WO2016194980A1 - 転がり軸受 - Google Patents
転がり軸受 Download PDFInfo
- Publication number
- WO2016194980A1 WO2016194980A1 PCT/JP2016/066287 JP2016066287W WO2016194980A1 WO 2016194980 A1 WO2016194980 A1 WO 2016194980A1 JP 2016066287 W JP2016066287 W JP 2016066287W WO 2016194980 A1 WO2016194980 A1 WO 2016194980A1
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- WO
- WIPO (PCT)
- Prior art keywords
- lip
- annular
- rolling bearing
- inner ring
- grease
- 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
- F16C33/72—Sealings
- F16C33/76—Sealings of ball or roller bearings
- F16C33/80—Labyrinth sealings
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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
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
- F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
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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
- F16C19/02—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
- F16C19/16—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 a single row of balls
- F16C19/163—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 a single row of balls with angular contact
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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
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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
- F16C33/583—Details of specific parts of races
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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
- F16C33/76—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
-
- 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
- F16C33/7816—Details of the sealing or parts thereof, e.g. geometry, material
- F16C33/782—Details of the sealing or parts thereof, e.g. geometry, material of the sealing region
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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
- F16C33/76—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
- F16C33/784—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race
- F16C33/7843—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a single annular sealing disc
- F16C33/7846—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a single annular sealing disc with a gap between the annular disc and the inner race
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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
- F16C2300/00—Application independent of particular apparatuses
- F16C2300/02—General use or purpose, i.e. no use, purpose, special adaptation or modification indicated or a wide variety of uses mentioned
-
- 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
- F16C33/66—Special parts or details in view of lubrication
- F16C33/6603—Special parts or details in view of lubrication with grease as lubricant
- F16C33/6607—Retaining the grease in or near the bearing
Definitions
- the present invention relates to a rolling bearing.
- Rolling bearings are known as bearings that support the rotating shafts of various mechanical devices, and rolling bearings require reliability such that seizure does not occur. Accordingly, rolling bearings employing grease lubrication having high lubrication performance are increasing even in the case of high-speed rotation applications. In this grease lubrication, the bearing is filled with grease in advance (see, for example, Patent Document 1).
- FIG. 4 is a cross-sectional view showing an example of a conventional rolling bearing.
- This rolling bearing is an angular ball bearing 90, and a ball 94 is in contact with the inner ring 91 and the outer ring 92 with a predetermined angle (contact angle).
- the shoulder diameter D2 on the other axial side (right side in FIG. 4) is larger than the shoulder diameter D1 on one axial side (left side in FIG. 4). (D1 ⁇ D2).
- the seals 97 and 98 are provided on both sides in the axial direction of the annular space 93. It has been.
- the seals 97 and 98 are labyrinth seals (non-contact seals) in order to realize high-speed rotation. That is, the labyrinth gaps 97a, 98a are formed between the seals 97, 98 and the inner ring 91, thereby preventing the grease from flowing out.
- the action of the grease flowing from one side to the other side in the axial direction as described above can occur even when the inner ring 91 has a different shoulder diameter than the rolling bearing.
- the shoulder diameter of the inner ring is the same on one side and the other side in the axial direction, the grease moves from one side in the axial direction to the other side due to the spinning of the rolling elements (balls) accompanying the rotation of the bearing.
- the rolling elements balls
- an object of the present invention is to provide a seal having a seal on the other side in the axial direction in a rolling bearing in which grease flows in an annular space formed between the inner ring and the outer ring. There is to increase.
- a rolling bearing comprising: Inner ring, Outer ring, A plurality of rolling elements provided between the inner ring and the outer ring; A cage for holding the rolling element; A first lip that is provided on one side in the axial direction of the rolling bearing in an annular space formed between the inner ring and the outer ring, and that forms a first labyrinth gap between the inner ring and prevents the grease from flowing out.
- a first seal having a portion;
- a second seal provided on the other axial side of the annular space and having a second lip portion that forms a second labyrinth gap with the inner ring to prevent grease from flowing out;
- the rolling bearing is configured such that the grease flows from the one axial side to the other axial side in the annular space,
- the second lip portion is larger than the first lip portion so that the path length of the second labyrinth gap is longer than the path length of the first labyrinth gap.
- the dimension in the axial direction of the second lip portion may be larger than the dimension in the axial direction of the first lip portion.
- the radius of the inner ring at the inlet portion of the second labyrinth gap arranged on the inner side of the rolling bearing is larger than the radius of the inner ring at the outlet portion of the second labyrinth gap arranged on the outer side of the rolling bearing. It can be big.
- the inner ring may have an annular side surface provided from the outer peripheral surface of the shoulder portion on the other side in the axial direction toward the radially inner side of the rolling bearing.
- the second lip portion may have a lip side surface facing the annular side surface with a gap.
- An inlet portion of the second labyrinth gap may be formed between the annular side surface and the lip side surface, and the inlet portion may open in the radial direction.
- the second lip portion may have a lip inclined surface that starts from an outer end portion in the radial direction of the lip side surface and extends outwardly toward the other side in the axial direction.
- the intersection of the outer peripheral surface of the shoulder and the annular side surface and the radial position of the start point may be the same.
- the radius of the inner ring at the inlet portion may be larger than the radius of the inner ring at the outlet portion.
- the outer end portion in the radial direction of the second seal is larger than the dimension in the radial direction of the first space formed between the outer end portion in the radial direction of the first seal and the first lip portion.
- the dimension in the radial direction of the second space formed between the second lip portion and the second lip portion may be large.
- the cage may have an annular portion on the other axial side of the rolling element.
- the inner peripheral surface of the annular portion may have a tapered surface that inclines outward in the radial direction toward the other side in the axial direction.
- the inner ring may have an annular side surface extending from the outer peripheral surface of the shoulder on the other axial side toward the radially inner side.
- the second lip portion has a lip side surface facing the annular side surface with a gap, and a lip extending outward in the radial direction from the radially outer end of the lip side surface toward the other side. And an inclined surface.
- the surface on the other axial side of the annular portion may be located on the one axial side with respect to the inlet portion of the second labyrinth gap.
- the path length of the second labyrinth gap on the other side in the axial direction is Since it is long, leakage of grease to the outside of the bearing can be effectively suppressed. That is, it becomes possible to improve the sealing performance by the seal on the other side in the axial direction. Since the axial dimension of the second lip part is larger than the axial dimension of the first lip part, the path length of the second labyrinth gap can be made longer than the path length of the first labyrinth gap.
- the inlet portion of the second labyrinth gap opens in the radial direction, so that the grease flowing along the outer peripheral surface of the shoulder portion on the other side in the axial direction becomes difficult to enter the second labyrinth gap. .
- the space between the annular side surface and the lip side surface is included in the second labyrinth gap, and the path length of the second labyrinth gap can be increased.
- the grease that has flowed along the outer peripheral surface of the shoulder portion on the other side in the axial direction becomes easy to flow along the lip inclined surface, and this grease is used for lubrication of the angular ball bearing.
- the centrifugal force increases as the turning radius increases.
- the radius of the inner ring at the inlet portion of the second labyrinth gap is made larger than the radius of the inner ring at the outlet portion, so that grease exists in the second labyrinth gap on the other side in the axial direction.
- the centrifugal force acting on the grease present on the inlet side is greater than that on the grease existing on the outlet side. For this reason, the effect
- the radial dimension of the second space is made larger than the radial dimension of the first space, so that the space on the other axial side of the annular space can be widened.
- the amount of grease stored can be increased. As a result, it is possible to extend the bearing life.
- the grease going to the other side can be guided radially outward. For this reason, it becomes possible to make it difficult for grease to enter the second labyrinth gap on the other side in the axial direction.
- the second lip portion since the second lip portion has the lip inclined surface, the grease that has flowed along the outer peripheral surface of the shoulder portion on the other side in the axial direction can easily flow along the lip inclined surface.
- the second lip portion has such a lip inclined surface, the gap between the second lip portion and the annular portion of the cage is narrowed, so that the grease is near the inlet portion of the second labyrinth gap.
- the inner peripheral surface of the annular portion has the tapered surface, so that the grease can be prevented from staying near the inlet portion of the second labyrinth gap. It becomes possible to make it difficult for the grease to enter the second labyrinth gap.
- the surface on the other side in the axial direction of the annular portion of the cage is positioned on the one side in the axial direction with respect to the inlet portion of the second labyrinth clearance, so that the second labyrinth clearance is increased as the bearing rotates.
- the annular portion does not exist on the radially outer side of the inlet portion, so that the grease on the inlet portion can easily flow outward in the radial direction. .
- the grease at the entrance of the second labyrinth gap is unlikely to flow out of the bearing through the second labyrinth gap.
- the rolling bearing of the present invention it is possible to improve the sealing performance by the seal on the other side in the axial direction, and the long-term reliability of the bearing can be improved.
- FIG. 1 is a cross-sectional view showing an embodiment of a rolling bearing according to the present invention.
- the rolling bearing is an angular ball bearing 1 and includes an outer ring 2, an inner ring 3, a plurality of balls (rolling elements) 4, an annular cage 5, a first seal 6, and a second seal 7. ing.
- the annular space S formed between the outer ring 2 and the inner ring 3 is filled with grease.
- the angular ball bearing 1 employs grease lubrication, and ensures lubrication performance.
- the angular ball bearing 1 is used under the condition of high speed rotation.
- one side in the axial direction and “the other side in the axial direction” are used with respect to the position of the angular ball bearing 1 in the axial direction.
- One side in the axial direction is the left side in FIG. 1, and the other side in the axial direction is the right side in FIG.
- An outer ring raceway groove 20 on which the balls 4 roll is formed on the inner peripheral surface of the outer ring 2.
- the ball 4 comes into contact with the outer ring raceway groove 20 at a predetermined contact angle.
- the outer ring 2 has a first outer shoulder portion 21 and a second outer shoulder portion 22 on both sides in the axial direction with the outer ring raceway groove 20 interposed therebetween.
- the inner diameter (shoulder diameter) of the first outer shoulder portion 21. ) Is larger than the inner diameter (shoulder diameter) of the second outer shoulder portion 22.
- a first groove 24 for fixing the seal 6 is formed at one end of the first outer shoulder 21 in the axial direction, and an end of the second outer shoulder 22 on the other side in the axial direction.
- a second groove 25 for fixing the seal 7 is formed.
- An inner ring raceway groove 30 on which the balls 4 roll is formed on the outer peripheral surface of the inner ring 3.
- the ball 4 contacts the inner ring raceway groove 30 at a predetermined contact angle.
- the inner ring 3 has a first inner shoulder 31 and a second inner shoulder 32 on both sides in the axial direction across the inner ring raceway groove 30.
- the outer diameter (shoulder) of the first inner shoulder 31 is shown.
- the outer diameter (shoulder diameter) of the second inner shoulder portion 32 is larger than the diameter).
- a first seal groove 34 is formed at an end portion on the one axial side of the first inner shoulder portion 31, and a second seal is formed at an end portion on the other axial side of the second inner shoulder portion 32.
- a groove 35 is formed.
- the outer peripheral surface of the inner ring 3 has a shape in which the outer diameter gradually increases from one side in the axial direction toward the other side (excluding the formation region of the seal grooves 34 and 35) as a whole.
- a shape having a different shoulder diameter on one side and the other side in the axial direction as in the present embodiment is hereinafter referred to as an angular shape.
- the plurality of balls 4 are provided in an annular space S between the outer ring 2 and the inner ring 3, and when the angular ball bearing 1 rotates (in this embodiment, the inner ring 3 rotates), these balls 4 are held in a cage. 5, the outer ring raceway groove 20 and the inner ring raceway groove 30 are rolled.
- the cage 5 can hold a plurality of balls 4 at predetermined intervals (equal intervals) along the circumferential direction.
- the cage 5 has pockets 10 for accommodating the balls 4.
- a plurality are formed along the circumferential direction.
- the cage 5 of the present embodiment includes a first annular portion 11 provided on one side of the ball 4 in the axial direction and a plurality of columns extending from the first annular portion 11 to the other side in the axial direction.
- Part 13 and a second annular part 12 provided on the other axial side of ball 4, and each pillar part 13 includes first annular part 11 and second annular part 12. It is connected.
- FIG. 1 The cage 5 of the present embodiment is made of resin, but may be made of metal.
- the cage 5 of the present embodiment includes an outer ring in which the first annular portion 11 is positioned in the radial direction by slidingly contacting an inner peripheral surface of a part of the outer ring 2 (first outer shoulder portion 21). This is a guide cage.
- the first seal 6 includes an annular cored bar 41 and a seal main body 42 fixed to the cored bar 41.
- the core metal 41 is made of metal
- the seal body 42 is made of rubber
- the seal body 42 is fixed to the core metal 41.
- the seal body 42 includes a radially outer end 43 attached to the first groove 24 and a lip portion (first lip portion) 44 that faces the seal groove 34 with a gap.
- the first seal 6 is attached to the outer ring 2 by the radial outer end 43 being fitted and fixed in the first groove 24. A slight gap is formed between the first lip portion 44 and the seal groove 34, and this gap becomes the first labyrinth gap 45. That is, the first lip portion 44 and the seal groove 34 constitute a labyrinth seal (non-contact seal).
- the second seal 7 includes an annular cored bar 51 and a seal body 52 fixed to the cored bar 51.
- the core metal 51 is made of metal
- the seal body 52 is made of rubber
- the seal body 52 is fixed to the core metal 51.
- the seal body 52 has a radially outer end 53 attached to the second groove 25 and a lip part (second lip part) 54 facing the seal groove 35 with a gap.
- the second seal 7 is attached to the outer ring 2 by the radial outer end 53 being fitted and fixed in the second groove 25.
- a slight gap is formed between the second lip portion 54 and the seal groove 35, and this gap becomes the second labyrinth gap 55. That is, the second lip portion 54 and the seal groove 35 constitute a labyrinth seal (non-contact seal).
- it becomes a structure suitable for high-speed rotation by setting it as a non-contact seal.
- the angular ball bearing 1 shown in FIG. 1 includes the first seal 6 having the first lip portion 44 and the second seal 7 having the second lip portion 54.
- the first seal 6 is provided on one side of the annular space S in the axial direction, and forms a first labyrinth gap 45 between the inner ring 3 and prevents the grease from flowing out.
- the second seal 7 is provided on the other axial side of the annular space S, and a second labyrinth gap 55 is formed between the second seal 7 and the inner ring 3 to prevent the grease from flowing out.
- the seals 6 and 7 prevent the grease existing in the annular space S from leaking to the outside.
- the space K2 functions as a space for storing grease.
- FIG. 2 is an enlarged view of the first seal 6 and the first seal groove 34.
- the first lip portion 44 of the first seal 6 has a main body portion 44a that is partly fixed to the core metal 41, and a protruding portion 44b that protrudes radially inward from the inner peripheral side of the main body portion 44a. is doing. Only the protruding portion 44b is accommodated in the first seal groove 34.
- the first lip portion 44 is a surface facing the inner ring 3, in order from the bearing inner side (ball 4 side), in the lip inner cylindrical surface 61, the lip annular surface 62, the lip intermediate cylindrical surface 63, the lip intermediate inclined surface 64, and the lip An outer cylindrical surface 65 is provided.
- the first seal groove 34 has an annular side surface 34a, a cylindrical surface 34b, and a raised convex surface 34c in order from the bearing inner side (the ball 4 side).
- the inner cylindrical surface 61 faces a part of the outer peripheral surface 31a of the first inner shoulder 31.
- the lip annular surface 62 faces the annular side surface 34a
- the lip middle cylindrical surface 63 faces the cylindrical surface 34b
- the lip middle slope 64 and the lip outer cylindrical surface 65 face the raised convex surface 34c.
- a first labyrinth gap 45 is formed between these opposing surfaces.
- the space between the inner lip inner cylindrical surface 61 and a part of the outer peripheral surface 31a of the first inner shoulder 31 is the inlet 45a side of the first labyrinth gap 45, and the space between the outer cylindrical surface 65 and the raised convex surface 34c.
- the first labyrinth gap 45 is on the outlet 45b side.
- FIG. 3 is an enlarged view of the second seal 7 and the second seal groove 35.
- the second lip portion 54 of the second seal 7 has a main body portion 54a partially fixed to the core metal 51, and a protruding portion 54b protruding radially inward from the inner peripheral side of the main body portion 54a. is doing. And both the main-body part 54a and the protrusion part 54b are the states accommodated in the 2nd seal groove 35.
- the second lip portion 54 is a surface facing the inner ring 3, in order from the bearing inner side (ball 4 side), lip side surface 71, lip inner cylindrical surface 72, lip annular surface 73, lip middle cylindrical surface 74, lip middle slope. 75 and an outer lip cylindrical surface 76.
- the second seal groove 35 has an inner annular side surface 35a, an inner cylindrical surface 35b, an intermediate annular side surface 35c, an intermediate cylindrical surface 35d, and a raised convex surface 35e in this order from the bearing inner side (ball 4 side). ing.
- the lip side surface 71 faces the inner annular side surface 35a
- the lip inner cylindrical surface 72 faces the inner cylindrical surface 35b
- the lip annular surface 73 faces the middle annular side surface 35c
- the lip middle cylindrical surface 74 is the middle cylindrical surface.
- the lip middle slope 75 and the outer lip cylindrical surface 76 are opposed to the raised convex surface 35e.
- a second labyrinth gap 55 is formed between these opposing surfaces. Further, the gap between the lip side surface 71 and the inner annular side surface 35a is the inlet portion 55a side of the second labyrinth gap 55, and the gap between the lip outer cylindrical surface 76 and the raised convex surface 35e is the outlet portion 55b of the second labyrinth gap 55. On the side.
- the surface including the term “cylindrical surface” is a center line that coincides with the center line of the angular ball bearing 1.
- the surface including the term “annular surface” and the lip side surface 71 are surfaces on an imaginary surface orthogonal to the center line of the angular ball bearing 1.
- the surface including the term “annular side surface” is a surface on a virtual surface orthogonal to the center line of the angular ball bearing 1.
- the surface including the term “cylindrical surface” is a cylindrical surface having a center line coinciding with the center line of the angular ball bearing 1.
- the axial dimension L1 of the first lip portion 44 is the sum of the axial lengths of the lip inner cylindrical surface 61, the lip middle cylindrical surface 63, the lip middle inclined surface 64, and the lip outer cylindrical surface 65.
- the axial dimension L ⁇ b> 2 of the second lip portion 54 is the sum of the axial lengths of the lip inner cylindrical surface 72, the lip inner cylindrical surface 74, the lip inner inclined surface 75, and the lip outer cylindrical surface 76.
- the axial lengths of the lip middle cylindrical surface 74, the lip middle slope 75, and the lip outer cylindrical surface 76 of the second lip portion 54 are respectively the lip middle cylinder of the first lip portion 44 (see FIG. 2).
- the axial length of the in-lip cylindrical surface 72 of the second lip portion 54 is longer than the axial length of the in-lip cylindrical surface 61 of the first lip portion 44 (see FIG. 2).
- the axial dimension L2 of the second lip 54 is larger than the axial dimension L1 of the first lip 44 (L1 ⁇ L2).
- the path length of the second labyrinth gap 55 is longer than the path length of the first labyrinth gap 45.
- the second labyrinth gap 55 also includes a small space between the inner annular side surface 35a and the lip side surface 71 facing in the axial direction on the inlet portion 55a side of the second labyrinth gap 55. included.
- the first labyrinth gap 45 has a radially opposing surface on the inlet 45a side of the first labyrinth gap 45 (the cylindrical surface 61 in the lip and the outer circumferential surface 31a). However, there is no surface facing in the axial direction. That is, in the present embodiment (see FIG.
- the inner ring 3 has an inner annular side surface 35a that is provided radially inward from the outer peripheral surface 32a of the second inner shoulder 32, and
- the two lip portions 54 have a lip side surface 71 facing the inner annular side surface 35a with a gap. Since the gap (small space) between the inner annular side surface 35a and the lip side surface 71 is also included in the second labyrinth gap 55, the path length of the second labyrinth gap 55 is the first labyrinth gap. The path length is longer than 45.
- the second lip portion 54 is larger than the first lip portion 44 in this embodiment. More specifically, the axial dimension L2 of the second lip portion 54 is larger than the axial dimension L1 of the first lip portion 44. Thereby, the path length of the second labyrinth gap 55 is longer than the path length of the first labyrinth gap 45. As described above, since the second lip portion 54 of the second seal 7 is enlarged, the path length of the second labyrinth gap 55 formed between the inner ring 3 (second seal groove 35) is lengthened. Therefore, even if the grease flows in the annular space S from the one side in the axial direction to the other side, the leakage of the grease to the outside of the bearing can be effectively suppressed by the second seal 7. That is, the sealing performance by the second seal 7 can be improved, and the long-term reliability of the bearing can be improved.
- the inlet portion 55a of the second labyrinth gap 55 is formed between the inner annular side surface 35a and the lip side surface 71 facing each other in the axial direction. And this entrance part 55a is opened toward the radial direction outer side.
- the inlet portion 98b of the labyrinth gap 98a on the other side in the axial direction is open toward the axial direction, and in this case, the grease flows from one side in the axial direction to the other side.
- the grease flowing along the outer peripheral surface 91b of the shoulder portion 91a tends to enter the labyrinth gap 98a as compared with the present embodiment.
- the inlet portion 55a opens toward the radially outer side, and therefore the first of the greases flowing from one side to the other side in the annular space S in the annular space S. 2
- the grease flowing along the outer peripheral surface 32 a of the inner shoulder portion 32 is difficult to enter the second labyrinth gap 55.
- the surface 12a on the other axial side of the annular portion 12 of the cage 5 is on the one axial side (the left side in FIG. 3) from the inlet portion 55a of the second labyrinth gap 55. positioned.
- the annular portion 12 does not exist on the radially outer side of the inlet portion 55a. That is, the inlet portion 55 a is not blocked by the annular portion 12. Therefore, when the grease existing in the inlet portion 55a flows radially outward due to centrifugal force as the bearing rotates, the grease is likely to flow radially outward. As a result, the grease at the inlet 55a is unlikely to flow out of the bearing through the second labyrinth gap 55.
- the second lip portion 54 has a lip inclined surface 77 that starts from the radially outer end 71a of the lip side surface 71 and extends radially outward toward the other side in the axial direction. And the intersection 37 of the outer peripheral surface 32a of the 2nd inner shoulder part 32 and the inner annular side surface 35a, and the radial direction position of the said starting point (end part 71a) are the same. With this configuration, the grease that has flowed along the outer peripheral surface 32 a of the second inner shoulder portion 32 and passed through the inlet portion 55 a can easily flow along the lip inclined surface 77. The grease flowing along the lip inclined surface 77 is held in the space K2 for storing the grease, and is used for lubricating the angular ball bearing 1.
- the cage 5 has an annular portion 12 on the other side in the axial direction of the ball 4.
- the inner peripheral surface 15 of the annular portion 12 has a tapered surface 16.
- the tapered surface 16 is inclined outward in the radial direction toward the other side in the axial direction. According to the tapered surface 16, the space between the annular portion 12 and the second inner shoulder portion 32 can be enlarged toward the other side in the axial direction. Further, the taper surface 16 can guide the grease directed toward the other side in the axial direction outward in the radial direction.
- the second lip portion 54 includes the lip side surface 71 facing the inner annular side surface 35a of the second seal groove 35 with a gap, and the radially outer end of the lip side surface 71. And a lip inclined surface 77 starting from the portion 71a.
- the gap between the retainer 5 and the annular portion 12 becomes narrow, and the grease is near the inlet portion 55a of the second labyrinth gap 55.
- the inner peripheral surface 15 of the annular portion 12 has the tapered surface 16, it is possible to prevent the grease from staying near the inlet portion 55a.
- a part of the inner peripheral surface 15 of the annular portion 12 is the tapered surface 16, but the entire inner peripheral surface 15 may be the tapered surface 16.
- the radial dimension RK2 of the second space K2 on the second seal 7 side is larger than the radial dimension RK1 of the first space K1 on the first seal 6 side.
- the first space K1 is a space formed between the radially outer end portion 43 and the first lip portion 44 of the first seal 6, and the second space K2 is the diameter of the second seal 7. It is a space formed between the direction outer side end portion 53 and the second lip portion 54.
- the radial dimension of the core bar 51 of the second seal 7 is longer than the core bar 41 of the first seal 6.
- the second space K2 on the other axial side of the annular space S can be widened, and the amount of grease stored can be increased.
- the grease flowing along the lip inclined surface 77 of the second lip portion 54 is stored in the second space K2, and thereafter, the grease in the space K2 flows toward the ball 4 and the angular ball bearing 1 Used for lubrication. Therefore, the bearing life can be extended by widening the second space K2 and increasing the amount of grease stored.
- the radius r1 at the inlet portion 55a on the bearing inner side of the second labyrinth gap 55 is larger than the radius r2 at the outlet portion 55b on the bearing outer side of the second labyrinth gap 55 (r1> r2). . That is, the radius at the intersection 37 between the outer peripheral surface 32a of the second inner shoulder portion 32 and the inner annular side surface 35a is larger than the radius of the raised convex surface 35e of the second seal groove 35. This is because the centrifugal force increases as the turning radius increases, and this action is used to cause the grease in the second labyrinth gap 55 to return to the second space K2.
- the annular portion 11 on the one side in the axial direction and the annular portion 12 on the other side are symmetrical in the longitudinal section shown in FIG.
- the annular portion 11 is formed with a tapered surface 17 that is symmetrical to the tapered surface 16 formed on the annular portion 12.
- the in-lip cylindrical surface 72 of the second lip portion 54 has a concave round surface 72 a between the lip annular surface 73. For this reason, in the case where grease exists between the lip annular surface 73 and the middle annular side surface 35c, the grease moves radially outward due to the centrifugal force accompanying the bearing rotation. It becomes easy to flow toward the inlet 55a side along 72a. That is, it is easy to return the grease to the inside of the bearing.
- This configuration includes an inner ring 3, an outer ring 2, a plurality of rolling elements (balls 4) provided between the inner ring 3 and the outer ring 2, and a cage 5 that holds these rolling elements (balls 4).
- a rolling bearing in which an action of flowing grease from one side in the axial direction to the other side in the annular space S formed between the inner ring 3 and the outer ring 2 is generated;
- a first seal 6 having a first lip portion 44 which is provided on one side in the axial direction of the annular space S and forms a first labyrinth gap 45 between the inner ring 3 and prevents the outflow of grease, and the axial direction of the annular space S
- a second seal 7 having a second lip portion 54 that is provided on the other side and forms a second labyrinth gap 55 between the inner ring 3 and prevents the grease from flowing out;
- the cage 5 has an annular portion 12 on the other axial side of the rolling element (ball 4),
- the inner peripheral surface 15 of the annular portion 12 has a tapered surface 16 that inclines radially outward toward the other side in the axial direction.
- the inner ring 3 has an inner annular side surface 35a provided radially inward from the outer peripheral surface 32a of the shoulder portion on the other side in the axial direction (second inner shoulder portion 32).
- the lip portion 54 has a lip side surface 71 opposed to the inner annular side surface 35a with a gap, and a radially outer end 71a of the lip side surface 71 as a starting point toward the other side in the axial direction. It can be set as the structure which has the lip inclination surface 77 extended.
- the surface 12 a on the other axial side of the annular portion 12 can be configured to be positioned on one axial side with respect to the inlet portion 55 a of the second labyrinth gap 55. The embodiments described with reference to FIGS. 1 to 3 can be applied to this configuration.
- the rolling bearing of the present invention is not limited to the illustrated form, but may be of another form within the scope of the present invention.
- the rolling element is the ball 4, it may be a roller.
- the outer ring 2 demonstrated the case where the internal diameter (shoulder diameter) of the 2nd outer shoulder part 22 was larger than the internal diameter (shoulder diameter) of the 1st outer shoulder part 21, These inner diameters (shoulder diameters) may be the same.
- the cage 5 is guided to rotate by the outer ring 2 at the annular portions 11 and 12 on both sides thereof.
- the rolling bearing of the present invention may be used for high-speed rotation or may be used for general purposes.
- the rolling bearing of the present invention it is possible to improve the sealing performance by the seal on the other side in the axial direction, and the long-term reliability of the bearing can be improved.
- Second seal 12 Second annular part (annular part) 12a: Surface on the other side in the axial direction 15: Inner peripheral surface 16: Tapered surface 32: Second inner shoulder (shoulder on the other side in the axial direction) 32a: outer peripheral surface 35a: inner annular side surface (annular side surface) 37: intersection 43: radial outer end 44: first lip 45: first labyrinth gap 53: radial outer end 54: second lip 55: second labyrinth gap 55a: inlet 71: lip side 71a : End portion 77: lip inclined surface K1: first space K2: second space RK1: radial dimension of the first space RK2: radial dimension of the second space L1: axial dimension of the first lip part L2: Axial dimension r1 of the second lip part r1: Radius of the inlet part
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Abstract
Description
すると、環状空間93のグリースが軸方向他方側の空間95に集まってグリースの偏りが発生し、やがてそのグリースがラビリンス隙間98aに侵入して軸受外部に漏れる場合がある。グリースの漏れが生じると、アンギュラ玉軸受90において潤滑不良が発生し、焼き付き、昇温、摩耗といった不具合が発生する可能性がある。
内輪と、
外輪と、
前記内輪と前記外輪との間に設けられている複数の転動体と、
前記転動体を保持する保持器と、
前記内輪と前記外輪との間に形成されている環状空間の前記転がり軸受の軸方向一方側に設けられ、前記内輪との間に第1ラビリンス隙間を形成してグリースの流出を防ぐ第1リップ部を有する、第1シールと、
前記環状空間の前記軸方向他方側に設けられ、前記内輪との間に第2ラビリンス隙間を形成してグリースの流出を防ぐ第2リップ部を有する、第2シールと、
を備え、
前記転がり軸受は、前記環状空間において前記グリースが前記軸方向一方側から前記軸方向他方側へ流れるよう構成され、
前記第1ラビリンス隙間の経路長よりも前記第2ラビリンス隙間の経路長が長いように、前記第2リップ部が前記第1リップ部よりも大きい、ものが供される。
前記第1リップ部の軸方向寸法よりも前記第2リップ部の軸方向寸法が大きいことにより、第1ラビリンス隙間の経路長よりも第2ラビリンス隙間の経路長を長くすることができる。
また本発明によれば、第2ラビリンス隙間の入口部が径方向に向かって開口することで、軸方向他方側の肩部の外周面に沿って流れるグリースは、第2ラビリンス隙間に入り難くなる。また、環状側面とリップ側面との間の空間が第2ラビリンス隙間に含まれ、第2ラビリンス隙間の経路長を長くすることができる。
本発明によれば、軸方向他方側の肩部の外周面に沿って流れたグリースは、リップ傾斜面に沿って流れやすくなり、このグリースがアンギュラ玉軸受の潤滑に用いられる。
回転半径が大きい方が遠心力は大きくなる。そこで、前記本発明によれば、第2ラビリンス隙間の入口部における内輪の半径が出口部における内輪の半径よりも大きくされることで、軸方向他方側における第2ラビリンス隙間にグリースが存在している状態において、入口部側に存在するグリースの方が出口部側に存在するグリースよりも作用する遠心力が大きくなる。このため、第2ラビリンス隙間に存在しているグリースを軸受内部側に戻す作用が生まれる。
本発明によれば、前記第1の空間の径方向寸法よりも前記第2の空間の径方向寸法が大きくされることで、環状空間のうち軸方向他方側の空間を広くすることができ、グリースの貯留量を高めることができる。これにより、軸受寿命を延ばすことが可能となる。
本発明によれば、前記テーパー面により保持器の前記環状部と内輪の肩部との間の空間を、軸方向他方側に向かって拡大させることが可能となり、また、前記テーパー面により軸方向他方側に向かうグリースを径方向外側に誘導することができる。このため、グリースが軸方向他方側の第2ラビリンス隙間に入り難くすることが可能となる。
本発明によれば、第2リップ部がリップ傾斜面を有することで、軸方向他方側の肩部の外周面に沿って流れたグリースが、リップ傾斜面に沿って流れやすくなり、このグリースがアンギュラ玉軸受の潤滑に用いられる。なお、第2リップ部がこのようにリップ傾斜面を有していると、第2リップ部と保持器の前記環状部との間の隙間が狭くなってグリースが第2ラビリンス隙間の入口部付近で滞留しやすくなるが、前記のとおり、当該環状部の内周面は前記テーパー面を有していることで、グリースが第2ラビリンス隙間の入口部付近で滞留するのを抑制することができ、グリースが第2ラビリンス隙間に入り難くすることが可能となる。
本発明によれば、保持器の環状部の軸方向他方側の面が第2ラビリンス隙間の入口部よりも軸方向一方側に位置することで、軸受の回転に伴って、第2ラビリンス隙間の入口部に存在しているグリースが遠心力により径方向外側へ流れる場合に、その入口部の径方向外側に環状部が存在しないことから、前記入口部のグリースを径方向外側に流動させやすくなる。この結果、第2ラビリンス隙間の入口部のグリースが、この第2ラビリンス隙間を通過して軸受外部へ流出し難くなる。
本発明の転がり軸受によれば、軸方向他方側のシールによる密封性を高めることが可能となり、軸受の長期信頼性を向上させることができる。
〔アンギュラ玉軸受の全体構成について〕
図1は、本発明の転がり軸受の実施の一形態を示す断面図である。この転がり軸受は、アンギュラ玉軸受1であり、外輪2と、内輪3と、複数の玉(転動体)4と、環状の保持器5と、第1シール6と、第2シール7とを備えている。そして、外輪2と内輪3との間に形成される環状空間Sにグリースが充填されている。つまり、このアンギュラ玉軸受1では、グリース潤滑が採用されており、潤滑性能を確保している。また、本実施形態では、このアンギュラ玉軸受1は高速回転の条件で用いられる。
なお、以下の説明において、アンギュラ玉軸受1の軸方向の位置に関して「軸方向一方側」及び「軸方向他方側」という用語を用いる。軸方向一方側は図1では左側であり、軸方向他方側は図1では右側である。
すると、環状空間Sのグリースが軸方向他方側の空間K2に集まってグリースの偏りが発生する。そこで、このようなグリースが軸受外部に漏れるのを前記第2シール7によって防いでいる。なお、前記空間K2は、グリースを溜めるための空間として機能する。
図2は、第1シール6及び第1シール溝34の拡大図である。第1シール6の第1リップ部44は、芯金41に一部が固定されている本体部44aと、この本体部44aの内周側から径方向内側に突出している突出部44bとを有している。そして、突出部44bのみが第1シール溝34に収容された状態となっている。
そして、本実施形態の第1シール溝34及び第2シール溝35が有する面に関して、「環状側面」という用語を含む面は、アンギュラ玉軸受1の中心線に直交する仮想面上の面であり、また、「円筒面」という用語を含む面は、アンギュラ玉軸受1の中心線と一致する中心線を有する円筒形状の面である。
図3において、第2リップ部54の軸方向寸法L2は、リップ内円筒面72、リップ中円筒面74、リップ中斜面75、及びリップ外円筒面76それぞれの軸方向長さの和となる。
第2リップ部54(図3参照)のリップ中円筒面74、リップ中斜面75、及びリップ外円筒面76の軸方向長さは、それぞれ第1リップ部44(図2参照)のリップ中円筒面63、リップ中斜面64、及びリップ外円筒面65の軸方向長さと同じである。第2リップ部54(図3参照)のリップ内円筒面72の軸方向長さは、第1リップ部44(図2参照)のリップ内円筒面61の軸方向長さよりも長くなっている。このため、第1リップ部44の軸方向寸法L1よりも第2リップ部54の軸方向寸法L2が大きくなる(L1<L2)。これにより、第1ラビリンス隙間45の経路長よりも第2ラビリンス隙間55の経路長が長い。
つまり、本実施形態では(図3参照)、内輪3は、第2内肩部32の外周面32aから径方向内側に向かって設けられている内環状側面35aを有しており、また、第2リップ部54は、この内環状側面35aと隙間を有して対向するリップ側面71を有している。そして、これら内環状側面35aとリップ側面71との間の隙間(小空間)も、第2ラビリンス隙間55に含まれていることから、この第2ラビリンス隙間55の経路長は、第1ラビリンス隙間45の経路長よりも長くなっている。
これに対して、図3に示す本実施形態の場合、入口部55aは径方向外側に向かって開口していることから、環状空間Sにおいて軸方向一方側から他方側へ流れるグリースのうち、第2内肩部32の外周面32aに沿って流れるグリースは、第2ラビリンス隙間55に入り難くなる。
図3に示すように、保持器5は、玉4の軸方向他方側に環状部12を有している。そして、この環状部12の内周面15は、テーパー面16を有している。このテーパー面16は、軸方向他方側に向かうにしたがって径方向外側に傾斜している。このテーパー面16によれば、環状部12と第2内肩部32との間の空間を、軸方向他方側に向かって拡大させることが可能となる。また、このテーパー面16により軸方向他方側に向かうグリースを径方向外側に誘導することができる。
なお、図3に示す実施形態では、環状部12の内周面15の一部がテーパー面16であるが、内周面15の全体がテーパー面16であってもよい。
この構成は、内輪3、外輪2、これら内輪3と外輪2との間に設けられている複数の転動体(玉4)、及びこれら転動体(玉4)を保持する保持器5を備え、内輪3と外輪2との間に形成されている環状空間Sにおいて軸方向一方側から他方側へグリースが流れる作用が生じる転がり軸受であって、
環状空間Sの軸方向一方側に設けられ内輪3との間に第1ラビリンス隙間45を形成してグリースの流出を防ぐ第1リップ部44を有する第1シール6と、環状空間Sの軸方向他方側に設けられ内輪3との間に第2ラビリンス隙間55を形成してグリースの流出を防ぐ第2リップ部54を有する第2シール7と、を更に備え、
保持器5は、転動体(玉4)の軸方向他方側に環状部12を有し、
この環状部12の内周面15は、軸方向他方側に向かうにしたがって径方向外側に傾斜するテーパー面16を有している。
また、この構成において、環状部12の軸方向他方側の面12aは、第2ラビリンス隙間55の入口部55aよりも軸方向一方側に位置している構成とすることができる。
なお、図1~図3により説明した実施例について、この構成に適用することができる。
また、図1に示す形態では、外輪2において、第1外肩部21の内径(肩径)よりも第2外肩部22の内径(肩径)が大きくなっている場合について説明したが、これらの内径(肩径)は同じであってもよい。この場合、保持器5はその両側の環状部11,12において外輪2により回転が案内される。また、外輪2の肩径を同じとする場合、軸方向他方側においてグリースの貯留量を多くするために、第2外肩部22にグリースを溜めるための凹部を形成するのが好ましい。
なお、本発明の転がり軸受は、高速回転用途であってもよく、一般用途であってもよい。
2:外輪
3:内輪
4:玉(転動体)
5:保持器
6:第1シール
7:第2シール
12:第2円環部(環状部)
12a:軸方向他方側の面
15:内周面
16:テーパー面
32:第2内肩部(軸方向他方側の肩部)
32a:外周面
35a:内環状側面(環状側面)
37:交点
43:径方向外側端部
44:第1リップ部
45:第1ラビリンス隙間
53:径方向外側端部
54:第2リップ部
55:第2ラビリンス隙間
55a:入口部
71:リップ側面
71a:端部
77:リップ傾斜面
K1:第1の空間
K2:第2の空間
RK1:第1の空間の径方向寸法
RK2:第2の空間の径方向寸法
L1:第1リップ部の軸方向寸法
L2:第2リップ部の軸方向寸法
r1:入口部の半径
r2:出口部の半径
S:環状空間
Claims (10)
- 転がり軸受であって、
内輪と、
外輪と、
前記内輪と前記外輪との間に設けられている複数の転動体と、
前記転動体を保持する保持器と、
前記内輪と前記外輪との間に形成されている環状空間の前記転がり軸受の軸方向一方側に設けられ、前記内輪との間に第1ラビリンス隙間を形成してグリースの流出を防ぐ第1リップ部を有する、第1シールと、
前記環状空間の前記軸方向他方側に設けられ、前記内輪との間に第2ラビリンス隙間を形成してグリースの流出を防ぐ第2リップ部を有する、第2シールと、
を備え、
前記転がり軸受は、前記環状空間において前記グリースが前記軸方向一方側から前記軸方向他方側へ流れるよう構成され、
前記第1ラビリンス隙間の経路長よりも前記第2ラビリンス隙間の経路長が長いように、前記第2リップ部が前記第1リップ部よりも大きい。 - 請求項1に記載の転がり軸受であって、
前記第1リップ部の前記軸方向における寸法よりも前記第2リップ部の前記軸方向における寸法が大きい。 - 請求項1または2に記載の転がり軸受であって、
前記転がり軸受の内部側に配置された前記第2ラビリンス隙間の入口部における前記内輪の半径は、前記転がり軸受の外部側に配置された当該第2ラビリンス隙間の出口部における前記内輪の半径よりも大きい。 - 請求項1又は2に記載の転がり軸受であって、
前記内輪は、前記軸方向他方側の肩部の外周面から、前記転がり軸受の径方向内側に向かって設けられている環状側面を有し、
前記第2リップ部は、前記環状側面と隙間を有して対向するリップ側面を有し、
前記環状側面と前記リップ側面との間に前記第2ラビリンス隙間の入口部が形成され、
当該入口部は径方向に向かって開口している。 - 請求項4に記載の転がり軸受であって、
前記第2リップ部は、前記リップ側面の前記径方向における外側の端部を始点として、前記軸方向他方側に向かうにしたがって前記外側に延びるリップ傾斜面を有し、
前記肩部の前記外周面と前記環状側面との交点と、前記始点との径方向位置は同じである。 - 請求項4または5に記載の転がり軸受であって、
前記入口部における前記内輪の半径は、前記第2ラビリンス隙間の出口部における前記内輪の半径よりも大きい。 - 請求項1~6のいずれか一項に記載の転がり軸受であって、
前記第1シールの前記径方向における外側端部と前記第1リップ部との間に形成される第1の空間の前記径方向における寸法よりも、前記第2シールの前記径方向における外側端部と前記第2リップ部との間に形成される第2の空間の前記径方向における寸法が大きい。 - 請求項1~7のいずれか一項に記載の転がり軸受であって、
前記保持器は、前記転動体の前記軸方向他方側に環状部を有し、
当該環状部の内周面は、前記軸方向他方側に向かうにしたがって前記径方向外側に傾斜するテーパー面を有している。 - 請求項8に記載の転がり軸受であって、
前記内輪は、前記軸方向他方側の肩部の外周面から前記径方向内側に向かって延伸する環状側面を有し、
前記第2リップ部は、前記環状側面と隙間を有して対向するリップ側面と、当該リップ側面の前記径方向外側の端部を始点として前記他方側に向かうにしたがって前記径方向外側に延びるリップ傾斜面と、を有している。 - 請求項8又は9に記載の転がり軸受であって、
前記環状部の前記軸方向他方側の面は、前記第2ラビリンス隙間の入口部よりも前記軸方向一方側に位置している。
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BR112017026108-1A BR112017026108B1 (pt) | 2015-06-03 | 2016-06-01 | Mancal de rolamento |
US15/578,482 US10221893B2 (en) | 2015-06-03 | 2016-06-01 | Rolling bearing |
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BR112017026108B1 (pt) | 2022-01-25 |
CN107614909B (zh) | 2020-07-07 |
DE112016002479T5 (de) | 2018-02-15 |
US10221893B2 (en) | 2019-03-05 |
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