US20010002939A1 - Sealed rolling bearing - Google Patents
Sealed rolling bearing Download PDFInfo
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- US20010002939A1 US20010002939A1 US09/769,254 US76925401A US2001002939A1 US 20010002939 A1 US20010002939 A1 US 20010002939A1 US 76925401 A US76925401 A US 76925401A US 2001002939 A1 US2001002939 A1 US 2001002939A1
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- Prior art keywords
- seal
- bearing
- inner race
- rolling bearing
- sealed rolling
- Prior art date
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Classifications
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- 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
- F16C33/30—Parts of ball or roller bearings
- F16C33/58—Raceways; Race rings
- F16C33/60—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
- F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
- F16C19/38—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers
- F16C19/383—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
- F16C19/388—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with four rows, i.e. four row tapered roller bearings
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- 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
- F16C33/726—Sealings with means to vent the interior of the bearing
-
- 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
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- 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
- F16C19/52—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions
- F16C19/525—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions related to temperature and heat, e.g. insulation
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S277/00—Seal for a joint or juncture
- Y10S277/928—Seal including pressure relief or vent feature
Definitions
- the intermediate seal 719 is comprised of an annular support member 729 having a U-shaped cross section, and a pair of lips 759 , 759 formed of elastic members which are fixedly provided in bent portions 729 a, 729 a formed at the both ends of the annular support member 729 .
- the tip ends of the both lips 759 , 759 are brought into contact with the side surfaces of the recess 9 , and a gap between the contact surfaces 13 c, 13 c of the paired inner races 13 , 13 is sealed, whereby the air-tight condition inside the bearing can be maintained.
- the intermediate seal has a core metal 929 , and the main body of the seal is brought into contact with the side wall and the bottom wall of the recess of the left inner race 613 ′.
- a seal lip 939 b protruding from the main body 919 a of the intermediate seal 919 is brought into pressure contact with the side wall of the recess 609 of the right inner race 613 ′ toward the inside of the bearing.
- FIGS. 16A and 16B The structure of a rolling bearing according to a twelfth embodiment shown in FIGS. 16A and 16B is the same C 19 as that shown in FIG. 1, apart from an intermediate seal thereof.
Abstract
A sealed rolling bearing in which a rolling member is disposed in a bearing space formed between an outer race and an inner race to rotate the outer race and the inner race relatively to each other, and rotation seal members are disposed at the both ends of the bearing space in the axial direction thereof while a stationary seal member is disposed on the side of the inner race, thereby sealing the bearing space. The bearing is provided with vent means on the side of the inner race for approximating a fluid pressure in the bearing space to an outside fluid pressure by causing the inside of the bearing space to communicate with the outer when the state of the fluid in the bearing space and state of the outside fluid become a predetermined relationship.
Description
- This application claims the benefits of Japanese Application Nos. 10-227525 and 11-208150 which are hereby incorporated by reference.
- 1. Field of the Invention
- The present invention relates to a sealed rolling bearing for preventing water, or the like, from invading from outside into the bearing space.
- 2. Related Background Art
- As a bearing to be used in an environment in which it may be splashed with fluid including water, such as a roll neck bearing of a rolling mill in steel mill equipment, a sealed rolling bearing provided with a sealing device as proposed in Japanese Patent Publication No. 60-14933, No. 61-12130, or the like, is used.
- A four-row tapered roller bearing provided with a seal for hermetically sealing is shown in FIG. 30 as one example of the sealed rolling bearing. Note that FIG. 30 shows an upper half of the longitudinal cross-section of the bearing excluding the shaft thereof.
- The sealed roller bearing shown in the same Figure is provided with a large number of
rollers outer races inner races inner races outer races seal holders outer races seals elastic lips sales inner races - FIG. 31 is a view for illustrating the shape of an
intermediate seal 9 which is retained on the inner surface of a portion in which theinner races intermediate seal 9 is arranged to prevent water, or the like, from invading into the bearing space S chiefly which the roll is attached or detached. - FIG. 22 shows another example9′ of the intermediate seal which has been conventionally used. This
intermediate seal 9′ haslip portions bottom surfaces inner races - [Problems to be solved by the Invention]
- However, the conventional hermetically sealed rolling bearing mentioned above can not satisfactorily prevent the invasion of water or the like, under a severe environment with drastic change in temperature.
- For example, when the sealed rolling bearing shown in FIG. 30 is used as a roll neck bearing for a rolling mill in steel mill equipment, the number of rotation of the roll which is supported by this hermetically sealed rolling bearing is frequently changed. More specifically, a high-speed rotation, low idling rotation, and a halt are repeated for the roll, and the temperature inside the sealed rolling bearing changes depending on each of the conditions. For this reason, expansion and contraction of the air or the like in the bearing space are repeated, the internal air which is expanded upon the increase in the temperature escapes from the
elastic seals - The value of this negative pressure becomes larger and is maintained longer when the temperature inside the bearing space S which has been high becomes lower (or a difference of the temperature is larger), that is, the number of rotation of the roll which has been rotating at a high speed becomes smaller (a difference of rotation is larger). These conditions are shown in FIG. 28A, FIG. 28B and FIG. 28C. These views respectively show the number of rotation of the roll, the temperature in the bearing (the temperature inside the bearing space S), and the internal pressure of the bearing (the pressure in the bearing space S), with respect to the time (along the abscissa) in that order.
- Also, when the internal temperature is 100° C. or higher with a little water existing inside, this water is expanded as vapor, and a large negative pressure is generated when the temperature decreases. This negative pressure accelerates abrasion of the elastic seal lips of the
seals seals seals - As described above, it is confirmed that when a great negative pressure is generated in the bearing space S, the greater the negative pressure is, the easier the invasion of external fluid such as water through the
lip portion 8 a of the elastic seal becomes. More specifically, as clearly seen from FIG. 29, the greater the negative pressure is (more to the left of the abscissa in the figure), the easier the flow of water into the sealed bearing becomes, thereby increasing an amount of the mixed water. The easier inflow of water means a degraded sealing function. In addition, the water inflow and the degraded sealing function accelerate deterioration of the lubricant in the bearing space S to degrade the bearing performance, thereby causing early damage or early peeling-off. - Accordingly, an object of the present invention is to provide a hermetically sealed rolling bearing capable of preventing deterioration of a lubricant due to the inflow of water which may be caused by the negative pressure in the bearing space, thereby preventing deterioration of the bearing performance, early damage, early peeling-off, etc.
- In order to achieve the above object, there is provided a hermetically sealed rolling bearing in which rolling members are disposed in a bearing space formed between an outer race and an inner race to rotate the outer race and the inner race relatively to each other, and side seal members are disposed at the both ends of the bearing space in the axial direction thereof while a bore seal member is disposed on the side of the inner race, thereby sealing the bearing space, characterized in that: there is provided vent means on the side of the inner race for approximating a fluid pressure in the bearing space to an outside fluid pressure when the state of the fluid in the bearing space and the state of the outside fluid becomes a predetermined relationship.
- Here, in the sealed rolling bearing according to the present invention, there is provided the vent means on the inner race side to approximate the fluid pressure in the bearing space to the fluid pressure outside when the state of the fluid in the bearing space and the state of the fluid outside reaches a predetermined relationship. Thus, even if, for example, the heated sealed rolling bearing is cooled, the fluid pressure in the bearing space is approximated to the fluid pressure outside so as not to pull the water or the like into the bearing space. Also according to the present invention, the vent mechanism is disposed at a position which is hardly exposed to external water or the like, compared with a
seal 18 and aseal holder 17 in an embodiment of the present application shown in FIG. 1, so that the above-mentioned function can be realized in a simpler and a more secured manner, than the case in which the vent mechanism is provided on these members. - FIG. 1 is a longitudinal cross-sectional view for showing the structure of a rolling bearing according to the first embodiment of the present invention.
- FIG. 2A is an enlarged cross-sectional view for illustrating a seal formed between inner races of the sealed rolling bearing shown in FIG. 1, and FIG. 2B is a view for illustrating the main portion of this seal.
- FIG. 3A is an enlarged cross-sectional view for illustrating a seal formed between inner races of a sealed rolling bearing according to the second embodiment of the present invention, and FIG. 3B is a view for illustrating the main portion of the seal.
- FIG. 4 is an enlarged cross-sectional view for illustrating a seal formed between inner races of a sealed rolling bearing according to the third embodiment of the present invention.
- FIG. 5 is an enlarged cross-sectional view for illustrating a seal formed between inner races of a sealed rolling bearing according to the fourth embodiment of the present invention.
- FIG. 6 is an enlarged cross-sectional view for illustrating a seal formed between inner races of a sealed rolling bearing according to the fifth embodiment of the present invention.
- FIG. 7 is a longitudinal cross-sectional view for showing the structure of a rolling bearing according to the sixth embodiment of the present invention.
- FIG. 8 is an enlarged cross-sectional view for illustrating a seal formed between inner races of the sealed rolling bearing according to the sixth embodiment of the present invention.
- FIG. 9 is an enlarged cross-sectional view for illustrating a seal formed between inner races of a sealed rolling bearing according to the seventh embodiment of the present invention.
- FIG. 10 is a view for illustrating an operation of the seal of FIG. 9.
- FIG. 11 is a view for illustrating the operation of the seal of FIG. 9.
- FIG. 12A is an enlarged cross-sectional view for illustrating a seal formed between inner races of a sealed rolling bearing according to the eighth embodiment of the present invention; FIG. 12B is a view for showing a part of FIG. 12A in a state where a seal lip is flexed due to the centrifugal force; and FIG. 12C is a view for illustrating a part of the seal seen from the inside in the radial direction.
- FIG. 13 is an enlarged cross-sectional view for illustrating a seal formed between inner races of a sealed rolling bearing according to the ninth embodiment of the present invention.
- FIG. 14 is an enlarged cross-sectional view for illustrating a seal formed between inner races of a sealed rolling bearing according to the tenth embodiment of the present invention.
- FIG. 15 is an enlarged cross-sectional view for illustrating a seal formed between inner races of a sealed rolling bearing according to the eleventh embodiment of the present invention.
- FIG. 16A is an enlarged cross-sectional view for illustrating a seal formed between inner races of a sealed rolling bearing according to the twelfth embodiment of the present invention, and FIG. 12B is a view for illustrating a part of the seal seen from the inside in the radial direction.
- FIG. 17A is an enlarged cross-sectional view for illustrating a seal formed between inner races of a sealed rolling bearing according to the thirteenth embodiment of the present invention, and FIG. 17B is a view for illustrating a part of the seal seen from the inside in the radial direction.
- FIG. 18 is an enlarged front view for illustrating a seal formed between the inner races of the sealed rolling bearing of the thirteenth embodiment.
- FIG. 19A is an enlarged cross-sectional view for illustrating a seal formed between inner races of a sealed rolling bearing according to the fourteenth embodiment of the present invention, and FIG. 19B is a cross-sectional view for illustrating an operation of the seal.
- FIG. 20A is an enlarged cross-sectional view for illustrating a seal formed between inner races of a sealed rolling bearing according to the fifteenth embodiment of the present invention, and FIG. 20B is a partial cross-sectional view of the seal when the bearing is mounted on the shaft.
- FIG. 21 is an enlarged front view for illustrating a seal formed between inner races of a sealed rolling bearing of the sixteenth embodiment.
- FIG. 22 is an enlarged partial cross-sectional view for illustrating a seal of the prior art.
- FIG. 23 is a view for illustrating a seal of the present invention which is used in a comparative experiment between the seal of the present invention and that of the prior art.
- FIG. 24 is a view for illustrating a seal of the prior art which is used for a comparative experiment between the seal of the present invention and that of the prior art.
- FIG. 25 is a graph for showing a result of the comparative test (in the stopped state).
- FIG. 26 is a graph for showing a result of the comparative test (in the rotating state).
- FIG. 27 is partial cross-sectional view for illustrating an experimental apparatus used in the comparative experiment.
- FIG. 28A is a graph for showing the number of rotation, FIG. 28B is a graph for showing the temperature inside the bearing, and FIG. 29C is a graph for showing the pressure inside the bearing, respectively for the used time of the bearing.
- FIG. 29 is a graph for showing the internal pressure of the bearing and an mount of mixed water inside the bearing, with respect to the sealed rolling bearing of the prior art.
- FIG. 30 is a view for illustrating the structure of the sealed rolling bearing of the prior art.
- FIG. 31 is an enlarged view of the main portion of the intermediate seal shown in FIG. 30.
- Embodiments of the present invention will be described below with reference to the drawings.
- (First Embodiment)
- FIG. 1 shows a longitudinal cross section of a four-row Tapered roller bearing provided with a seal for hermetically sealing as a first embodiment of a sealed rolling bearing according to the present invention. Note that this view shows an upper part of the longitudinal cross section of the bearing excluding the shaft thereof.
- The four-row Tapered roller bearing10 with the seal for hermetically sealing (hereinafter called the “sealed rolling bearing”) shown in FIG. 1 comprises
outer races 11, 12, 11,inner races rollers outer races 11, 11, 12 and theinner races retainers rollers intermediate rings outer race 12 and the outer races 11, 11,seal holders seal holders intermediate seal 19 retained by arecess 9 which is formed on the inner diameter surface of a portion in which the pair ofinner races - The whole outer race is constituted by the single-low outer races11, 11 disposed at the both end portions in the axial direction and the double-low
outer race 12 which is formed by two single-low outer races connected with each other. Taper surfaces 11 a, 11 a, 12 a are formed on the inner peripheries of theouter races 11, 11, 12, respectively. - The whole inner race is constituted by the two double-row
inner races inner races outer races 11, 12 mentioned above, so as to constitute a bearing space S with these taper surfaces 11 a, 12 a. Aroll shaft 8 is loosely fitted in theinner races inner races roll shaft 8 with a small gap therebetween. The right and left end portions of theinner races lip sliding surfaces elastic lips - The four rows of
rollers outer races 11, 12 and the outer peripheral surfaces of theinner races rollers 14 is rotated in a predetermined direction when theinner races roll shaft 8, whereby theinner races outer races - The four
annular retainers retainers 15 supports a large number ofrollers - The outer race
intermediate rings outer race 12 and the single-row outer race 11 on the tip end (left) side and between the double-rowouter race 12 and the single-row outer race 11 on the base end (right) side, respectively. - The
seal holders - The side seals18, 18 which serve as rotation seal members are supported on the inner peripheral sides of the above-mentioned
seal holders elastic lips lip sliding surfaces inner races - The
intermediate seal 19 serving as a bore seal member is formed to be annular and is fitted to be retained in arecess 9 formed on the inner diameter surface side of surfaces with which the pair of theinner races intermediate seal 19, there is formed a vent portion described later (omitted in FIG. 1) for ventilating the air under an appropriately applied pressure. - FIG. 2A is a partial enlarged cross-sectional view for illustrating the portion A in FIG. 1, in order to describe the structure of the
intermediate seal 19. FIG. 2A is an enlarged view of a cross section of theintermediate seal 19, while FIG. 2B is an enlarged view of the vent portion of theintermediate seal 19, seen from the direction indicated by the arrow C. - The
intermediate seal 19 is comprised of acore metal 29 for maintaining the shape of the seal, and anelastic member 39 such as a rubber tightly in contact with therecess 9. Alip 59 having elasticity is extended from themain part 49 of theelastic member 39. Themain part 49 is brought into contact with the bottom wall and the side wall of the recess of one of theinner races 13, and thelip 59 is brought into contact with the side wall of the recess of the otherinner race 13. As a result, a gap between the contact surfaces 13 c, 13 c of the pairedinner races - On the root side of the
lip 59, there is formed avent hole 69 serving as the vent means. The vent holes 69 may be formed over the entire periphery of theintermediate seal 19 at appropriate intervals. Apartition wall 69 a is formed integrally in a middle part of eachvent hole 69. Thispartition wall 69 a is formed of a thin elastic member, and is provided with a slit 69 b which is extended to the both ends of the wall through the center thereof. The slit 69 b functions as a valve mechanism and is closed when no pressure difference is generated between the inside of the bearing (the bearing space S in FIG. 1) and the outside of the bearing, but forms a small gap when a pressure difference is generated between the inside of the bearing and the outside of the bearing (for example, when the pressure inside the sealed rolling bearing becomes negative), thereby forming the vent mechanism. Even if the air volume in the bearing changes due to a change in temperature inside the bearing during the operation of the sealed rolling bearing, the air can be sucked from the outside of the bearing into the bearing or can be evacuated from the inside of the bearing to the outside of the bearing by means of a function of the slit 69 b, whereby the pressure difference between the inside and the outside of the bearing can be automatically balanced. - In addition, the slit69 b is usually closed unless a considerable pressure is applied, so as to serve to prevent water or other pollutant from invading into the bearing through the
vent hole 69. Here, the slit 69 b is disposed at a position which is hardly exposed to the water or other liquid, compared with the case in which the vent hole is formed on theseal holder 17 or on theside seal 18, so that the invasion of water or the like into the bearing through thevent hole 69 can be securely prevented. - Note that the slit69 b as mentioned above is provided on the
intermediate seal 19 for sealing the gap between theinner races vent hole 69. - (Second Embodiment)
- A sealed rolling bearing according to a second embodiment of the invention will be described in the following. Note that the sealed rolling bearing according to the second embodiment is the same as that according to the first embodiment shown in FIG. 1, apart from an
intermediate seal 119. - In the following description of each of the embodiments, identical portion are given the same referential numbers and symbols to save redundant description.
- FIG. 3 is a view for illustrating the structure of the
intermediate seal 119 for sealing a sealed rolling shaft on the side of theinner races intermediate seal 119, while FIG. 3B is a view for illustrating an operation of a vent portion of theintermediate seal 119. - The
intermediate seal 119 is comprised of acore metal 129 for maintaining the shape of the seal, and anelastic member 139 in tight contact with therecess 9. Alip 159 having elasticity is extended from themain part 149 of theelastic member 139. Themain part 149 is brought into contact with the bottom wall and the side wall of the recess of one of theinner races 13, and thelip 59 is brought into contact with the side walls of the otherinner race 13. As a result, a gap between the contact surfaces 13 c, 13 c of the pairedinner races - On the tip end side of the
lip 159, there are formed with cut-awayportions 169. The cut-awayportions 169 may be formed over the entire periphery of theintermediate seal 119 at appropriate intervals. Apartition wall 169 a is formed on the roll shaft side of each cut-awayportion 169. Thispartition wall 169 a is formed of a thin elastic member, and is in tight contact with the side surface of therecess 9 when no pressure difference is generated between the inside of the bearing and the outside of the bearing, but is separated a little from the side surface of the recess when a pressure difference is generated between the inside of the bearing and the outside (FIG. 3B), thereby forming a vent mechanism. Thus, even if the air volume in the bearing changes due to a change in temperature inside the bearing during the operation of the sealed rolling bearing, the pressure difference between the inside and the outside can be automatically balanced. - In addition, the
partition wall 169 a is usually in tight contact with the side surface of therecess 9 unless a considerable pressure is applied, and also serves to prevent water or other pollutant from invading into the bearing through thenotch 169. - (Third Embodiment)
- A sealed rolling bearing according to a third embodiment of the invention will be described below with reference to FIG. 4. Note that the sealed rolling bearing according to the third embodiment is the same as that according to the first embodiment, apart from an
intermediate seal 219. - FIG. 4 is an enlarged cross-sectional view for illustrating the structure of the
intermediate seal 219 for sealing the sealed rolling shaft on the side of theinner races - The
intermediate seal 219 is comprised of acore metal 229 for maintaining the shape of the seal, and anelastic member 239 in tight contact with therecess 9. Alip 259 having elasticity is extended from themain part 249 of theelastic member 239. Themain part 249 is brought into contact with the bottom wall and the side wall of the recess of one of theinner races 13, and thelip 259 is brought into contact with the side wall of the recess of the otherinner race 13. As a result, a gap between the contact surfaces 13 c, 13 c of the pairedinner races - On the root side of the
lip 259, there are formed vent holes 269. The vent holes 269 may be formed over the entire periphery of theintermediate seal 219 at appropriate intervals. Thisvent hole 269 is formed to be transparent and has no partition wall on which a slit serving as a valve mechanism is not formed. Even if the vent mechanism is formed by thevent hole 269 and the air volume inside the bearing changes due to a change in temperature inside the bearing, the air can be sucked from the outside of the bearing into the bearing or can be evacuated from the inside of the bearing to the outside of the bearing, whereby the pressure difference between the inside and the outside of the bearing can be automatically balanced. - Taking into consideration the fact that the sealed rolling bearing according to the third embodiment is used in an environment into which water or the like hardly invade from the side of the
inner races vent hole 269 itself is disposed at a position which is hardly exposed to water or the like directly, but no slit is formed to serve as the vent mechanism. - (Fourth Embodiment)
- A sealed rolling bearing according to a fourth embodiment of the invention will be described below with reference to FIG. 5. Note that the sealed rolling bearing according to the fourth embodiment is the same as that according to the first embodiment, apart from portions described below.
- FIG. 5 is an enlarged cross-sectional view for illustrating the structure of a portion in which the
inner races - In the vicinity of the
contact surface 113 c of eachinner race 113, there is formed avent hole 113 e. The vent holes 113 e may be formed over the entire periphery of theinner race 113 at appropriate intervals. - The intermediate seal319 is comprised of a
core metal 329 for maintaining the shape of the seal, and anelastic member 339 in tight contact with therecess 9. Alip 359 having elasticity is extended from themain part 349 of theelastic member 339. Themain part 349 is brought into contact with the bottom wall and the side wall of the recess of one of theinner races 13, and thelip 359 is brought into contact with the side wall of the recess of the otherinner race 113. A gap between the contact surfaces 113 c, 113 c of the pairedinner races lip 359 has no vent hole. - In this embodiment, a vent mechanism is constituted by
vent holes inner races vent hole - (Fifth Embodiment)
- A sealed rolling bearing according to a fifth embodiment of the invention will be described below with reference to FIG. 6. Note that the sealed rolling bearing according to the fifth embodiment is the same as that according to the first embodiment, apart from an
intermediate seal 419. - FIG. 6 is an enlarged cross-sectional view for illustrating the structure of the
intermediate seal 419 for sealing a sealed rolling shaft on the side of theinner races - The
intermediate seal 419 is comprised of acore metal 429 for maintaining the shape of the seal, and anelastic member 439 in tight contact with therecess 9. A pair oflips main part 449 of theelastic member 439. Thelip 459 is brought into contact with the side wall of therecess 9, and thelip 559 is brought into contact with the bottom surface of therecess 9. - The
lips vent holes lips - In a middle part of each of the vent holes469, 569, there is formed a
partition wall partition walls lips lips - (Sixth Embodiment)
- A sealed rolling bearing according to a sixth embodiment of the invention will be described below with reference to FIGS. 7 and 8. Note that in the sealed rolling bearing according to the sixth embodiment, the inner races, the intermediate seal, etc., which forms the sealed rolling bearing of the first embodiment are modified to have other structures.
- FIG. 7 shows a longitudinal cross section of a four-row tapered roller bearing provided with a seal for sealing as the sixth embodiment of a sealed rolling bearing according to the present invention. Note that this view shows an upper part of the longitudinal cross section of the bearing excluding the shaft thereof. Note that the four-row tapered bearing according to the sixth embodiment has the same structure as that shown in FIG. 1, apart from portions opposite to each other of the
inner races intermediate seal 619 provided therein. Structural portions identical to those shown in FIG. 1 will be indicated only by the referential numerals and symbols and detailed description thereof will be omitted. Only the structural portions which are different from those in FIG. 1 will be described below. - In the sixth embodiment, a recess609 (see FIG. 8) is formed on the outer diameter side of surfaces with which a pair of
inner races intermediate seal 619 is fitted in thisrecess 609 to be retained. A vent portion (omitted in the drawing) for ventilating the air under an appropriately applied pressure is formed in a part of thisintermediate seal 619. - FIG. 8 is an enlarged cross-sectional view of the part A in FIG. 7, for illustrating the structure of the
intermediate seal 619 for hermetically sealing the sealed rolling bearing on the inner diameter sides of theinner races - The
intermediate seal 619 is comprised of themain body 619 a and a pair ofannular protrusions main body 619 a is sandwiched by and between the end surfaces 613 c, 613 c of the pairedinner races rings annular protrusions recesses 609 formed on the pairedinner races inner races rings 600. 600, thereby maintaining the air-tight condition inside the bearing. - A part of the
intermediate seal 619 which is approximated to oneend surface 613 c of themain body 619 a of the seal is provided with a longitudinallyelongated space 619 d which is obtained by cutting away a part of themain body 619 a. Thespaces 619 d may be formed over the entire periphery of the bearing. Thisspace 619 d communicates with the outside of the bearing or the inner peripheries of theinner races inner races vent hole 619 f is extended substantially from the center of thisspace 619 d to reach the inside of the bearing, that is, the outer periphery of themain body 619 a. - The
vent hole 619 f formed on the main body of theintermediate seal 619 is arranged to suck the air from the outside of the bearing into the bearing, or to evacuate the air from the inside of the bearing to the outside, so as to balance a pressure difference between the inside and the outside of the bearing. Thevent hole 619 f may be provided with suitable valve means or a suitable portion wall which permits gas to pass but does not permit fluid to pass. - (Seventh Embodiment)
- A sealed rolling bearing according to a seventh embodiment of the invention will be described below. Note that the sealed rolling bearing according to the seventh embodiment is the same as that according to the first embodiment, apart from an
intermediate seal 719. - FIG. 9 is an enlarged cross-sectional view for illustrating the structure of the
intermediate seal 719 for sealing a sealed rolling shaft on the side of theinner races - The
intermediate seal 719 is comprised of anannular support member 729 having a U-shaped cross section, and a pair oflips bent portions annular support member 729. The tip ends of the bothlips recess 9, and a gap between the contact surfaces 13 c, 13 c of the pairedinner races - FIG. 10 is an enlarged cross-sectional view corresponding to FIG. 9, for showing the heated state of the
intermediate seal 719. As clearly seen from the drawing, when theannular support member 729 is heated, thebent portions annular support member 729 are further bent so that thelips bent portions recess 9. As a result, the air can be sucked from the outside of the bearing into the bearing, or can be evacuated from the inside of the bearing to the outside, so as to automatically balance a pressure difference between the inside and the outside of the bearing. Note that when theannular support member 729 returns to the normal temperature, the shape thereof returns to its original one, and thelips recess 9. Consequently, the inside and the outside of the bearing can be sealed. - FIG. 11 is a view for illustrating the structure of the
annular support member 729. Thisannular support member 729 is formed bybonding plate members bent portions annular support member 729 is at the normal temperature. On the other hand, when theannular support member 729 becomes at a high temperature, thebent portions annular support members 729 return to the normal temperature, thebent portions - In the above description, a member which is obtained by bonding the
plate members annular support member 729. However, it is possible to use a bimetal member, instead, which is obtained by bonding materials having different coefficients of linear expansion. In this case, with an increase in temperature inside the sealed rolling bearing, the bimetal can be bent to remove the pressure difference between the inside and the outside of the bearing. - Note that the
roll shaft 8 which is supported by theinner races inner races inner races intermediate seal 719 of the seventh embodiment, since thelips inner races roll shaft 8 is exchanged, the invasion of water or the like can be securely prevented. - Also, in the above description, the
lips recess 9. However, it is not always necessary to completely separate thelips recess 9. For example, if a contact pressure with which thelips recess 9 is adjusted by using deformation of theannular support member 729, both the sealing function and the ventilating function can be provided, so that when the sealing function is degraded, generation of a negative pressure inside the bearing can be prevented to some extent. - In addition, it is possible to provide a seal portion of various kind of material which is deformed upon a change in temperature, so as to adjust the atmospheric pressure inside and outside the bearing by stopping or degrading the sealing function upon the increase in temperature of the bearing.
- (Eighth Embodiment)
- A sealed rolling bearing according to an eighth embodiment of the invention will be described below with reference to FIG. 12. Note that the sealed rolling bearing according to the eighth embodiment is the same as that according to the first embodiment, apart from an
intermediate seal 819. - FIG. 12 is an enlarged cross-sectional view for illustrating the structure of the
intermediate seal 819 for sealing a sealed rolling shaft on the side of theinner races - The
intermediate seal 819 is comprised of acore metal 829 for maintaining the shape of the seal, and anelastic member 839 which is in tight contact with the side walls and the bottom wall of therecess 9 of one of theinner races 13. Onelip 839 b having elasticity is extended from the main part 849 of theelastic member 839. The lip 838 b is brought into contact with the side surface of therecess 9 of the otherinner race 13 toward the inside of the bearing. - When the
lip 839 b is brought into contact with the side wall of the recess inward as described so as to generate the negative pressure inside the bearing, or when the inner races are rotated upon driving of the apparatus, the lip is easily flexed due to the centrifugal force, to exhibit the ventilating function (see FIG. 12B). - The
lip 839 b may be provided withslits 839 c over the entire periphery thereof at proper positions in the axial direction, as shown in FIG. 12C, or, instead of the slits, may be provided with portions having different rigidity so as to adjust the degree of the enhanced ventilating function when the negative pressure is generated or when the bearing is driven. - (Ninth Embodiment)
- A sealed rolling bearing according to a ninth embodiment of the invention shown in FIG. 13 is provided with a
recess 609 which is formed on the outer diameter surface side of the facing surfaces of theinner races 613′, 613′. The facing surfaces other than therecess 609 are brought into contact with each other. Anintermediate seal 919 having the same structure as theintermediate seal 819 shown in FIG. 12 is provided in therecess 609. The third embodiment has the same structure as those of the first and sixth embodiments, apart from theinner races 613′, 613′ and theintermediate seal 919. - In the ninth embodiment, the intermediate seal has a
core metal 929, and the main body of the seal is brought into contact with the side wall and the bottom wall of the recess of the leftinner race 613′. Aseal lip 939 b protruding from the main body 919 a of theintermediate seal 919 is brought into pressure contact with the side wall of therecess 609 of the rightinner race 613′ toward the inside of the bearing. - It is possible to provide slits in the same manner as in the eighth embodiment, or portions having different rigidity also on the
lip 939 b of theintermediate seal 919 according to the ninth embodiment. - A function of the intermediate seal in the ninth embodiment is the same as that of the seal of the sixth embodiment shown in FIG. 7.
- (Tenth Embodiment)
- FIG. 14 shows a tenth embodiment of the invention. The tenth embodiment has the same structure as that of the rolling bearing of the sixth embodiment, apart from an intermediate seal thereof.
Inner races recess 609 on the facing surfaces of the inner races on the outer diameter side, with a predetermined gap between the facing surfaces. - An annular intermediate seal A19 takes a bilateral symmetrical form having portions A39 b, A39 c which are extended from the main body portion A39 a through the
recess 609 of the both inner races toward the both ends in the axial direction, and a portion A39 d which is brought into contact with the facing surfaces of theinner races - Recesses A39 e, A39 f are respectively formed on the main body A39 a of the intermediate seal to face the bottom wall of the recess of the
inner races inner races - A function of this intermediate seal A39 is the same as that of the sixth embodiment.
- (Eleventh Embodiment)
- The structure of a rolling bearing shown in FIG. 15 according to an eleventh embodiment of the invention is the same as that shown in FIG. 1, apart from an intermediate seal B19 thereof. More specifically, according to the eleventh embodiment, the structures of the
inner races vent hole 69 which is provided on theintermediate seal 19 of the first embodiment shown in FIG. 2. - (Twelfth Embodiment)
- The structure of a rolling bearing according to a twelfth embodiment shown in FIGS. 16A and 16B is the same C19 as that shown in FIG. 1, apart from an intermediate seal thereof.
- The intermediate seal C19 of the twelfth embodiment is different from that of the first embodiment only in the position of a vent hole. In the twelfth embodiment, the intermediate seal C19 is comprised of an elastic member C39 and a core metal C29. The elastic member C39 is integrally formed with a main body C39 a and a lip 39 b. A vent hole C39C is formed in the main body C39 a, and a cross-shaped slit C39 e is formed on a partition wall C39 d on the bottom of the vent hole.
- The ventilating function according to the twelfth embodiment is the same as that of the first embodiment and that of the eleventh embodiment. In addition, according to the present embodiment, since the vent hole is not formed in the lip portion, an adverse influence of the vent hole on the performance of the lip can be avoided.
- Instead of having the slit C39 e, the partition wall C39 d may be made of a material which transmits only gases and no liquid as shown in FIG. 15.
- (Thirteenth Embodiment)
- The structure of a rolling bearing according to a thirteenth embodiment shown in FIG. 17 is the same as that shown in FIG. 1, apart from an intermediate seal D19.
- The intermediate seal D19 of the thirteenth embodiment is comprised of a core metal D29 and an elastic member D39. The elastic member D39 is integrally formed with a main body D39 a and a lip D39 b which is protruded from the main body. The main body D30 a is urged upon the side wall and the bottom wall of the
recess 9 of the leftinner race 13, and the tip end of the lip D39 b is urged upon the side walls of therecess 9 of the rightinner race 13 outward the outside of the bearing. - In the thirteenth embodiment, there are respectively formed between the main body D39 a of the elastic member D39 and the bottom wall and the side walls of the
recess 7 of the leftinner race 13 axial slits D39 c and radial slits D39 d at proper intervals over the entire periphery thereof. The slit D39 c and the slit D39 d communicate with each other, to form a vent portion. The axial slit D39 c and the radial slit D39 d are preferably provided with a little phase shift therebetween. - FIG. 18 is a schematic view of this intermediate seal D39, seen from the left side in FIG. 17, for illustrating one of the plural axial slits D39 c and one of the plural radial slits D39 d.
- The function of the thirteenth embodiment is the same as that of the first embodiment.
- In addition, it is possible to form interception ribs D39 e projected radially outwardly in the main body D39 a of the elastic member of the intermediate seal D19 at several positions in the circumferential direction so as to intercept between the radial slit D39 and the axial slit D39C at the outer periphery of the seal, thereby setting a longer flow path. Consequently, the function of preventing invasion of water or other foreign substances through the slit D39 d can be enhanced.
- It is also possible to provide a valve with a slit, like in the first embodiment shown in FIG. 2, or a filter member to transmit only gases but no fluid, like in the eleventh embodiment shown in FIG. 15, in the flow path of a vent mechanism which includes the axial slits D39 c and the radial slits D39 e.
- (Fourteenth Embodiment)
- A rolling bearing of a fourteenth embodiment shown in FIG. 19 is the same as that of the first embodiment, except an intermediate seal E19.
- The intermediate seal E19 in the fourteenth embodiment has a bilateral symmetrical structure, comprised of a pair of annular core metal members E29 a, E29 b which are made of bimetal or shape memory alloy and separated from each other bilaterally and symmetrically, and an annular elastic member E39. The elastic member E39 has a radially-outward annular protrusion E39 b at the center thereof protruded in the axial direction from the main body E39 a. The radially-outward annular protrusion E39 a has a flat outer peripheral surface. Annular lip portions E39 b, E39 c are formed at the both ends in the axial direction to be outward over the entire periphery from the main body E39 a of the elastic member E39. The axial annular lip portions E39 c, E39 d are urged upon the side walls of the recess formed by the
inner races - The intermediate seal E19 of the fourteenth embodiment is inclined as a whole, as shown in FIG. 19B, due to the function of the core metals E29 a, E29 b made of bimetal or shape memory alloy, when the bearing temperature is increased during the operation, whereby the ventilating function can be enhanced to remove the pressure difference between the inside and the outside of the bearing.
- (Fifteenth Embodiment)
- A rolling bearing of a fifteenth embodiment shown in FIG. 20 is the same as that of the first embodiment, apart from an intermediate seal F19.
- According to the fifteenth embodiment, the intermediate seal F19 which is fitted with pressure in a recess between the facing surfaces of the
inner races inner race 13 and a lip portion F39 b protruding from the main body. A central downward bent portion of the lip portion F39 b takes an inner position in the radial direction than the inner diameter surfaces of theinner races roller shaft 8 as shown in FIG. 20A. On the other hand, the tip end of the lip is urged upon the side walls of the recess of the rightinner race 13 to be tightly sealed, thereby preventing water or other foreign substances from invading from the inner diameter side into the bearing. In this intermediate seal F19, when the rolling bearing is assembled in theshaft 8, as shown in FIG. 20B, the inner diameter surface of the lip F39 b′ is pushed onto the outer peripheral surface of theshaft 8 to be flexed outward in the radial direction, so that the tip end of the lip is separated from the side walls of the recess of the rightinner race 13 to enhance the ventilating function. - (Sixteenth Embodiment)
- A rolling bearing of a sixteenth embodiment of the invention shown in FIG. 21 is the same as that of the first embodiment shown in FIG. 1, apart from an intermediate seal G19.
- According to the sixteenth embodiment, the intermediate seal G19 which is provided in a recess formed between the facing surfaces of the right and left
inner races - The elastic member G39 has an outer peripheral surface G39 d having the same diameter, and is brought into face-to-face pressure contact with the bottom wall surface of the recess between the
inner races inner races - In the sixteenth embodiment, the intermediate seal G19 and the
inner races - Description will be made below on a comparative test between a structure in which the seal is comprised of an intermediate seal member and inner race surfaces brought into face-to-face contact with each other, as shown in FIG. 21, and a structure in which the seal is comprised of a seal lip of the intermediate seal member and the inner race surfaces brought into linear contact with each other, as in the conventional example shown in FIG. 22.
- FIG. 27 is a schematic partial cross-sectional view of an apparatus used in this comparative test. The test apparatus has a sealed housing T2 which is fixed to a table T1. A rotary shaft T3 is supported through a bearing T4 in the central part of the sealed housing T2. Two race members T13, T13 which are corresponding to the inner races of the rolling bearing of the present invention are aligned in the axial direction on the outer periphery of the rotary shaft through a flange T5 which is integrally assembled with the rotary shaft. A recess T9 is formed in the inner diameter portions of the facing surfaces of the race members. A chamber on the inner diameter side formed between the race members T13, T13, and the rotary shaft T3, and the housing T2 is separated from an inner surface of the housing T2 and a room corresponding to the inside of the bearing formed outside the race members T13, T13, with a seal member T15 therebetween. The recess T9 is provided with a communication hole between the room corresponding to the inside of the bearing and the inner diameter side chamber. The chamber TA on the inner diameter side is opened to the air, while the room TS corresponding to the inside of the bearing communicates with a pressure adjusting member.
- The test is performed by fitting a face-to-face contact intermediate seal which is corresponding to the intermediate seal of the sixteenth embodiment of the present invention shown in FIG. 23 which is subjected to the test and a linear-contact seal corresponding to the seal of the conventional example shown in FIG. 22 into the recess T9 formed between the facing surfaces of the two race members T13, T13.
- FIG. 25 and FIG. 26 show test results of the ventilating function of the intermediate seal of the present invention shown in FIG. 23 and that of the intermediate seal of the prior art shown in FIG. 24. The experiment is to observe and compare internal pressure changes (the ventilating functions) by making a pressure in the room corresponding to the inside of the bearing to be negative in advance. The broken line in the drawing indicates the change according to the conventional art and the solid line indicates the change according to the present invention. In a stationary state shown in FIG. 25, a difference between the both cases is not generated. However, at the time of rotation, the pressure is restored to the atmospheric pressure for 1000 seconds or around in case of the face-to-face contact seal. On the other hand, the pressure is hardly restored to the atmospheric pressure when 3000 seconds have elapsed in case of the linear-contact seal. It can be understood that the ventilating function is conspicuously enhanced by the face-to-face contact seal.
- As described above, according to the present invention, there is provided on the side of the above-mentioned inner races the vent means which approximates the fluid pressure inside the bearing space to the outside fluid pressure by causing the air in the bearing space to communicate with the outside air when a difference between the fluid pressure in the bearing space and the outside fluid pressure becomes a predetermined value or more. Consequently, if, for example, the heated sealed rolling bearing is cooled, the fluid pressure in the bearing space is approximated to the outside fluid pressure, so that water or the like are not taken into the bearing space.
Claims (12)
1. A sealed rolling bearing in which a rolling member is disposed in a bearing space formed between an outer race and an inner race to rotate said outer race and said inner race relatively to each other, and side seal members are disposed at the both ends of said bearing space in the axial direction thereof while a bore seal member is disposed on the side of said inner race, thereby sealing said bearing space, characterized in that: there is provided vent means on the side of said inner race for approximating a fluid pressure in said bearing space to an outside fluid pressure when state of said fluid in said bearing space and state of said outside fluid become a predetermined relationship.
2. A sealed rolling bearing according to , wherein said inner race consists of two inner race elements adjacent in the axial direction, an intermediate seal is disposed between these two inner race elements, and said vent means is disposed on said seal.
claim 1
3. A sealed rolling bearing according to , wherein said seal is provided with a valve with slit.
claim 2
4. A sealed rolling bearing according to , wherein said seal consists of a seal main body and a seal lip integrally formed with said seal main body as a unitary structure, and a valve with a slit capable of causing the inside of the bearing to communicate with the outside thereof is formed on said seal main body or the seal lip.
claim 2
5. A sealed rolling bearing according to , wherein said vent means comprises a shape memory alloy or a bimetal, and said seal is deformed by an increase of temperature to cause the inside of the bearing to communicate with the outside.
claim 2
6. A sealed rolling bearing according to , wherein said vent means is formed of a material for transmitting gas and not transmitting liquid.
claim 2
7. A sealed rolling bearing according to , wherein said seal consists of a seal main body and a seal lip integrally with said seal main body as a unitary structure, said seal lip has a part with the diameter smaller than the inner diameter of said inner race element in the natural condition, and, when said bearing is assembled in a shaft, said part with the smaller diameter is brought into contact with said shaft to flux said seal lip, thereby changing the ventilating performance.
claim 2
8. A sealed rolling bearing according to , wherein said seal consists of a seal main body and a seal lip integrally with said seal main body as a unitary structure, said seal lip is brought into contact with said inner race elements toward the inside of the bearing, and the inside of the bearing is caused to communicate to the outside when a negative pressure of not less than a predetermined value is generated in said bearing or when a centrifugal force is caused by rotation of said inner race.
claim 2
9. A sealed rolling bearing according to , wherein said seal consists of a seal main body and a seal lip integrally with said seal main body as a unitary structure, and a slit for adjusting the vent is disposed on said seal lip in the axial direction thereof.
claim 2
10. A sealed rolling bearing according to , wherein said seal has elasticity and is brought into face-to-face contact with said two inner race elements so as to seal the inside and the outside of the bearing.
claim 2
11. A sealed rolling bearing according to , wherein said inner race consists of two inner race elements adjacent in the axial direction thereof, an intermediate seal is disposed between these two inner race elements, and a hole for ventilation is formed in the vicinity of said intermediate seal between said inner race elements.
claim 1
12. A sealed rolling bearing according to , wherein said inner race consists of two inner race elements adjacent in the axial direction thereof, an intermediate washer is disposed between these two inner race elements, and a hole for ventilation is formed on said intermediate washer for causing the inside of the bearing to communicate with the outside when the negative pressure is generated in the bearing.
claim 1
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US09/769,254 US6457870B2 (en) | 1998-07-29 | 2001-01-26 | Sealed rolling bearing |
Applications Claiming Priority (6)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP10-227525 | 1998-07-29 | ||
JP22752598 | 1998-07-29 | ||
JP11208150A JP2000104747A (en) | 1998-07-29 | 1999-07-22 | Capped rolling bearing |
JP11-208150 | 1999-07-22 | ||
US36219499A | 1999-07-28 | 1999-07-28 | |
US09/769,254 US6457870B2 (en) | 1998-07-29 | 2001-01-26 | Sealed rolling bearing |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US36219499A Continuation | 1998-07-29 | 1999-07-28 |
Publications (2)
Publication Number | Publication Date |
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US20010002939A1 true US20010002939A1 (en) | 2001-06-07 |
US6457870B2 US6457870B2 (en) | 2002-10-01 |
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Application Number | Title | Priority Date | Filing Date |
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US09/769,254 Expired - Lifetime US6457870B2 (en) | 1998-07-29 | 2001-01-26 | Sealed rolling bearing |
Country Status (3)
Country | Link |
---|---|
US (1) | US6457870B2 (en) |
JP (1) | JP2000104747A (en) |
DE (1) | DE19935014B4 (en) |
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US6746151B2 (en) | 2002-01-14 | 2004-06-08 | Seagate Technology Llc | Parallel capillary seal for a disk drive |
US20070154128A1 (en) * | 2004-02-09 | 2007-07-05 | Hidenobu Mikami | Grease, rolling bearing, constant velocity joint and rolling parts |
US8003582B2 (en) | 2004-02-09 | 2011-08-23 | Ntn Corporation | Grease, rolling bearing, constant velocity joint, and rolling parts |
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CN104632880A (en) * | 2013-11-07 | 2015-05-20 | Skf公司 | Bearing arrangement for fluid machinery application |
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CN105387070A (en) * | 2014-08-20 | 2016-03-09 | 斯凯孚公司 | Roller bearing and mounting method |
CN106499734A (en) * | 2015-09-03 | 2017-03-15 | 斯凯孚公司 | Sealing device for roller bearing unit |
CN108603532A (en) * | 2016-02-02 | 2018-09-28 | 株式会社捷太格特 | The containment member and rolling bearing system of rolling bearing |
US10550891B2 (en) | 2016-02-02 | 2020-02-04 | Jtekt Corporation | Seal member for rolling bearing and rolling bearing assembly |
CN110206816A (en) * | 2018-02-28 | 2019-09-06 | 斯凯孚公司 | Bearing |
US11053980B2 (en) * | 2019-01-08 | 2021-07-06 | Aktiebolaget Skf | Rolling-element bearing unit and assembly method |
Also Published As
Publication number | Publication date |
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US6457870B2 (en) | 2002-10-01 |
DE19935014B4 (en) | 2005-03-17 |
DE19935014A1 (en) | 2000-02-03 |
JP2000104747A (en) | 2000-04-11 |
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