters, and therefore the pressing force of this auxiliary seal lip need not be increased. Because of this, it is possible to make small or null the abrasion at the slidably contacting region between the tip edge of this auxiliary seal lip and the above side surface of the mating member. Also, even if there is some abrasion at this slidably contacting region, no influence thereof is exerted upon the sealing performance of the slidably contacting region between the side surface of the mating member and the radially inner end of the tip edge of the above axially oriented seal lip. Furthermore, since the pressing force of the above auxiliary seal lip can be significantly decreased, it is possible to prevent the pressing force of the above outer seal lip from excessively decreasing because of the provision of this auxiliary seal lip 19 .
  • FIG. 1 is a partly cut away, cross sectional view of a first example of the embodiment of the present invention.
  • FIG. 2 is a partly cut away cross sectional view of the first example of FIG. 1 to show a seal member and metal core before they are combined with a slinger.
  • FIG. 3 is a partly cut away, cross sectional view of a second example of the embodiment of the present invention, similar to FIG. 2 .
  • FIG. 4 is an example of the conventional structure used for comparison, similar to FIG. 2 .
  • FIG. 5 is a view to show a distribution in the circumferential direction of the pressing force of the intermediate seal lip.
  • FIG. 6 is a diagram to show a relationship between the ratio in thickness of the parts of the intermediate seal lip, and the maximum value of the pressing force of the intermediate seal lip.
  • FIG. 7 is a graph to show a distribution in the circumferential direction of the pressing force of the inner seal lip.
  • FIG. 8 is a graph to show a relationship between the ratio in thickness of the parts of the inner seal lip, and the maximum value of the pressing force of the inner seal lip.
  • FIG. 9 is a partly cut away, cross sectional view of a third example of the embodiment of the present invention.
  • FIG. 10 is a graph to show a relationship between the ratio of interference to diameter, and the pressing force with respect to the intermediate seal lip.
  • FIG. 11 is a graph to show a relationship between the ratio of interference to diameter, and the pressing force with respect to the outer seal lip.
  • FIG. 12 is a partly cut away, cross sectional view of a fourth example of the embodiment of the present invention, similar to FIG. 2 .
  • FIG. 13 is a cross sectional view of part of the assembled structure of the fourth example.
  • FIG. 14 is a view to show a relationship between the thickness at three locations of the outer seal lip and the maximum strain.
  • FIG. 15 is a partly cut away, cross sectional view of a fifth example of the embodiment of the present invention, similar to FIG. 2 .
  • FIG. 16 is a cross sectional view of part of the assembled structure of the fifth example.
  • FIG. 17 is a partly cut away, cross sectional view of a sixth example of the embodiment of the present invention, similar to FIG. 2 .
  • FIG. 18 is a partly cut away, cross sectional view of a seventh example of the embodiment of the present invention.
  • FIG. 19 is a partly cut away, cross sectional view of an eighth example of the embodiment of the present invention, similar to FIG. 2 .
  • FIG. 20 is a cross sectional view of part of the assembled structure of the eighth example.
  • FIG. 21 is cross sectional view to show a hub unit with a sealing assembly of the present invention installed in it.
  • FIG. 22 is a partly cut away, cross sectional view of a ninth example of the embodiment of the present invention.
  • FIG. 23 is a partly cut away, cross sectional view of a tenth example of the embodiment of the present invention.
  • FIG. 24 is a partly cut away, cross sectional view of an eleventh example of the embodiment of the present invention.
  • FIG. 25 is a cross sectional view of part of a first example of the conventional structure.
  • FIG. 26 is a cross sectional view of part of a second example of the conventional structure.
  • FIG. 27 is a cross sectional view of part of a third example of the conventional structure.
  • FIGS. 1 and 2 show a first example of the embodiment of the present invention corresponding to the first to seventh aspects.
  • the seal assembly 17 according to the present invention is composed of a metal core 5 , a slinger 6 and a sealing member 7 a .
  • the metal core 5 among these elements is formed in a single body by punching process, such as press work, and plastic-working process of a metallic plate such as a low-carbon steel plate.
  • the metal core 5 is formed in a generally annular ring shape having an L-shaped cross section, and composed of a radially outer cylindrical portion 9 which can be internally fitted and fixed to the inner peripheral surface of the end portion of the outer race 8 (see FIG. 25 ) of the rolling bearing and an inner circular ring portion 10 which is bent inwardly in the radial direction from the end edge at the axially inner end of this radially outer cylindrical portion 9 (the left edge as illustrated in FIGS. 1 and 2 ).
  • the above slinger 6 is also integrally formed in a single body by punching process, such as press work, and plastic-working process of a metallic plate having an excellent corrosion resistance such as a stainless steel plate.
  • the slinger 6 is formed in a generally annular ring shape having an L-shaped cross section, and composed of, as the components of the above rolling bearing, a radially inner cylindrical portion 12 which can be externally fitted and fixed to the outer peripheral surface of the end portion of an inner race 11 (see FIG. 25 ) of the rolling bearing and an outer circular ring portion 13 which is bent outwardly in the radial direction from the edge at the axially outer end of this radially inner cylindrical portion 12 (the right edge as illustrated in FIGS. 1 and 2 ).
  • FIG. 2 illustrates the seal assembly 17 before the slinger 6 is engaged with the metal core 5 and the sealing member 7 a.
  • the above sealing member 7 a is made of a resilient member, for example, an elastomer such as a rubber, and provided with three seal lips 14 , 15 a and 16 a , i.e., an outer, an intermediate and an inner seal lip, whose base end portion is fixedly connected to the above metal core 5 .
  • the outer seal lip 14 which is provided in the outermost location, has the tip edge to be in slidable contact with the inner surface of the outer circular ring portion 13 .
  • the intermediate seal lip 15 a and the inner seal lip 16 a which are the remaining two seal lips, have tip edges to be in slidable contact with the outer peripheral surface of the inner cylindrical portion 12 of the above slinger 6 .
  • At least a location of the base end portion of the above intermediate seal lip 15 a (the most thin location) is designed to have a thickness d2 satisfying 0.2 ⁇ d1 d2 0.8 ⁇ d1, where d1 is the thickness of a location of the tip end portion of the intermediate seal lip 15 a (the most thick location).
  • the thickness d2 of the location of the above base end portion is about 0.5 times the thickness d1 of the location of the above tip end portion (d2 0.5 ⁇ d1) within the above predetermined range.
  • At least a location of the base end portion of the above inner seal lip 16 a (the most thin location) is designed to have a thickness D2 satisfying 0.5 ⁇ D1 D2 ⁇ D1, where D1 is the thickness of a location of the tip end portion of the inner seal lip 16 a (the most thick location).
  • D2 of the location of the above base end portion is about 0.6 times the thickness D1 of the location of the above tip end portion (D2 0.6D1) within the above predetermined range.
  • the above three seal lips 14 , 15 a and 16 a are tilted outwardly in the axial direction of the above rolling bearing toward the tip edges thereof respectively. Then, with the tip edge of the inner seal lip 16 a most inwardly located being abutted against the outer peripheral surface of the radially inner cylindrical portion 12 constituting the above slinger 6 , the interference is nearly zero with no or very little elastic deformation of the above inner seal lip 16 a . For this reason, the inner diameter of the above inner seal lip 16 a in its free state is designed to be almost the same in size as the outer diameter of the above inner cylindrical portion 12 .
  • the outer diameter D12 of the radially inner cylindrical portion 12 is about 40 mm to 70 mm, and in this case, the inner diameter R16a of the above inner seal lip 16 a in its free state is regulated to be no smaller than the above outer diameter D12 minus 0.5 mm and no lager than this outer diameter D12 plus 0.2 mm, that is ⁇ (D12 ⁇ 0.5 mm) R16a (D12+0.2 mm) ⁇ .
  • the thicknesses d2 and D2 at the base end of the intermediate seal lip 15 a and the inner seal lip 16 a are designed to be small, and the tip edge of this inner seal lip 16 a is externally fitted onto the outer peripheral surface of the radially inner cylindrical portion 12 constituting the slinger 6 with almost zero interference.
  • all the three seal lips 14 , 15 a and 16 a inclusive of the above inner seal lip 16 a are tilted outwardly in the axial direction of the above rolling bearing toward the tip edges thereof respectively, and therefore the grease applied inside of this rolling bearing can adequately be supplied to the slidably contacting region between the slinger 6 and the tip edges of the respective seal lips 14 , 15 a and 16 a . Accordingly, it is possible to maintain the lubrication condition of the respective slidably contacting regions, attain the lower rotating torque of the rolling bearing, and improve the sealing performance of the above respective slidably contacting regions by closing the respective slidably contacting regions with a grease.
  • FIG. 3 shows a second example of the embodiment of the present invention corresponding to the first to seventh aspects.
  • an inner seal lip 16 b which is located in the innermost position among these three seal lips 14 , 15 a and 16 b constituting a sealing member 7 b , is tilted in the direction to the center of the rolling bearing in the axial direction toward the tip edge thereof. Then, with the tip edge of the inner seal lip 16 b being abutted against the outer peripheral surface of the radially inner cylindrical portion 12 constituting the above slinger 6 , the interference is nearly zero with no or very little elastic deformation of the above inner seal lip 16 b .
  • At least a location of the base end portion of the above inner seal lip 16 b (the most thin tip edge portion) is designed to have a thickness D2 satisfying 0.5 ⁇ D1 D2 ⁇ D1, where D1 is the thickness of a location of the tip end portion of the inner seal lip 16 b (the most thick location).
  • the inner seal lip 16 b is tilted in the direction to the center of the rolling bearing in the axial direction toward the tip edge thereof. Because of this, the grease applied inside of this rolling bearing tends relatively not to be supplied to the slidably contacting region between the slinger 6 and the tip edges of the respective outer and intermediate seal lips 14 and 15 a , and therefore there is the possibility of decreasing the sealing performance and increasing the rotating torque of the rolling bearing as compared to the case of the first example. However, even in the case of this example, when the inner race 11 is tilted or decentered relative to the outer race 8 (see FIG.
  • the tip edges of the respective intermediate and inner seal lips 15 a and 16 b can satisfactorily follow the movement of the surface of the above slinger 6 to limit the variation of the pressing force of the respective intermediate and inner seal lips 15 a and 16 b . Accordingly, although being inferior to the performance of the first example, it is also possible to attain a satisfactory sealing performance and limit the increase in the rotating torque of the rolling bearing by inhibiting the abrasion of the respective intermediate and inner seal lips 15 a and 16 b.
  • the ratio d2′/d1′ of the thickness d2′ of the location of the base end portion of the intermediate seal lip 15 b (the most thick location) to the thickness d1′ of the location of the tip end portion of the intermediate seal lip 15 b (the most thin location) was 1.5
  • the ratio D2′/D1′ of the thickness D2′ of the location of the base end portion of the inner seal lip 16 c (the most thick location) to the thickness D1′ of the location of the tip end portion of the inner seal lip 16 c (the most thin location) was 1.2.
  • the ratio d2/d1 of the thickness d2 of the location of the base end portion of the intermediate seal lip 15 a (the most thin location) to the thickness d1 of the location of the tip end portion of the intermediate seal lip 15 a (the most thick location) was 0.5
  • the ratio D2/D1 of the thickness D2 of the location of the base end portion of the inner seal lip 16 a (the most thin location) to the thickness D1 of the location of the tip end portion of the inner seal lip 16 a (the most thick location) was 0.6.
  • the finite element method was applied for obtaining the distribution of the pressing force of the intermediate seal lips 15 a and 15 b and the inner seal lips 16 a and 16 c in the circumferential direction of the respective slidably contacting regions.
  • FIG. 5 shows the result of simulation conducted by the inventors with the intermediate seal lips 15 a and 15 b .
  • the abscissa shows the location in the circumferential direction of the slidably contacting region between the peripheral surface of the slinger 6 and the tip edges of the intermediate seal lips 15 a and 15 b
  • the ordinate shows the pressing forces of the above intermediate seal lips 15 a and 15 b .
  • the numerical values of this ordinate are values relative to the average value of the pressing force of the intermediate seal lip 15 b of the conventional structure with the slinger 6 being not tilted relative to the metal core 5 .
  • the pressing forces of the intermediate seal lips 15 a and 15 b with the slinger 6 being tilted relative to the metal core 5 at the above predetermined angle are plotted respectively by a solid line according to the present invention and by a broken line according to the conventional structure.
  • the one-dot chained line shows the pressing force with the slinger 6 being not tilted relative to the metal core 5 according to the conventional structure.
  • the pressing force varied in the range of about 0.6 to about 1.4 in the circumferential direction of the slidably contacting region.
  • the above pressing force varied in the range of about 0.8 to about 1.2.
  • FIG. 6 shows the result of obtaining the relationship between the maximum value of the pressing force and the thickness of the base end portion of the intermediate seal lip 15 a or 15 b .
  • the abscissa shows the ratio d2/d1 (d2′/d1′) between the thickness d2 (d2′) of the base end portion and the thickness d1 (d1′) of the tip end portion of the intermediate seal lips 15 a and 15 b
  • the ordinate shows the maximum value of the pressing force the intermediate seal lips 15 a and 15 b
  • the arrow “a” indicates the range of the above ratio d2/d1 (d2′/d1′) in accordance with the first aspect of the present invention.
  • the above ratio d2/d1 (d2′/d1′) falls below 0.2, which is the lower limit of the range according to the present invention, the above pressing force becomes too small and therefore the sealing performance of the rolling bearing is degraded. For this reason, various types of foreign matters such as rain water, mud, dust and the like tend to enter the inside of the rolling bearing. Namely, if the above ratio d2/d1 (d2′/d1′) falls below 0.2, the thickness of the base end portion of the intermediate seal lip becomes too small to obtain a necessary sealing performance even by increasing in some degree the contact area between the tip end portion of this intermediate seal lip and the outer peripheral surface of the slinger.
  • FIG. 7 shows the result of simulation for obtaining the circumferential distribution of the pressing force of the inner seal lips 16 a and 16 c .
  • the relationship between the ordinate and the abscissa in this FIG. 7 is the same as that of the intermediate seal lips 15 a and 15 b illustrated in FIG. 5 .
  • the pressing forces of the above inner seal lips 16 a and 16 c with the slinger 6 being tilted relative to the metal core 5 at the predetermined angle are plotted respectively by a solid line according to the present invention and by a broken line according to the conventional structure.
  • the one-dot chained line shows the pressing force with the slinger 6 being not tilted relative to the metal core 5 in the structure according to the present invention.
  • the pressing force of the above inner seal lip 16 a becomes approximately zero with the slinger 6 being not tilted relative to the metal core 5 . Also, when the slinger 6 is tilted relative to the metal core 5 at a predetermined angle, if the maximum value of the pressing force of the inner seal lip 16 c is 1 in the case of the above conventional structure, the maximum value of the pressing force of the inner seal lip 16 a becomes significantly small as about 0.1 in the structure according to the present invention.
  • FIG. 8 shows the result of obtaining the relationship between the thickness of the base end portion of the inner seal lip 16 a or 16 c and the maximum value of the pressing force.
  • the relationship between the abscissa and the ordinate is the same as illustrated in FIG. 6 .
  • the arrow “b” indicates the range of the ratio D2/D1 (D2′/D1′) between the thickness D2 (D2′) of the base end portion and the thickness D1 (D1′) of the tip end portion of the inner seal lips 16 a and 16 c in accordance with the first aspect of the present invention.
  • the above ratio D2/D1 (D2′/D1′) is smaller than 1.0, which is the upper limit of the range according to the present invention, the maximum value of the above pressing force can be maintained low.
  • the above ratio D2/D1 (D2′/D1′) is smaller than 0.5, which is the lower limit of the range according to the present invention, the thickness of the above inner seal lips 16 a and 16 c becomes excessively small to significantly decrease the strength.
  • FIG. 9 shows a third example of the embodiment of the present invention corresponding to the second and seventh aspects.
  • the slinger 6 as an annular member and the sealing member 7 c are illustrated in the respective free states, partially overlapping each other, and the illustration does not correspond to an actual assembled condition.
  • the outer seal lip 14 which is located in the outermost position is tilted outwardly in the radial direction of the rolling bearing toward the tip edge thereof.
  • the intermediate seal lip 15 a located in the intermediate position and the inner seal lip 16 d located in the innermost position are tilted outwardly in the axial direction of the above rolling bearing toward the tip edges thereof respectively.
  • this inner seal lip 16 d has the nearly same thickness throughout the entire length from the base end portion to the tip edge.
  • the above outer seal lip 14 corresponds to the axially oriented seal lip of the second aspect
  • the above inner seal lip 16 d corresponds to the radially oriented seal lip of the second aspect.
  • the thickness d2 of the base end portion of the above intermediate seal lip 15 a is smaller than the thickness d 1 of the tip end portion of this intermediate seal lip 15 a (d2 ⁇ d1).
  • the interference between the intermediate seal lip 15 a and the slinger 6 as well as the interference between the outer seal lip 14 and the slinger 6 are controlled within the respective predetermined range. That is, in the case of this example, the diametrical interference between the tip edge of the above intermediate seal lip 15 a and the outer peripheral surface of the radially inner cylindrical portion 12 constituting the slinger 6 is designed to be L1 in the radial direction of this radially inner cylindrical portion 12 .
  • the interference between the tip edge of the above intermediate seal lip 14 and inner surface of the outer circular ring portion 13 constituting the slinger 6 is designed to be L2 in the axial direction of this outer circular ring portion 13 .
  • the diameter of the fitting portion between the outer peripheral surface of the inner race 11 and the inner peripheral surface of the radially inner cylindrical portion 12 is designed to be R. Then, in this case, the respective dimensions are determined in order that 0.010 L1/R 0.020 and 0.008 L2/R 0.015.
  • the sealing performance can be improved by suitably controlling the interference of the respective outer and intermediate seal lips 14 and 15 a . Because of this, it is possible to prevent the grease applied inside of the rolling bearing from leaking out and various types of foreign matters such as rain water, mud, dust and the like from entering the inside of the rolling bearing. Furthermore, the rotating torque of the rolling bearing is prevented from excessively increasing.
  • the structures and the functionality of the other members are similar to those of the first example as illustrated in FIGS. 1 and 2 . Also, this example can be practiced in combination with the first example as described above. Meanwhile, although not shown in the figure, it will be appreciated in the case of the second example that the inner seal lip may be tilted in the direction to the axial center of the rolling bearing toward the tip edge thereof.
  • the abscissa and the ordinate show the above ratio L1/R and the pressing force of the intermediate seal lip 15 a respectively.
  • the numerical values of this ordinate are values relative to, as a reference value, the pressing force when the above ratio L1/R was 0.015.
  • the arrow “c” indicates the range of the above ratio L1/R in accordance with the second aspect of the present invention. As apparent from the result of simulation as illustrated in FIG. 10 , if the above ratio L1/R is smaller than 0.010, the pressing force of the intermediate seal lip 15 a quickly decreases. In contrast to this, if the above ratio L1/R is 0.010 or larger, the pressing force of the intermediate seal lip 15 a can be sufficiently secured, that is 0.8 or larger.
  • the pressing force excessively decreased to shorten the life of the seal, and therefore water easily entered the inner space of the rolling bearing.
  • the above ratio L1/R exceeds 0.020, the maximum strain of the sealing member 7 c increases to 15%, and in addition to this, the pressing force becomes excessively large to increase the abrasion between the intermediate seal lip 15 a and the slinger 6 and, to shorten the life of the seal than lengthening it.
  • the finite element method was applied for obtaining the pressing force of the outer seal lip 14 of the above structure of the third example as described above with varying values of the ratio L2/R of the interference L2 between the tip edge of the outer seal lip 14 and the inner surface of the radially outer circular ring portion 13 to the diameter R of the above fitting portion.
  • the result of simulation as conducted in this manner is shown in FIG. 11 .
  • the abscissa and the ordinate show the above ratio L2/R and the pressing force of the above outer seal lip 14 respectively.
  • the numerical values of this ordinate are values relative to, as a reference value, the pressing force when the above ratio L2/R was 0.010.
  • the arrow “d” indicates the range of the above ratio L2/R in accordance with the second aspect of the present invention.
  • the pressing force of the outer seal lip 14 quickly decreases.
  • the above ratio L2/R is at least 0.008
  • the pressing force of the above outer seal lip 14 can be sufficiently secured to be 0.9 or larger.
  • the pressing force excessively decreased with the above ratio L2/R being smaller than 0.008 to shorten the life of the seal, and therefore water easily entered the inner space of the rolling bearing.
  • FIGS. 12 and 13 show a fourth example of the embodiment of the present invention corresponding to the third and seventh aspects.
  • an inner seal lip 16 d which is located in the innermost position among these three seal lips 14 b , 15 a and 16 d constituting a sealing member 7 d , is designed to have the nearly uniform thickness throughout the entire length from the base end portion to the tip edge.
  • the outer seal lip 14 b which is located in the outermost position among these three seal lips 14 b , 15 a and 16 d , is designed to have a base end portion, an intermediate portion and a tip end portion whose thicknesses satisfy the predetermined relationship to each other.
  • a phantom line segment “s” is designated such that it passes the center in the thickness direction throughout the entire length of the above outer seal lip 14 b .
  • a point C is designated such that it is located in the center point between the base and tip ends A and B of this phantom line so that the length therefrom to the base end A is equal to the length therefrom to the tip end B.
  • the thickness of the above outer seal lip 14 b is assumed to be t1 at the base end A, t2 at the center point C and t3 at the tip end B.
  • the respective thicknesses t1, t2 and t3 of the above outer seal lip 14 b satisfy 0.70 ⁇ t2/t1 ⁇ 0.85 and 0.35 ⁇ t3/t1 ⁇ 0.65.
  • the above outer seal lip 14 b may be provided with a notch, a projection or the like for several reasons, the above thicknesses t1, t2 and t3 are defined on the assumption that such a notch, a projection or the like does not exist.
  • the above outer seal lip 14 b corresponds to the axially oriented seal lip of the third aspect.
  • the strain generated in the outer seal lip 14 b can be reduced, and therefore it is possible to maintain the pressing force of this outer seal lip 14 b to the slinger 6 constant in the long term use. Because of this, in accordance with the structure of this example, the improved sealing performance can be maintained in the long term use. Also, even when the inner race is tilted relative to the outer race, the outer seal lip 14 b can satisfactorily follow the movement of the slinger 6 so that the sealing performance can be improved.
  • the structures and the functionality of the other members are similar to those of the first example as illustrated in FIGS. 1 and 2 , and therefore redundant explanation is not repeated.
  • this simulation was performed by assigning 60 mm to the inner diameter d12 of the radially inner cylindrical portion 12 constituting the slinger 6 , 80 mm to the outer diameter D9 of the radially outer cylindrical portion 9 constituting the metal core 5 , and 4 mm to the entire width L17 of the seal assembly 17 after assembling. Also, 0.8 mm was assigned to the interference in the axial direction of the outer seal lip 14 b with the inner surface of the outer circular ring portion 13 constituting the above slinger 6 .
  • FIG. 14 shows the result of simulation conducted in this manner.
  • the numeral associated with each curve indicates the ratio of the maximum strain generated in the above outer seal lip 14 b .
  • This ratio was obtained by assigning “1” to the maximum strain generated in the outer seal lip 14 b when the thickness t1 at the base end A, the thickness t2 at the center point C and the thickness t3 at the tip end B were set equal to each other under the condition as assumed above.
  • the arrow “e” indicates the range of the ratio t2/t1 of the above outer seal lip 14 b in accordance with the third aspect of the present invention.
  • the arrow “f” indicates the range of the ratio t3/t1 of the above outer seal lip 14 b in accordance with the third aspect of the present invention.
  • the above ratios t2/t1 and t3/t1 fall within the ranges in accordance with the third aspect of the present invention, it is possible to minimize the maximum of strain generated in the above outer seal lip 14 b.
  • FIGS. 15 and 16 show a fifth example of the embodiment of the present invention corresponding to the fourth and seventh aspects.
  • the thickness of the inner seal lip 16 d constituting the sealing member 7 e is designed to have the nearly same thickness throughout the entire length from the base end portion to the tip edge.
  • the thickness of the outer seal lip 14 c that is an axially oriented seal lip, is gradually decreasing from the base end portion to the tip edge.
  • a projection 18 having a sharp end is formed around the entire circumference on the side surface of the tip end portion of this outer seal lip 14 c which is on the radially inward side in the free state thereof.
  • this projection 18 is abutted to the inner surface of the outer circular ring portion 13 of this slinger 6 when the slinger 6 and the sealing member 7 e on the metal core 5 as a support member are engaged by moving them close to each other as illustrated in FIG. 16 .
  • the tip end portion of the above outer seal lip 14 c is prevented from being in surface-to-surface contact with the inner surface of the outer circular ring portion 13 to improve the sealing performance.
  • FIGS. 17 and 18 show a sixth and a seventh example of the embodiment of the present invention corresponding to the fifth and seventh aspects.
  • the thicknesses of the outer seal lips 14 e and 14 f as the axially oriented seal lip are gradually increased toward the tip edge from a position of the intermediate portion closer to the tip end to prevent the tip end portion of these outer seal lips 14 e and 14 f from being excessively small in the thickness dimension, so that the thickness dimension of the tip end portions of the outer seal lips 14 e and 14 f can be secured even after abrasion.
  • the thickness dimension of this outer seal lip 14 e is gradually increased toward the tip edge of the above outer seal lip 14 e from a point P in the intermediate portion of the seal lip 14 a .
  • the point P is located at a location displaced a little to the tip end of the seal lip 14 a from the center of the intermediate portion on the surface, which is one of the opposite surfaces of the outer seal lip 14 e , that is opposed to the outer circular ring portion 13 of the slinger 6 in its use condition and that is located on the radially inner side in its free state.
  • the thickness of the outer seal lip 14 f is gradually increased toward the tip edge of the above outer seal lip 14 f from this point P similar as that of the above sixth example and from a point Q located in the opposite surface of the outer seal lip 14 f approximately corresponding to the point P of the sixth example as described above.
  • the chained lines of the outer seal lips 14 e and 14 f drawn in FIGS. 17 and 18 indicate the profiles of the cross sections in the case where the thicknesses are not increased toward the tip edges from the points P and Q. The reason of increasing the thicknesses of the tip edges of the outer seal lips 14 e and 14 f is as follows.
  • this outer seal lips 14 e and 14 f are made thick, the decrease in the pressing force and the fatigue of these outer seal lips 14 e and 14 f can be suppressed even if foreign matters enter the slidably contacting region between the tip edges of the outer seal lips 14 e and 14 f and the side surface of the above outer circular ring portion 13 to cause the abrasion of the side surface of the outer circular ring portion 13 and the tip edges of this outer seal lip 14 e and 14 f .
  • FIGS. 19 and 20 show an eighth example of the embodiment of the present invention corresponding to the sixth and seventh aspects.
  • the thickness of the inner seal lip 16 d constituting the sealing member 7 f is designed to have the nearly same thickness throughout the entire length from the base end portion to the tip edge.
  • the thickness of the outer seal lip 14 d is gradually decreasing from the base end portion to the tip edge.
  • an auxiliary seal lip 19 is provided on the radially outer end of the tip edge of this outer seal lip 14 d to project from this tip edge. Then, when the slinger 6 and the sealing member 7 f on the metal core 5 as a support member are engaged as illustrated in FIG.
  • the tip edge of the above auxiliary seal lip 19 comes in slidably contact with the inner surface of the outer circular ring portion 13 , as well as the radially inner edge of the tip end portion of the above outer seal lip 14 d which is radially inwardly displaced from the above auxiliary seal lip 19 comes in slidably contact with the inner surface of the outer circular ring portion 13 .
  • auxiliary seal lip 19 it is possible to prevent foreign matters from entering the slidably contacting region between the radially inner end of the tip end portion of the above outer seal lip 14 d and the inner surface of the above outer circular ring portion 13 . Because of this, the abrasion of this slidably contacting region can be suppressed by preventing hard foreign matters from being bitten by this slidably contacting region. Accordingly, in the case of this example, the sealing performance can be improved. In addition to this, since the above auxiliary seal lip 19 is formed to project from the tip edge of the above outer seal lip 14 d , the cost does not substantially rise.
  • the above auxiliary seal lip 19 sufficiently works as long as it prevents the entrance of foreign matters, and therefore the pressing force of this auxiliary seal lip 19 need not be large. Because of this, it is possible to make small or null the abrasion at the slidably contacting region between the tip edge of this auxiliary seal lip 19 and the inner surface of the above outer circular ring portion 13 . Also, even if there is some abrasion at this slidably contacting region, no influence thereof is exerted upon the sealing performance of the slidably contacting region between the radially inner end of the tip edge of the above outer seal lip 14 d and the inner surface of the outer circular ring portion 13 . Also, since the pressing force of the above auxiliary seal lip 19 can be small, it is possible to prevent the pressing force of the above outer seal lip 14 d from decreasing because of the provision of this auxiliary seal lip 19 .
  • the seal assembly according to the present invention and the rolling bearing implemented therewith can be applied to the case where either the inner or outer race constituting the rolling bearing rotates at the time of use.
  • the seal assembly according to the present invention and the rolling bearing implemented therewith can be used in a hub unit by fitting and fixing the inner race onto the outer peripheral surface of the hub of the hub unit which supports the wheel, and by fitting and fixing the outer race into the supporting hole of a knuckle of the suspension of a motor vehicle.
  • the outer peripheral surface of the above outer race may be formed with a fixed side flange to be fixed to the end surface of the above knuckle. Furthermore, as illustrated in FIG.
  • the seal assembly 17 is implemented in a hub unit in which an inner race 11 a having an inner raceway 21 a in its outer peripheral surface is externally fitted and fixed onto the outer peripheral surface of the inner end of a hub 20 , and an inner raceway 21 b is formed on the outer peripheral surface of the intermediate portion of the above hub 20 in the location apart from this inner race 11 a .
  • a fixed side flange 23 to be fixed to the end surface of the knuckle 22 is formed on the outer peripheral surface of the outer race 8 a .
  • a rotation side flange 34 for fixing a wheel thereto is formed on the outer peripheral surface of the above hub 20 at a location displaced a little to the outer end thereof.
  • FIG. 22 shows a ninth example of the embodiment of the present invention corresponding to the second, third and seventh aspects.
  • the base end portion of a first sealing member 24 is securely connected to the radially inner end of a first metal core 29 having an L-shaped cross section and internally fitted and fixed to the end portion of the outer race
  • the base end portion of a second sealing member 25 is securely connected to the radially outer end of a second metal core 30 having an L-shaped cross section and externally fitted and fixed to the end portion of the inner race.
  • the first sealing member 24 fixed to the above first metal core 29 is formed with an inner seal lip 26 which is a radially oriented seal lip, and the tip edge of this inner seal lip 26 comes in slidably contact with the outer peripheral surface of the radially inner cylindrical portion 12 constituting the above second metal core 30 .
  • the second sealing member 25 fixed to the above second metal core 30 is formed with an intermediate seal lip 27 which is an axially oriented seal lip and an outer seal lip 28 .
  • the outer seal lip 28 among them is located in a radially outer position than the above intermediate seal lip 27 .
  • this intermediate seal lip 27 is arranged to come in slidably contact with a radially intermediate portion of the axially oriented outer surface of the inner circular ring portion 10 constituting the above first metal core 29
  • the tip edge of the above outer seal lip 28 is arranged to come in slidably contact with the inner peripheral surface of the radially outer cylindrical portion 9 constituting the above first metal core 29 .
  • the predetermined relationship is established between two interferences, i.e., the radial interference in the radial direction of the inner cylindrical portion 12 between the tip edge of the above inner seal lip 26 and the outer peripheral surface of the inner cylindrical portion 12 constituting the above second metal core 30 , and the axial interference in the axial direction of the inner circular ring portion 10 between the tip edge of the above intermediate seal lip 27 and the outer surface of the inner circular ring portion 10 constituting the above first metal core 29 .
  • the thickness t1 of the base end portion of the above intermediate seal lip 27 , the thickness t2 of the intermediate portion thereof and the thickness t3 of the tip end thereof satisfy 0.70 ⁇ t2/t1 ⁇ 0.85 and 0.35 ⁇ t3/t1 ⁇ 0.65.
  • FIG. 23 shows a tenth example of the embodiment of the present invention corresponding to the third and eighth aspects.
  • the seal assembly 17 a in accordance with this example is used to seal between the inner peripheral surface of the outer end portion of the outer race 8 a and the intermediate outer peripheral surface of the hub 20 constituting the hub unit as described in FIG. 21 , and composed of a metal core 5 which can be internally fitted and fixed to the outer peripheral surface of the end portion of this outer race 8 a and a sealing member 7 g made of a resilient material with its base end portion attached to this metal core 5 . Then, this sealing member 7 g is provided with three seal lips 31 to 33 having tip edges arranged to come in slidably contact with the outer peripheral surface of the above hub 20 .
  • the outer seal lip 31 located in the outermost position and the intermediate seal lip 32 , in an intermediate position, among these seal lips 31 to 33 , are arranged to have their tip edges come in slidably contact with a side surface inwardly oriented in the axial direction of the rotation side flange 34 provided on the outer peripheral surface of the above hub 20 .
  • the inner seal lip 33 which is located in the innermost position, is arranged to have its tip edge come in slidably contact with the outer peripheral surface of the intermediate portion of the above hub 20 .
  • the predetermined relationship in thickness is established among the base end portion, the tip end and the intermediate portion of each of the above outer seal lip 31 and the intermediate seal lip 32 .
  • the outer and intermediate seal lips 31 and 32 correspond to the axially oriented seal lip according to the third aspect.
  • FIG. 24 shows an eleventh example of the embodiment of the present invention corresponding to the third and seventh aspects.
  • the seal assembly 17 b according to this example is provided with a first seal ring 35 and a second seal ring 36 .
  • the first seal ring 35 is provided with a first metal core 37 , and a first sealing member 38 with a portion being securely connected to this first metal core 37 , an intermediate seal lip 39 and an inner seal lip 40 which are formed at radially inwardly displaced locations of this first sealing member 38 .
  • the above second seal ring 36 is provided with a second metal core 41 , a second sealing member 42 having a portion securely connected to this second metal core 41 , and an outer seal lip 43 formed at a radially outwardly displaced location of this second sealing member 42 .
  • the above first seal ring 35 and the second seal ring 36 are located opposed to each other in the axial direction. Then, the tip edge of the intermediate seal lip 39 of this first seal ring 35 is arranged to come in slidably contact with the radially inwardly oriented side surface of the second metal core 41 constituting the above second seal ring 36 .
  • the tip edge of the inner seal lip 40 of the above first seal ring 35 is arranged to come in slidably contact with the outer peripheral surface of the above inner race 11
  • the tip edge of the outer seal lip 43 of the above second seal ring 36 is arranged to come in slidably contact with the inner peripheral surface of the above outer race 8 .
  • this intermediate seal lip 39 corresponds to the axially oriented seal lip according to the third aspect.
  • the present invention is constructed and operated as mentioned above, it is possible to realize a seal assembly for rolling bearing having an excellent sealing performance and high durability. For this reason, it is possible to prevent various types of foreign matters such as rain water, mud, dust and the like from entering the inside of the rolling bearing, and thereby to improve the durability of the rolling bearing.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Sealing Of Bearings (AREA)
  • Sealing With Elastic Sealing Lips (AREA)
US10/504,528 2002-02-14 2003-02-06 Sealing device, and rolling bearing and hub unit incorporating the sealing unit Abandoned US20050104302A1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
US11/715,890 US7731200B2 (en) 2002-02-14 2007-03-09 Seal assembly, and rolling bearing and hub unit assembled therewith
US11/715,891 US20070152404A1 (en) 2002-02-14 2007-03-09 Seal assembly, and rolling bearing and hub unit assembled therewith

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
JP2002-37306 2002-02-14
JP2002037306 2002-02-14
JP2002-363579 2002-12-16
JP2002363579 2002-12-16
PCT/JP2003/001259 WO2003069177A1 (fr) 2002-02-14 2003-02-06 Dispositif d'etancheite ainsi que roulement et unite de moyeu comprenant ce dispositif d'etancheite

Related Child Applications (2)

Application Number Title Priority Date Filing Date
US11/715,890 Division US7731200B2 (en) 2002-02-14 2007-03-09 Seal assembly, and rolling bearing and hub unit assembled therewith
US11/715,891 Division US20070152404A1 (en) 2002-02-14 2007-03-09 Seal assembly, and rolling bearing and hub unit assembled therewith

Publications (1)

Publication Number Publication Date
US20050104302A1 true US20050104302A1 (en) 2005-05-19

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Family Applications (3)

Application Number Title Priority Date Filing Date
US10/504,528 Abandoned US20050104302A1 (en) 2002-02-14 2003-02-06 Sealing device, and rolling bearing and hub unit incorporating the sealing unit
US11/715,890 Expired - Fee Related US7731200B2 (en) 2002-02-14 2007-03-09 Seal assembly, and rolling bearing and hub unit assembled therewith
US11/715,891 Abandoned US20070152404A1 (en) 2002-02-14 2007-03-09 Seal assembly, and rolling bearing and hub unit assembled therewith

Family Applications After (2)

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US11/715,890 Expired - Fee Related US7731200B2 (en) 2002-02-14 2007-03-09 Seal assembly, and rolling bearing and hub unit assembled therewith
US11/715,891 Abandoned US20070152404A1 (en) 2002-02-14 2007-03-09 Seal assembly, and rolling bearing and hub unit assembled therewith

Country Status (5)

Country Link
US (3) US20050104302A1 (fr)
EP (1) EP1475548B1 (fr)
JP (1) JPWO2003069177A1 (fr)
AU (1) AU2003207062A1 (fr)
WO (1) WO2003069177A1 (fr)

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US20060186603A1 (en) * 2005-02-24 2006-08-24 Freudenberg-Nok General Partnership Dynamic seal
US20100038864A1 (en) * 2006-10-16 2010-02-18 Nok Corporation Sealing device
US20100066030A1 (en) * 2007-01-29 2010-03-18 Nok Corporation Hermetic sealing device
US20100201078A1 (en) * 2006-10-16 2010-08-12 Nok Corporation Sealing device
US20100295254A1 (en) * 2007-11-20 2010-11-25 Masahiro Tabata Sealing device
US20100322545A1 (en) * 2009-06-17 2010-12-23 Schaeffler Technologies Gmbh & Co. Kg Sealing arrangement with an installation aid
US20120068413A1 (en) * 2010-09-17 2012-03-22 Carl Freudenberg Kg Sealing profile
US20130051721A1 (en) * 2010-05-05 2013-02-28 Suresh T. Salunke Sealing Assembly in a Thrust Bearing King Pin Application
US9695937B2 (en) 2014-02-04 2017-07-04 Freudenberg-Nok General Partnership Energy saving seal with vacuum induced counter-balance and rocking feature
US9714710B2 (en) 2014-02-04 2017-07-25 Freudenberg-Nok General Partnership Energy saving self-contact seal with pushing bead
US9759330B2 (en) 2014-02-04 2017-09-12 Freudenberg-Nok General Partnership Energy saving seal with rocking dust lip
US9845825B2 (en) 2014-04-08 2017-12-19 Nrb Bearings Ltd. Roller bearing with enhanced stress bearing capacity

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DE102004025355A1 (de) * 2004-05-19 2006-02-02 Carl Freudenberg Kg Radialwellendichtung
CN101052832B (zh) * 2004-11-02 2011-12-07 株式会社小松制作所 轴承密封件
EP3101292A3 (fr) 2004-12-16 2017-02-22 Uchiyama Manufacturing Corp. Structure d'étanchéité d'un élément de rotation
DE102005012733B4 (de) * 2005-03-19 2016-03-31 Schaeffler Kg Dichtung
JP5564180B2 (ja) * 2006-10-23 2014-07-30 株式会社ジェイテクト 密封装置、転がり軸受および車輪用転がり軸受
JP5328027B2 (ja) * 2009-03-30 2013-10-30 内山工業株式会社 密封装置
JP5452199B2 (ja) * 2009-12-07 2014-03-26 株式会社ショーワ プロペラシャフト装置
JP5530799B2 (ja) * 2010-05-11 2014-06-25 日本ピラー工業株式会社 グランドパッキン装着方法
CN102062214B (zh) * 2010-11-25 2016-06-01 青岛开世密封工业有限公司 无簧分体式防泥水油封及其安装方法
JP2013029129A (ja) * 2011-07-27 2013-02-07 Ntn Corp 密封型転がり軸受
ITTO20120307A1 (it) * 2012-04-06 2013-10-07 Skf Ab Dispositivo anulare di tenuta
JP6518406B2 (ja) * 2014-04-30 2019-05-22 Ntn株式会社 円すいころ軸受
JP6839948B2 (ja) * 2016-09-28 2021-03-10 光洋シーリングテクノ株式会社 農機具の車軸用密封装置
US9651153B1 (en) 2016-10-19 2017-05-16 American Axle & Manufacturing, Inc. Axle assembly and contamination self-trapping seal
JP6947557B2 (ja) * 2017-07-07 2021-10-13 Nok株式会社 密封装置
JP6930027B2 (ja) * 2018-04-06 2021-09-01 Nok株式会社 密封装置
IT201900020112A1 (it) * 2019-10-31 2021-05-01 Skf Ab Dispositivo e sistema di tenuta dinamica ad interferenza con comportamento di contatto migliorato
DE102020105149B3 (de) 2020-02-27 2021-05-06 Carl Freudenberg Kg Dichtring und dessen Verwendung
CN115552136A (zh) * 2020-05-22 2022-12-30 Nok株式会社 密封装置

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US3892418A (en) * 1973-04-04 1975-07-01 Sacomo Sierra Inc Seal ring
US3921992A (en) * 1973-12-21 1975-11-25 Paulstra Sa Seals notably for rotary shafts
US5382098A (en) * 1992-11-24 1995-01-17 Skf France Sealing device including an encoding element for a bearing, and bearing equipped with such a device
US5947611A (en) * 1996-01-22 1999-09-07 Nsk Ltd. Rolling bearing unit with tone wheel
US5967527A (en) * 1996-11-19 1999-10-19 Forsheda Ab Sealing assembly for a moving mechanical member, in particular a rotary shaft of a hydraulic pump
US6082905A (en) * 1997-09-12 2000-07-04 Skf Industrie S.P.A. Sealing assembly for a rolling bearing
US6059663A (en) * 1998-07-13 2000-05-09 Neapco Inc. One-piece sealing system for a universal joint assembly
US6561337B2 (en) * 1999-03-09 2003-05-13 Nsk Ltd. Clutch release bearing
US7004471B2 (en) * 2003-12-17 2006-02-28 General Motors Corporation Radial lip seal

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Publication number Priority date Publication date Assignee Title
US7854432B2 (en) * 2005-02-24 2010-12-21 Freudenberg-Nok General Partnership Dynamic seal
US20060186603A1 (en) * 2005-02-24 2006-08-24 Freudenberg-Nok General Partnership Dynamic seal
US20100038864A1 (en) * 2006-10-16 2010-02-18 Nok Corporation Sealing device
US20100201078A1 (en) * 2006-10-16 2010-08-12 Nok Corporation Sealing device
US20100066030A1 (en) * 2007-01-29 2010-03-18 Nok Corporation Hermetic sealing device
US8557904B2 (en) * 2007-11-20 2013-10-15 Jtekt Corporation Sealing device
US20100295254A1 (en) * 2007-11-20 2010-11-25 Masahiro Tabata Sealing device
US20100322545A1 (en) * 2009-06-17 2010-12-23 Schaeffler Technologies Gmbh & Co. Kg Sealing arrangement with an installation aid
US20130051721A1 (en) * 2010-05-05 2013-02-28 Suresh T. Salunke Sealing Assembly in a Thrust Bearing King Pin Application
US8807842B2 (en) * 2010-05-05 2014-08-19 Nrb Bearings Ltd. Sealing assembly in a thrust bearing king pin application
US20120068413A1 (en) * 2010-09-17 2012-03-22 Carl Freudenberg Kg Sealing profile
US9695937B2 (en) 2014-02-04 2017-07-04 Freudenberg-Nok General Partnership Energy saving seal with vacuum induced counter-balance and rocking feature
US9714710B2 (en) 2014-02-04 2017-07-25 Freudenberg-Nok General Partnership Energy saving self-contact seal with pushing bead
US9759330B2 (en) 2014-02-04 2017-09-12 Freudenberg-Nok General Partnership Energy saving seal with rocking dust lip
US9845825B2 (en) 2014-04-08 2017-12-19 Nrb Bearings Ltd. Roller bearing with enhanced stress bearing capacity

Also Published As

Publication number Publication date
EP1475548A4 (fr) 2007-07-25
US20070152404A1 (en) 2007-07-05
WO2003069177A1 (fr) 2003-08-21
AU2003207062A1 (en) 2003-09-04
JPWO2003069177A1 (ja) 2005-06-09
EP1475548A1 (fr) 2004-11-10
US7731200B2 (en) 2010-06-08
US20070152403A1 (en) 2007-07-05
EP1475548B1 (fr) 2012-04-11

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