JP2010101369A - Rolling bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve the easiness of handling of a rolling bearing having a segment retainer during the assembling by preventing an unrestricting race which does not constrain the derailment of rolling elements from a raceway surface, such as an outer ring, from being disengaged after the bearing is assembled. <P>SOLUTION: This rolling bearing includes an inner ring 2, the outer ring 3, the plurality of rolling elements 4, and the retainer 5. The race of at least one of the inner ring 2 and the outer ring 3 is the unrestricting race which does not constrain the derailment of the rolling elements 4 from the raceway surface. For example, the outer ring 3 is the unrestricting race. The retainer 5 is the segment retainer which is divided into at least two segments in the circumferential direction. A projection 7 which is radially projecting toward the raceway 2 opposed thereto and axially opposed to the rolling elements 4 or the retainer 5 is formed on the peripheral surface of the unrestricting raceway 3 or on the extension surface thereof on the side where the derailment of the rolling elements 4 from the raceway surface 3 is not restricted. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a rolling bearing provided with a segment cage, and more particularly to a large-sized rolling bearing used for a main shaft bearing of a wind power generator.

Large-sized rolling bearings used for main shaft bearings of wind power generators, etc., make it difficult to manufacture a ring-integrated cage. Therefore, segment cages that are divided into multiple segments in the circumferential direction are often used. (For example, Patent Document 1). Patent Document 1 shows an example in which the rolling bearing is a tapered roller bearing.
Japanese Patent No. 4105750

  In a state where there is no outer ring, the rolling bearing provided with the segment cage has a small restraint force of the rolling element by the cage, so that the rolling element comes off from the raceway surface of the inner ring and the rolling element and the cage are likely to fall off. When the bearing is assembled to the machine, the bearing may be tilted or suspended, and at that time, the outer ring may be disengaged in the axial direction. Therefore, when assembling a rolling bearing equipped with a segment cage, careful handling was required to avoid the outer ring coming off and the rolling elements and cage falling off.

  It is an object of the present invention to provide a rolling bearing having a segment cage in which an unconstrained bearing ring that does not restrain the rolling element from deviating from the raceway surface, such as an outer ring, is prevented from coming off after the assembly of the bearing. Is to improve the performance.

  The rolling bearing according to the present invention is disposed between an inner ring having a raceway surface on an outer periphery, an outer ring having a raceway surface on an inner periphery, and a raceway between the raceway surface of the inner ring and the raceway surface of the outer ring. A plurality of rolling elements, and a holder that holds the rolling elements in a circumferentially spaced manner so that the rolling elements can freely roll. At least one of the inner ring and the outer ring has at least one side of the raceway surface. In a rolling bearing that is a non-restraining race ring that does not restrain the rolling element from deviating from the raceway surface, and the cage is a segment cage that is divided into at least two segments in the circumferential direction. On the peripheral surface of the unconstrained raceway or its extension surface, the side that does not restrain the deviation of the rolling element from the raceway surface protrudes in a radial direction toward the opposite raceway and extends axially with the rolling element or cage. Opposite convex parts And wherein the digit.

  According to the configuration of the present invention, the rolling element or the cage is axially opposed to the side that does not restrain the deviation of the rolling element from the raceway surface on the peripheral surface having the raceway surface of the unconstrained raceway or its extended surface. Since the convex part is provided, even if the unconstrained raceway moves to the side that does not restrain the deviation from the raceway surface of the rolling element, the convex part hits the rolling element or the cage, and the unconstrained raceway no longer moves. Movement is restricted. For this reason, once the rolling bearing is assembled, the unrestrained bearing ring does not come off, and handling when the rolling bearing is assembled to the machine is easy.

  In the rolling bearing according to the present invention, only one of the inner ring and the outer ring may be the non-restraining raceway ring. The unconstrained raceway ring may have a flange portion that restrains the rolling element from deviating from the raceway surface on one side of the raceway surface.

In the present invention, the convex part is a part of a convex part that is separate from the non-constrained raceway, and the convex part is placed in a recess formed on the peripheral surface of the non-constraint raceway other than the convex part. These portions may be fitted and provided.
If the convex portion is a part of a convex component separate from the unconstrained raceway, the convex portion can be easily processed. In that case, if the convex part is provided by fitting a part other than the convex part into the concave part formed on the peripheral surface of the unconstrained raceway ring, compared to the case where the convex part is provided on the end face of the unconstrained raceway ring, The width dimension (axial dimension) of the restraining race can be shortened. In particular, if there is a dimensional allowance on the side of the peripheral surface of the unconstrained race that does not restrain the deviation of the rolling element from the raceway, the width of the unconstrained race is not changed, Convex parts can be provided on the peripheral surface.

When the convex component is provided on the peripheral surface of the unconstrained raceway ring, it is preferable that the portion where the recess is formed on the peripheral surface of the unconstraint raceway is cylindrical.
If the part where the concave part is formed is cylindrical, the distance between the base position of the convex part of the convex part and the rolling element or the cage is compared to the case where the part is inclined farther away from the axial direction. It becomes possible to approach, and the moment which acts on a convex part when a rolling element or a holder contacts a convex part can be made small. Therefore, it is difficult for the convex component to come off from the concave portion.

  In the present invention, the rolling element may be a tapered roller, and the inner ring may be a raceway with a double collar having flange portions protruding radially toward the outer ring on both sides of the raceway surface. That is, the type of the rolling bearing can be a tapered roller bearing in which the inner ring is provided with both collars.

When the rolling bearing is the tapered roller bearing, the concave portion is an annular groove, and the convex component is a C-shape that is divided at one place in the circumferential direction when viewed from the axial direction, and the convex component is By using the elasticity of this convex part, by inserting into the concave part in a reduced diameter state and then expanding the diameter, a part other than the convex part is fitted into the concave part, and the gap size of the divided part is The outer diameter of the convex component when it is zero may be larger than the inner diameter of the portion where the concave portion is formed on the peripheral surface of the unconstrained raceway ring.
Even if an external force is applied to reduce the diameter of a convex component that is in a state of being fitted in the concave portion, the diameter of the convex component is not reduced until the gap dimension at the dividing portion becomes zero or less. Therefore, if the outer diameter of the convex part when the gap size at the dividing part is zero is larger than the inner diameter of the part where the concave part is formed on the peripheral surface of the unconstrained raceway, I won't get over it.

Further, when the rolling bearing is the tapered roller bearing, the concave portion is an annular groove, and the convex component is a C-shape in which one place in the circumferential direction is divided when viewed from the axial direction, and the convex portion The part is inserted into the concave part in a state of being reduced in diameter using the elasticity of the convex part, and then expanded in diameter, so that a part other than the convex part is fitted into the concave part and no external force is applied. The outer diameter of the convex component may be equal to or smaller than the inner diameter of the groove bottom of the recess.
When the convex part fitted in the concave part gives an elastic restoring force to the outer ring, that is, when an interference is given between the groove bottom of the concave part and the outer periphery of the convex part, the inner circumferential large diameter side of the outer ring is caused by the elastic restoring force. There is a possibility that it may expand locally and adversely affect the accuracy of the raceway surface of the outer ring. However, if the outer diameter of the convex part in the state where no external force is applied is less than the inner diameter of the groove bottom of the concave part and there is no interference between the groove bottom of the concave part and the outer periphery of the convex part, the convex part is elastically restored to the outer ring. Since no force is applied, deformation of the outer ring can be prevented, and adverse effects on the accuracy of the raceway surface can be eliminated.

As described above, when no interference is provided between the groove bottom of the recess and the outer periphery of the convex component, a protrusion that protrudes toward the inner ring is provided on the groove bottom of the recess, and the protrusion is provided in the recess other than the protrusion. In the state where the portion is fitted, it is preferable that the protrusion is positioned at a parting position of the convex component in a circumferential phase.
When no interference is given between the groove bottom of the concave portion and the outer periphery of the convex component, a frictional force does not act between the two, and the convex component tends to rotate in the circumferential direction. However, as described above, the protrusion provided on the groove bottom of the concave portion is positioned at the dividing portion of the convex component in the circumferential phase, thereby preventing the convex component from rotating in the circumferential direction.

In this invention, the convex component may be partially provided in a part of the circumferential direction. For example, it can be like a rod.
In the rolling bearing according to the present invention, when the non-restraining raceway moves to a side where the deviation from the raceway surface of the rolling element is not restrained, if the convex portion hits at least one rolling element or the cage, the non-restraining raceway is further increased. Is restricted from moving. Therefore, even if the convex part is like a rod, it has a function of preventing the unconstrained raceway from coming off.
In addition, if the convex part is partially provided in a part of the circumferential direction, the lubricating oil flows from the raceway surface to the end surface side along the circumferential surface of the non-restraining raceway when lubricating oil is allowed to flow in the bearing. Since it does not hinder the flow of the bearing, heat generation of the bearing can be suppressed.

When using a convex part partially provided in a part in the circumferential direction, it is desirable that the material of the convex part has a larger linear expansion coefficient than the material of the unconstrained raceway ring. For example, when the material of the unconstrained raceway is bearing steel (linear expansion coefficient is 12.5 × 10 ⁻⁶ / ° C.), the material of the convex part is high strength brass (linear expansion coefficient is 18.4 × 10 ^−6). / ° C).
As described above, the convex component has a linear expansion coefficient larger than that of the non-restraining raceway, so that the convex component can be prevented from dropping from the concave portion due to heat generated by the bearing during operation.

When using a convex component with a narrow circumferential width, the circumferential width of the convex component is preferably larger than the sum of the circumferential clearances between the segments of the cage.
If the circumferential width of the convex parts is larger than the sum of the circumferential clearances between the cage segments, the segments are gathered at one circumferential location, and between the wide circumferential segments. Even when a gap occurs, it is possible to prevent the convex portion of the convex component from coming off from the gap.

In this invention, you may make the said convex part oppose the said holder | retainer. In that case, it is preferable that the opposing portions of the convex portion and the cage are parallel to each other.
Even if the convex portion is opposed to the cage, it is possible to prevent the unrestrained raceway from coming off. In that case, if the opposing portions of the convex portion and the cage are parallel to each other, the convex portion and the cage can be prevented from coming into edge contact, and the cage can be prevented from being damaged or worn. .

In this invention, the cage may be made of a resin blended with reinforcing fibers.
When the cage is made of resin, wear of the cage due to contact with the convex component can be suppressed by blending the reinforcing fiber with the resin. For example, glass fiber or carbon fiber is suitable as the reinforcing fiber to be added.

  The rolling bearing according to the present invention is disposed between an inner ring having a raceway surface on an outer periphery, an outer ring having a raceway surface on an inner periphery, and a raceway between the raceway surface of the inner ring and the raceway surface of the outer ring. A plurality of rolling elements, and a holder that holds the rolling elements in a circumferentially spaced manner so that the rolling elements can freely roll. At least one of the inner ring and the outer ring has at least one side of the raceway surface. In a rolling bearing that is a non-restraining race ring that does not restrain the rolling element from deviating from the raceway surface, and the cage is a segment cage that is divided into at least two segments in the circumferential direction. On the peripheral surface of the unconstrained raceway or its extended surface, the side that does not restrain the deviation of the rolling element from the raceway surface protrudes in a radial direction toward the opposite raceway and extends axially with the rolling element or cage. Opposite convex parts For digits, can not deviate unconstrained raceway after the bearing assembly, it is to improve the handling property at the time of assembling.

  An embodiment of the present invention will be described with reference to FIGS. The rolling bearing 1 is a tapered roller bearing, and holds an inner ring 2 and an outer ring 3 that are raceways, a plurality of rolling elements 4 formed of tapered rollers interposed between the inner and outer rings 2 and 3, and each rolling element 4. The cage 5 is provided.

  In FIG. 1, the inner ring 2 has a raceway surface 2a formed of a conical surface on the outer periphery, and has flange portions 2b and 2c on the large diameter side and the small diameter side of the raceway surface 2a, respectively. The outer ring 3 is formed with a raceway surface 3a opposite to the raceway surface 2a of the inner ring 2 on the inner periphery, and has no collar. The rolling element 4 is formed of a tapered roller, the outer peripheral surface is formed as a rolling surface 4a, and is freely rollable between the both raceway surfaces 2a and 3a. The inner ring 2 restrains the rolling elements 4 from deviating to both sides of the raceway surface 2a by the collar portions 2b and 2c. On the other hand, the outer ring 3 is a non-restrained race ring that does not restrain the rolling element 4 from deviating from the raceway surface 3a to the larger diameter side because it has no collar. Note that the rolling element 4 deviates from the raceway surface 3a to the smaller diameter side is regulated by the outer ring 3 itself.

  The cage 5 has a plurality of pockets 5a provided at predetermined intervals in the circumferential direction, and holds the rolling elements 4 in the pockets 5a so as to roll apart from each other in the circumferential direction. As shown in FIG. 2, the cage 5 is a segment cage that is divided into a plurality of segments 5 </ b> A in the circumferential direction.

  The large diameter side of the raceway surface 3a on the inner peripheral surface of the outer ring 3 which is a non-restraining raceway is cylindrical, and protrudes in the radial direction toward the inner race 2 in the cylindrical portion 3b and faces the rolling element 4 in the axial direction. A convex portion 7 is provided. The convex portion 7 includes a part of a convex component 6 that is a separate body from the outer ring 3. The convex component 6 is composed of the convex portion 7 and the other portion 8, and only the convex portion 7 is fitted to the outer ring 3 by fitting the portion 8 other than the convex portion into the concave portion 9 formed in the cylindrical portion 3 b. It is provided in a state of projecting from the inner peripheral surface. In addition, the convex part 7 shall not contact the rolling element 4 at the time of bearing operation.

  In this embodiment, as shown in FIGS. 2 and 4, the convex component 6 is a C-shaped retaining ring (FIG. 4) that is divided at one dividing point 6a in the circumferential direction when viewed from the axial direction. is there. Moreover, the said recessed part 9 is a cyclic | annular groove | channel, and as shown in FIG. 3, the protrusion 10 which protrudes toward the inner ring | wheel 2 is provided in the circumferential direction 1 place of the groove bottom. The convex component 6 is inserted into the concave portion 9 in a contracted state using the elasticity of the convex component 6 and then expanded in diameter, thereby fitting the portion 8 other than the convex portion into the concave portion 9. At that time, the protrusion 10 is positioned at the dividing portion 6a of the convex component 6 in the circumferential phase.

The outer diameter D ₀ (FIG. 5) of the convex part 6 when the gap dimension S (see FIGS. 2 and 4) of the dividing portion 6a is zero is the inner diameter d ₁ (FIG. 1) of the cylindrical portion 3b of the outer ring 3. It is set larger than. Therefore, the convex component 6 cannot be inserted into the concave portion 9 simply by reducing the diameter of the convex component 6. Therefore, as shown in FIG. 6, the positions of both ends of the convex component 6 are shifted in the axial direction, the diameter is reduced so that the gap dimension S of the dividing portion 6 a is equal to or less than zero, and the convex component 6 is inserted into the concave portion 9. At this time, if the outer ring 3 is heated and expanded, insertion of the convex component 6 into the concave portion 9 is further facilitated.

The outer diameter D _N (FIG. 4) of the convex component 6 in a state where no external force is applied is equal to or less than the inner diameter d ₂ (FIG. 1) of the groove bottom of the concave portion 9. That is, in the state where the convex part 6 is fitted in the concave part 9, no interference is given between the groove bottom of the concave part 9 and the outer periphery of the convex part 6, and the convex part 6 does not give elastic restoring force to the outer ring 3. It is like that.

  The rolling bearing having this configuration is a convex that faces the rolling element 4 in the axial direction on the large diameter side of the inner peripheral surface of the outer ring 3 that is an unconstrained race ring, that is, the side that does not restrain the deviation of the rolling element 4 from the raceway surface 3a. Since the portion 7 is provided, even if the outer ring 3 moves to the larger diameter side, the convex portion 7 hits the rolling element 4 and further movement of the outer ring 3 is restricted. Therefore, once the rolling bearing is assembled, the outer ring 3 does not come off, and handling when the rolling bearing is assembled to the machine is easy.

  Since the convex portion 7 is formed of a part of the convex component 6 that is a separate body from the outer ring 3, the processing of the convex portion 7 is easier than when the convex portion 7 is integral with the outer ring 3. Further, since the convex component 6 is provided by fitting a portion 8 other than the convex portion into a concave portion 9 formed on the inner peripheral surface of the outer ring 3, for example, the convex component 6 is attached to the outer ring 3 as shown in FIG. The width dimension (axial dimension) of the outer ring 3 can be shortened compared with the case where it is provided on the end face. In particular, when there is a dimensional allowance on the side where the deviation from the raceway surface 3a of the rolling element 4 on the inner peripheral surface of the outer ring 3 is not restricted, the inner peripheral surface of the outer ring 3 is not changed without changing the width dimension of the outer ring 3. The convex part 6 can be provided in the.

  Since the concave portion 9 is formed in the cylindrical portion 3 b on the inner peripheral surface of the outer ring 3, the convex component 6 is not easily detached from the concave portion 9. This is because, if the portion where the concave portion 9 is formed is cylindrical, the root position of the convex portion 7 of the convex component 6 and the rolling element 4 are compared with the case where the concave portion 9 is inclined farther away from the axial direction. And the moment acting on the convex part 6 when the rolling element 4 comes into contact with the convex part 6 can be reduced. Therefore, the convex component 6 is difficult to come off from the concave portion 9.

The convex component 6 in the state of being fitted in the concave portion 9 is not reduced in diameter until the gap dimension S of the dividing portion 6a becomes zero or less even when an external force is applied to reduce the diameter. Therefore, as in this embodiment, the outer diameter D ₀ of the convex component 6 when the gap dimension S of the dividing portion 6 a is zero is the inner diameter d of the portion where the concave portion 9 is formed on the inner peripheral surface of the outer ring 3. If it is larger than ₁ , the convex part 6 will not get over the concave part 9 and come off.

Further, in this embodiment, there the outer diameter D _N of the convex part 6 in a state where external force does not act as a less than or equal to the inner diameter d ₂ of the groove bottom of the recess 9. Thereby, the deformation | transformation of the outer ring | wheel 3 by having fitted and provided the convex component 6 in the recessed part 9 can be prevented. When the convex component 6 fitted in the concave portion 9 gives an elastic restoring force to the outer ring 3, that is, in a state where an interference is given between the groove bottom of the concave portion 9 and the outer periphery of the convex component 6, the outer ring is caused by the elastic restoring force. There is a possibility that the inner peripheral large diameter side of 3 is locally expanded and deformed. However, if the interference between the groove bottom of the concave portion 9 and the outer periphery of the convex component 6 is not given as the dimensional relationship, the convex component 6 does not give an elastic restoring force to the outer ring 3. Can be prevented. Thereby, the adverse effect on the accuracy of the raceway surface 3a of the outer ring 3 can be eliminated.

  As described above, since no interference is given between the groove bottom of the recess 9 and the outer periphery of the convex component 6, no frictional force acts between them, and the convex component 6 is easy to rotate in the circumferential direction. Since the protrusion 10 provided on the groove bottom of the concave portion 9 is positioned at the dividing portion 6a of the convex component 6 in the circumferential phase, the convex component 6 is prevented from rotating in the circumferential direction.

  In the above embodiment, the portion where the concave portion 9 is formed on the inner peripheral surface of the outer ring 3 is cylindrical, but the concave portion 9 is formed on the inner peripheral surface of the outer ring 3 formed of a conical surface as shown in FIG. Then, the convex component 6 may be fitted into the concave portion 9.

  9 and 10 show different embodiments. This rolling bearing 1 is formed into a rod shape in which convex parts 6 are partially provided in a part of the circumferential direction. In this embodiment, the convex member 6 has a cylindrical shape, and the tip 7a of the convex portion 7 has a tapered tapered shape. The tapered tip 7a faces the cage 5 in the axial direction. The tip 7a of the convex portion 7 and the end surface of the cage 5 which are the opposing portions of the convex portion 7 and the cage 5 are parallel to each other. In addition, the convex part 7 shall not contact the holder | retainer 5 at the time of bearing operation.

  In the rolling bearing according to the present invention, when the outer ring 3 moves to the larger diameter side, if the convex portion 7 hits at least one rolling element 4 or the cage 5, the outer ring 3 is restricted from moving further. Therefore, even if the convex component 6 has such a rod shape, it has a function of preventing the outer ring 3 from coming off.

  Since the tip 7a of the convex portion 7 and the end surface of the cage 5 are parallel to each other, the edge contact between the convex portion 7 and the cage 5 can be prevented, and the cage 5 can be damaged or worn. Can be suppressed. If the cage 5 is made of a resin in which reinforcing fibers are blended, wear of the cage 5 due to contact with the convex component 6 can be further suppressed. For example, glass fiber or carbon fiber is suitable as the reinforcing fiber to be added.

  Further, if the convex component 6 is partially provided in a part in the circumferential direction, the lubricating oil is lubricated from the raceway surface 3a to the large diameter side along the peripheral surface of the outer ring 3 when lubricating oil is allowed to flow in the bearing. Since the oil does not hinder the flow, heat generation of the bearing can be suppressed.

The diameter A of the projecting part 6 (FIG. 9) is, is made larger than the sum of the circumferential gap dimension _B 1 .about.B _n between segments 5A of the cage 5 (Figure 10). That is, the relationship of A> B ₁ + B ₂ + B ₃ +... + B _n is established. By adopting this dimensional relationship, even when the segments 5A are gathered in one place in the circumferential direction and a gap between the segments having a wide circumferential width is generated, the convex portion 7 of the convex component 6 comes out from the gap. I can prevent that. If convex parts 6 is not cylindrical, the circumferential width larger than the sum of the circumferential gap dimension B ₁ ~B _n. In addition, FIG. 10 is explanatory drawing for demonstrating each circumferential direction clearance gap between the segments 5A, and the dimension ratio of each part differs from an actual thing.

The material of the convex component 6 is preferably larger in linear expansion coefficient than the material of the outer ring 3. For example, when the material of the outer ring 3 is bearing steel (linear expansion coefficient is 12.5 × 10 ⁻⁶ / ° C.), the material of the convex component 6 is high strength brass (linear expansion coefficient is 18.4 × 10 ⁻⁶ / ° C). As described above, the convex component 6 has a linear expansion coefficient larger than that of the outer ring 3, so that the convex component 6 can be prevented from dropping from the concave portion 9 due to heat generated by the bearing during operation.

  Although the said embodiment made the front-end | tip 7a of the convex part 7 taper shape, each opposing part of the convex part 7 and the holder | retainer 5 was made mutually parallel, but the shape of the holder | retainer 5 like FIG. By devising, the opposing portions of the convex portion 7 and the cage 5 may be made parallel to each other. In the case of FIG. 11, a protruding portion 5 c that protrudes to the outer diameter side is provided on the annular portion 5 b on the large diameter side of the cage 5, and this protruding portion 5 c serves as a portion facing the convex portion 7. The convex portion 7 has a cylindrical shape that does not have a tapered tip.

  In each of the above embodiments, the type of the rolling bearing is a tapered roller bearing in which the inner ring is provided with both collars. However, the present invention can also be applied to other types of rolling bearings. For example, FIG. 12 is an application example in which the rolling bearing 1 is a cylindrical roller bearing, and FIG. 13 is an application example in which the rolling bearing 1 is an angular ball bearing.

  In the case of FIG. 12, the outer ring 3 is an unconstrained raceway, and the rolling elements 4 are not restrained from deviating from the raceway surface 3a on both axial sides of the raceway surface 3a. Therefore, the convex part 7 which consists of the convex component 6 is provided in the internal peripheral surface of the raceway surface 3a both sides of the outer ring | wheel 3. As shown in FIG. In this example, a C-shaped retaining ring is used as the convex component 6. In addition, the inner ring | wheel 2 has restrained that the rolling element 4 deviates from the track surface 2a by a pair of collar part 2b.

  In the case of FIG. 13, both the inner ring 2 and the outer ring 3 are unconstrained race rings. The inner ring 2 does not restrain the rolling element 4 from deviating from the raceway surface 2 a to the right side of the figure, and the outer ring 3 Deviating from the raceway surface 3a to the left side of the figure is not constrained. Therefore, convex portions 7 each including a convex component 6 are provided on the outer peripheral surface on the right side of the raceway surface 2 a of the inner ring 2 and on the inner peripheral surface on the left side of the raceway surface 3 a of the outer ring 3. In this example, a bar-shaped part partially provided in a part in the circumferential direction is used as the convex component 6. For the inner ring 2, the collar portion 2 b on the left side of the raceway surface 2 a restrains the rolling element 4 from deviating from the raceway surface 2 a to the left side, and for the outer ring 3, the collar portion on the right side of the raceway surface 3 a. By 3c, it has restrained that the rolling element 4 deviates from the track surface 2a to the right side.

The rolling bearing of the present invention is used, for example, for supporting the main shaft of the wind power generator shown in FIGS. The wind power generator 11 shown in the figure is provided with a nacelle 13 on a support base 12 so as to be able to turn horizontally, and a main shaft 15 is rotatably supported by a pair of rolling bearings 1 in a casing 14 of the nacelle 13. The blade 16 which is a swirl | wing blade is attached to the end which protruded 14 out. The other end of the main shaft 15 is connected to the speed increaser 17, and the output shaft 18 of the speed increaser 17 is coupled to the rotor shaft of the generator 19.
Other than wind power generators, it can be applied to construction machines such as hydraulic excavators and cranes, rotary tables of machine tools, parabolic antennas, and the like.

It is sectional drawing of the rolling bearing concerning embodiment of this invention. (A) is the figure which looked at the rolling bearing from the large end surface side, (B) is the IIB part enlarged view. It is the perspective view of the outer ring | wheel and convex component of the rolling bearing, and its partial enlarged view. (A) is a front view of the convex component, and (B) is a side view thereof. (A) is the front view which shows the different state of the same convex component, (B) is the side view. (A) is the front view which shows the further different state of the same convex component, (B) is the side view. It is sectional drawing of the rolling bearing concerning different embodiment of this invention. It is sectional drawing of the rolling bearing concerning further different embodiment of this invention. It is sectional drawing of the rolling bearing concerning further different embodiment of this invention. It is explanatory drawing which shows the circumferential direction clearance dimension between the segments of the holder | retainer of the rolling bearing. It is sectional drawing of the rolling bearing concerning further different embodiment of this invention. It is sectional drawing of the rolling bearing concerning further different embodiment of this invention. It is sectional drawing of the rolling bearing concerning further different embodiment of this invention. It is the perspective view which notched and represented a part of example of the wind power generator for wind power generation. It is a fracture side view of the wind power generator for wind power generation.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Rolling bearing 2 ... Inner ring 2a ... Inner ring raceway surface 2b, 2c ... Collar part 3 ... Outer ring 3a ... Outer ring raceway surface 3b ... Collar part 3c ... Collar part 4 ... Rolling element 5 ... Cage 5A ... Segment 6 ... Convex Part 6a ... Dividing part 7 ... Convex part 8 ... Non-convex part 9 ... Concave part 10 ... Protrusion

Claims (15)

An inner ring having a raceway surface on the outer periphery, an outer ring having a raceway surface on the inner periphery, and a plurality of rolling elements disposed between the raceway surface of the inner ring and the raceway surface of the outer ring so as to be freely rollable in a circumferential direction. And a cage that holds the rolling elements in a circumferentially spaced manner so that the rolling elements can freely roll, and at least one of the inner ring and the outer ring has a rolling element on at least one side of the raceway surface. In a rolling bearing that is a non-restraining race ring that does not restrain deviating from the surface, and the cage is a segment cage that is divided into at least two segments in the circumferential direction,
On the peripheral surface of the unconstrained raceway or its extension surface, the side that does not restrain the deviation of the rolling element from the raceway surface protrudes in a radial direction toward the opposite raceway and extends axially with the rolling element or cage. A rolling bearing characterized by providing opposing convex portions.   The rolling bearing according to claim 1, wherein only one of the inner ring and the outer ring is the unconstrained raceway ring.   3. The rolling bearing according to claim 1, wherein the unconstrained race ring has a flange portion that restrains the rolling element from deviating from the raceway surface on one side of the raceway surface.   4. The convex portion according to claim 1, wherein the convex portion is a part of a convex component that is separate from the unconstrained raceway, and the convex component is a peripheral surface of the non-constraint raceway. A rolling bearing provided by fitting a portion other than the convex portion into the concave portion formed in the inner surface.   The rolling bearing according to claim 4, wherein a portion where the concave portion is formed on a peripheral surface of the non-restraining raceway is cylindrical.   The double collar according to any one of claims 1 to 5, wherein the rolling element is a tapered roller, and the inner ring has flange parts protruding radially toward the outer ring on both sides of the raceway surface. Rolling bearings with bearing rings.   In Claim 6, the said recessed part is a cyclic | annular groove | channel, and the said convex component is C-shape where one place of the circumferential direction was divided seeing from the axial direction, and the said convex component has this convex component By using elasticity, the diameter is reduced and inserted into the recess, and then the diameter is expanded, so that a portion other than the protrusion is fitted into the recess, and the gap size at the dividing portion is zero. A rolling bearing in which an outer diameter of a convex component is larger than an inner diameter of a portion where the concave portion is formed on the peripheral surface of the unconstrained raceway ring.   In Claim 6 or Claim 7, the concave portion is an annular groove, and the convex component is a C-shape that is divided at one place in the circumferential direction when viewed from the axial direction. The convex component in a state in which a portion other than the convex portion is fitted into the concave portion and no external force is applied by inserting into the concave portion in a contracted state and then expanding the diameter using the elasticity of the convex component. A rolling bearing in which the outer diameter is equal to or smaller than the inner diameter of the groove bottom of the recess.   In Claim 8, in a state where a projection protruding toward the inner ring is provided at the groove bottom of the recess, and the projection is provided by fitting a portion other than the projection into the recess, the circumferential phase is A rolling bearing in which the protrusion is located at a parting point of a convex part.   6. The rolling bearing according to claim 4 or 5, wherein the convex component is partially provided in a part in a circumferential direction.   The rolling bearing according to claim 10, wherein a material of the convex component has a larger linear expansion coefficient than a material of the unconstrained raceway ring.   The rolling bearing according to claim 10 or 11, wherein a circumferential width of the convex component is larger than a sum of circumferential clearance sizes between segments of the cage.   The rolling bearing according to claim 1, wherein the convex portion is opposed to the cage.   The rolling bearing according to claim 13, wherein the opposing portions of the convex portion and the cage are parallel to each other.   The rolling bearing according to any one of claims 1 to 14, wherein the cage is made of a resin in which reinforcing fibers are blended.

Images