JP2017008990A - Seal structure of slewing bearing and slewing bearing - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a seal structure of a slewing bearing which can efficiently and accurately perform the exchange work of a seal member, and can prevent that an adhesive for fixing the seal member leaks to the inside/outside of the bearing.SOLUTION: This seal structure is employed to a slewing bearing having an elastic-body made seal member 7A for sealing an axial end of a bearing space 6. One raceway ring 1 has a stepped annular notch 11 which is formed over a peripheral face 1a from an end face 1c, and a fitting recess 12 which extends to the inside of an axial direction from the annular notch 11. The seal member 7A has a base part 23 which is fit into the annular notch 11, seal lips 21, 22 which contact with a peripheral face 2a of the other raceway ring 2, and a fitting protrusion 24 which is fixedly fit into the fitting recess 12. Marking recesses 40 which are opened at the end face 1c are arranged in a plurality of points of a peripheral face 16 of the annular notch 11 in a circumferential direction, and marks 41 which coincide with the marking recesses 40 in positions in a peripheral direction are arranged at the seal member 7A.SELECTED DRAWING: Figure 2

Description

  The present invention is, for example, a swivel used for a swivel part of various machines used in the vicinity of the outdoors or indoors, such as a swivel seat for a yaw and a blade of a wind power generator, a deck crane, a construction machine, and a lifting machine. The present invention relates to a seal structure of a bearing and a slewing bearing.

  It is said that the maintenance cost of wind power generators is about 25% of the operating cost. Maintenance costs include losses from shutting down operations. For this reason, in order to reduce the maintenance cost, it is important to facilitate the maintenance and shorten the operation stop time.

  One of the maintenance of wind turbine generators is the replacement of seals for slewing bearings used in yaw and blade slewing seats. This type of slewing bearing is generally lubricated with grease, and a rubber seal member is mounted to prevent foreign matter from entering and grease leakage from the inside of the bearing (for example, Patent Document 1).

  The seal member has problems such as wear caused by rubbing against the peripheral surface of the race, plastic flow and fatigue failure caused by constant external force, deterioration and aging due to oxidation, and it is necessary to replace it once every several years. is there. However, current yaw and blade slewing bearings are not designed with seal replacement in mind. For this reason, it takes time to replace the seal, which has been a factor in reducing the operating rate of the wind turbine generator.

JP 2011-27235 A

  Many slewing bearings for yaw and blade have a diameter exceeding 1000 mm. In addition, since the seal member is assembled manually, it is easy for variations in assembly accuracy to occur. For this reason, it is important to design with sufficient consideration of variations in assembly accuracy.

  As an example of the variation in assembling accuracy, as shown in FIG. 11, a portion A in which a seal member 7 is stretched in the circumferential direction on any one of the inner and outer rings 1 and 2 (for example, the inner ring) 1 It may be incorporated in a state where the pressed and contracted portion B is unevenly distributed. Thus, when the seal member 7 is not uniformly integrated in the circumferential direction, a tensile force acts on the stretched portion A, so that the seal member 7 is uniformly integrated as shown in FIG. ), The seal lips 21 and 22 are deformed in a standing manner with respect to the peripheral surface 2a of the other raceway ring (for example, the outer ring) 2. For this reason, reaction force from the outer ring 2 is increased, and wear is promoted by the seal lips 21 and 22 being rubbed strongly against the outer ring 2. On the other hand, the compression force acts on the compressed portion B, so that the seal lips 21 and 22 are compared with the case where the seal member 7 is uniformly incorporated, as shown by the chain line in FIG. The other bearing ring 2 is deformed so as to fall over the peripheral surface 2a. For this reason, the reaction force from the other race 2 is weakened and there is a concern about grease leakage. Therefore, in order to extend the life of the seal member 7 and prevent grease leakage, it is very important to incorporate the seal member 7 with high accuracy as intended.

  Further, for example, as shown in FIG. 13, the seal member 7 used for the slewing bearing for yaw and blade is incorporated in an annular seal mounting portion 10 provided on one of the race rings 1, and the seal mounting portion 10 The fitting concave portion 12 is fixed by fitting the fitting convex portion 24 of the seal member 7 into the fitting concave portion 12. At that time, if an adhesive is used, the fixing force is further improved. The adhesive is applied to the inner surface of the fitting recess 12.

  When the fitting convex portion 24 of the seal member 7 is fitted into the fitting concave portion 12 with the adhesive applied to the inner surface, excess adhesive flows in the circumferential direction in the fitting concave portion 12, but the adhesion is lost. The agent may flow out to the bearing space 6 between the inner and outer rings 1 and 2 and the outside of the bearing. When a large amount of adhesive flows into the bearing space 6, the adhesive adheres to the rolling elements and the contact surface pressure partially increases, which is harmful to the bearing.

  The object of the present invention is to perform the replacement operation of the seal member efficiently and accurately, and when using an adhesive for fixing the seal member, it is possible to prevent excess adhesive from leaking into and out of the bearing. It is to provide a seal structure for a slewing bearing.

  In the seal structure of the slewing bearing according to the present invention, raceway grooves are formed on the mutually opposing peripheral surfaces of the inner ring and outer ring, which are race rings, and a plurality of rolling elements are provided between the race grooves of the inner and outer rings. A seal member made of an elastic body that seals the axial end portion of the bearing space between, and one of the inner and outer rings has a step shape formed from the end surface to the opposing circumferential surface An annular notch, and a fitting recess extending inward in the axial direction of the raceway from the annular notch, and the seal member includes a base that fits into the annular notch, and the base and the inner and outer rings. A seal lip extending toward the other raceway and contacting the opposing circumferential surface of the other raceway, and a fitting that protrudes inward in the axial direction from the base and fits into the fitting recess in a fixed state And a circumferential surface of the annular notch A plurality of locations of definitive circumferentially provided with a mark recess opened to the end surface, the seal member, the circumferential position, characterized in that a mark which is consistent with the mark recess.

  According to this configuration, the base of the seal member is fitted into the annular notch of one of the race rings, and the fitting protrusion of the seal member is fitted into the fitting recess of the one of the race rings, so that the seal member is fitted into one of the race rings. Is incorporated. At this time, the seal member can be easily and accurately incorporated by aligning the circumferential position of the mark of the seal member with the mark recess of one of the races. In addition, when an adhesive is used for fixing the seal member, even if a part of the adhesive applied to the inner surface of the fitting recess leaks out of the fitting recess, the leaked adhesive is transferred to the mark recess. By flowing in, it is possible to prevent the adhesive from flowing out to the bearing space between the inner and outer rings and the outside of the bearing.

In this invention, it is preferable that the mark recess is deeper in the axial direction than the annular notch and communicates with the fitting recess.
In this case, since the adhesive leaking from the fitting recess easily flows into the mark recess, it is possible to reliably prevent the adhesive from flowing out to the bearing space between the inner and outer rings and the outside of the bearing.

In this invention, the concave part for a mark may be capable of inserting a tool used for removing the seal member.
In this case, the operation of removing the old seal member is facilitated by inserting a tool into the mark recess.

In the present invention, the concave portion for a mark may have an arc shape when viewed from the axial direction of the one raceway ring.
If the mark recess is arcuate, the mark recess can be easily cut using a rotary tool.

In this invention, the depth in the axial direction of the mark recess is 1 / of the height from the axial outer end of the base of the seal member to the axial inner end of the fitting convex. It is desirable to be 2 or more.
If the depth of the mark recess and the height of the seal member satisfy the above relationship, when removing the old seal member for maintenance or the like, it is possible to easily remove the seal member by inserting a tool into the mark recess It becomes possible.

In this invention, when the diameter of the circumference in which the plurality of mark concave portions are arranged is φ mm, and the number of the mark concave portions is N,
φ × π / N ≦ 1000
It is desirable to satisfy this relationship.
When the distance between two adjacent mark recesses (φ × π / N) exceeds 1000 mm, the seal member is incorporated into the raceway in a state where the circumferentially stretched portion and the compressed portion are unevenly distributed. It becomes easy. By satisfying the above relationship, the seal member can be uniformly incorporated in the circumferential direction.

In this invention, the inner surface of the fitting concave portion of the one bearing ring and the outer surface of the fitting convex portion of the seal member may be adhered by an adhesive.
If an adhesive is used, the fitting convex part of a sealing member can be fixed reliably.

  The slewing bearing according to the present invention is one in which any of the above-described seal structures is applied, and supports the blade of the wind power generator so as to be rotatable about an axis substantially perpendicular to the main axis with respect to the main axis. Alternatively, the nacelle of the wind power generator may be supported so as to be rotatable with respect to the support base.

  In the seal structure of the slewing bearing according to the present invention, raceway grooves are formed on the mutually opposing peripheral surfaces of the inner ring and outer ring, which are race rings, and a plurality of rolling elements are provided between the race grooves of the inner and outer rings. A seal member made of an elastic body that seals the axial end portion of the bearing space between, and one of the inner and outer rings has a step shape formed from the end surface to the opposing circumferential surface An annular notch, and a fitting recess extending inward in the axial direction of the raceway from the annular notch, and the seal member includes a base that fits into the annular notch, and the base and the inner and outer rings. A seal lip extending toward the other raceway and contacting the opposing circumferential surface of the other raceway, and a fitting that protrudes inward in the axial direction from the base and fits into the fitting recess in a fixed state And a circumferential surface of the annular notch In addition to providing concave portions for marks opened in the end face at a plurality of locations in the circumferential direction, and providing the seal members with marks whose circumferential positions coincide with the concave portions for marks, it is possible to efficiently replace the seal member. In addition, it can be performed with high accuracy, and when an adhesive is used for fixing the seal member, it is possible to prevent excess adhesive from leaking into and out of the bearing.

1 is a longitudinal sectional view of a slewing bearing to which a seal structure according to an embodiment of the present invention is applied. (A) is the elements on larger scale of the slewing bearing, (B) is the exploded view. It is the elements on larger scale of the different longitudinal cross-section of the slewing bearing. It is a top view of the inner ring | wheel of the slewing bearing. It is a top view of the seal member of the slewing bearing. It is a top view which shows the state which incorporated the seal member in the inner ring | wheel of the slewing bearing. It is sectional drawing of a part of slewing bearing to which the seal structure concerning different embodiment of this invention was applied. It is sectional drawing of a part of slewing bearing to which the seal structure concerning further different embodiment of this invention was applied. It is the perspective view which notched and represented a part of example of the wind power generator. It is a fracture side view of the wind power generator. It is explanatory drawing of the force which acts on a sealing member. It is explanatory drawing of a deformation | transformation of a sealing member. It is sectional drawing of the seal structure of the conventional slewing bearing.

An embodiment of the present invention will be described with reference to FIGS.
This slewing bearing is, for example, a bearing that supports a blade of a wind power generator so as to be rotatable about an axis substantially perpendicular to the main shaft axis with respect to the main shaft, or a nacelle of the wind power generator is supported so as to be rotatable with respect to a support base. Used as a bearing.

  As shown in FIG. 1, the slewing bearings are formed on the inner ring 1 and the outer ring 2 that are race rings and the outer circumferential surface 1 a and the inner circumferential surface 2 a that are circumferential surfaces of the inner and outer rings 1 and 2 that face each other. A ball 3 as a plurality of rolling elements is provided between the grooves 1b and 2b so as to freely roll. A spacer or a cage is interposed between the balls 3 and 3 adjacent in the circumferential direction (not shown).

  Each of the raceway grooves 1b and 2b of the inner and outer rings 1 and 2 is composed of two curved surfaces. The two curved surfaces constituting each raceway groove 1b, 2b are Gothic arch-shaped arcs having a larger radius of curvature than that of the ball 3 and different centers of curvature. Each ball 3 is in contact with the curved surfaces of the raceway groove 1b of the inner ring 1 and the raceway groove 2b of the outer ring 2 at a contact point and makes contact at four points. That is, this slewing bearing is configured as a four-point contact ball bearing. The spacer is made of a resin material, for example. The spacer has a concave shape in which the rolling element contact surfaces on both sides form a spherical surface that is deeply recessed toward the center. The cage is manufactured from, for example, an iron plate. This cage made of iron plate is disposed between the inner and outer rings 1 and 2 and has a pocket into which the ball 3 is inserted.

  A plurality of through holes 4 are provided in the inner ring 1 at regular intervals in the circumferential direction. These through holes 4 are used, for example, for connecting and fixing the inner ring 1 to a nacelle casing, a blade, etc., which will be described later. The outer ring 2 is also provided with a plurality of through holes 5 at regular intervals in the circumferential direction. These through-holes 5 are used, for example, for connecting and fixing the outer ring 2 to a support base described later. The through holes 4 and 5 of the inner and outer rings 1 and 2 are formed in parallel to the bearing axial direction.

The seal structure will be described.
The bearing space 6 between the inner and outer rings 1 and 2 is filled with grease, and both axial ends, that is, upper and lower ends of the bearing space 6 are sealed by seal members 7A and 7B, respectively. Since the seal structure at the upper end and the seal structure at the lower end of the bearing space 6 are the same structure, the seal structure at the upper end will be described as a representative. In order to prevent the grease from leaking from one side in the axial direction of the bearing space 6, a seal member may be provided only on the side where it is not desired to leak. For example, in the case of a blade support bearing, a seal member may be provided only at the blade side end of the bearing space 6.

  2A and 2B are a sectional view and an exploded view of the longitudinal section shown in FIG. 1 in the seal structure at the upper end, and FIG. 3 is a sectional view of a different longitudinal section. As shown in FIG. 2B, a seal attachment portion 10 for attaching the seal member 7A is provided at the upper end portion of the outer peripheral surface 1a of the inner ring 1. The seal mounting portion 10 includes a stepped annular notch 11 formed from the upper end surface 1 c to the outer peripheral surface 1 a and a fitting recess 12 extending downward from the annular notch 11. The height of the upper surface of the inner ring 1 serving as the bottom surface of the annular notch 11 is different on both sides of the fitting recess 12, and the outer diameter side upper surface 13 is formed lower than the inner diameter side upper surface 14. An annular groove 15 as a press-fitting allowance is formed on the inner peripheral wall surface of the fitting recess 12. In the case of this example, the annular groove 15 is positioned slightly above the intermediate portion in the axial direction of the fitting recess 12 and has a circular arc cross-sectional shape.

  The annular notch 11 is provided with a plurality of mark recesses 40 which are opened in the upper end surface 1c and recessed toward the inner diameter side in a plurality of circumferential directions. The mark recess 40 includes a main body portion 40a positioned on the inner diameter side of the annular notch 11, and a groove-shaped communication portion 40b formed on the inner diameter side upper surface 14 and communicating the main body portion 40a and the fitting recess portion 12. Become. In this embodiment, the bottom surface height of the main body part 40a and the communication part 40b is the same as the height of the outer diameter side upper surface 13. As in the example of FIG. 2, the axial depth of the mark concave portion 40 is the height in the axial direction of a seal member 7A described later, that is, the height from the upper end of the base portion 23 to the lower end of the fitting convex portion 24. It is desirable that it is 1/2 or more. When the upper end of the base 23 of the seal member 7A protrudes above the upper end surface 1c of the inner ring 1 as in the example of FIG. 2, the axial height of the seal member 7A is the upper end surface 1c of the inner ring 1. To the lower end of the fitting convex portion 24.

For example, as shown in FIG. 4, the mark recesses 40 are provided at four locations at equal intervals in the circumferential direction. In consideration of the assembly accuracy of the seal member 7A, when the diameter of the circumference in which the plurality of mark recesses 40 are arranged is φmm and the number of mark recesses 40 is N,
φ × π / N ≦ 1000
It is desirable to satisfy this relationship. In this example, the mark recess 40 has an arc shape when viewed from above. Thus, when it is circular arc shape, it can cut easily using a rotary tool. 2 shows a vertical cross section where the mark recess 40 of the inner ring 1 exists, and FIG. 3 shows a vertical cross section where the mark recess 40 does not exist.

  2 and 3, the seal member 7 </ b> A is made of an elastic body such as a nitrile group or an acrylic group, and the mounted portion 20 attached to the seal mounting portion 10, and the mounted portion 20 to the bearing space 6, respectively. And two seal lips 21 and 22 extending obliquely inward and outward. Both of these two seal lips 21 and 22 are in contact with the inner peripheral surface 2a of the outer ring 2 in the assembled state of the seal member 7A shown in FIG. The seal lip 21 that extends inward is a main lip that mainly prevents leakage of grease from the bearing space 6, and the seal lip 22 that extends outwardly allows foreign matters such as moisture and dust to enter the bearing space 6 mainly from the outside. It is a secondary lip to prevent. The number of seal lips may be three or more.

  The attached portion 20 of the seal member 7A includes a base portion 23 that fits into the annular notch 11 of the seal attachment portion 10, and a fitting that protrudes inward in the axial direction from the base portion 23 and fits into the fitting recess 12 in a fixed state. It consists of a convex part 24. The protruding length in the axial direction of the fitting convex portion 24 is shorter than the axial depth of the fitting concave portion 12. Further, the radial width of the fitting convex portion 24 is slightly narrower than the radial width of the fitting concave portion 12.

  A first annular protrusion 25 that press fits into the annular groove 15 of the fitting recess 12 protrudes from the inner diameter side surface of the fitting protrusion 24. The first annular protrusion 25 is located at an axial position corresponding to the annular groove 15 and has a circular cross section. Further, a second annular protrusion 26 having a smaller radial dimension and smaller axial dimension than the first annular protrusion 25 protrudes from the outer diameter side surface of the fitting convex portion 24.

  As shown in FIG. 5, the same number of marks 41 as the mark recesses 40 are provided on the upper surface of the seal member 7A. The circumferential position of the mark 41 coincides with the mark recess 40 when the seal member 7A is assembled. The mark 41 only needs to be visible when viewed from above when the seal member 7A is incorporated into the inner ring 1. For example, the mark 41 may be a projection or colored in a color different from the surroundings.

  When assembling the seal member 7A into the inner ring 1, as shown in FIGS. 2 and 3, the base 23 of the mounted portion 20 is connected to the annular notch 11 (FIG. 2B) of the seal mounting portion 10 (FIG. 2B). ) And the fitting convex portion 24 is fitted into the fitting concave portion 12 of the seal mounting portion 10 by press fitting. At that time, as shown in FIG. 6, the seal member 7A can be easily and accurately incorporated by aligning the circumferential position of the mark 41 of the seal member 7A with the mark recess 40 of the inner ring 1. Thus, the sealing member 7A assembled with high accuracy does not have a portion stretched in the circumferential direction and a portion compressed and contracted (see FIG. 11).

  In the assembled state of the seal member 7A, the fitting projection 24 is fitted into the fitting recess 12 as shown in FIGS. 2 and 3, so that the attached portion 20 of the seal member 7A is the seal attachment portion of the inner ring 1. 10 is held. At this time, since the first annular protrusion 25 is engaged with the annular groove 15, the fitting convex portion 24 is prevented from coming off from the fitting concave portion 12. Further, the second annular protrusion 26 is pushed and deformed by the inner peripheral wall surface of the fitting recess 12 and functions as a press-fitting allowance. As a result, the fitting convex portion 24 of the seal member 7 </ b> A is fixed to the inner ring 1. If an adhesive is used, the fixing of the fitting convex part 24 will become still more reliable.

  When using an adhesive, the adhesive is applied to the inner surface of the fitting recess 12. When the fitting convex portion 24 is fitted into the fitting concave portion 12 with the adhesive applied to the inner surface, excess adhesive may leak from the fitting concave portion 12, but the leaked adhesive is used as the mark concave portion. Since the fluid flows into the main body 40a through the 40 communication portions 40b, the adhesive can be prevented from flowing out to the bearing space 6 or the outside of the bearing.

  In a state in which the seal member 7A is incorporated in the seal mounting portion 10 of the inner ring 1, the outer diameter side upper surface 13 and the inner diameter side upper surface 14 of the inner ring 1 that are the bottom surface of the annular notch 11 are the seal member 7A in the assembled state of the seal member 7A. It becomes a reference plane to maintain the posture of the machine properly. The outer diameter side lower surface 27 and the inner diameter side lower surface 28 of the seal member 7A are in contact with the outer diameter side upper surface 13 and the inner diameter side upper surface 14, respectively.

  By using the outer diameter side upper surface 13 and the inner diameter side upper surface 14 positioned on both sides of the fitting recess 12 as the reference surfaces as described above, the seal member 7A is fitted by the internal pressure of the bearing space 6 or the external pressure when the seal member is attached. It is restricted that the posture is changed with the convex portion 24 as a fulcrum. As a result, the seal lips 21 and 22 are not separated from the inner peripheral surface 2a of the outer ring 2, and grease leakage from the bearing space 6 and foreign matters such as moisture and dust from the outside are prevented from entering the bearing space 6. it can.

  7 and 8 show different seal structures. In this seal structure, the size of the mark recess 40 is made larger in the axial direction and the radial direction than in the seal structure of FIG. In this example, the bottom surface heights of the main body part 40 a and the communication part 40 b of the mark recess 40 coincide with the bottom surface height of the fitting recess 12. As described above, when the depth of the mark recess 40 is increased, the adhesive 42 leaking from the fitting recess 12 easily flows into the mark recess 41 as shown in FIG. It can be surely prevented from flowing out.

Further, by enlarging the mark recess 40, the old seal member 7A can be removed by inserting the tool 43 into the mark recess 40 as shown in FIG. Specifically, the tip of the tool 43 is brought into contact with the inner surface 28 of the seal member 7A, and the seal member 7A is taken out upward. For this reason, the replacement work of the seal member 7A is easy.
In addition, even when the size of the mark recess 40 is small as in the seal structure shown in FIG. 2, the axial depth of the mark recess 40 is not less than ½ of the axial height of the seal member 7A. The tool 43 can be inserted into the mark recess 40 to easily remove the seal member 7A.

In the upper end seal structure described above, the seal attachment portion 20 for attaching the seal member 7A is provided in the inner ring 1, and the seal lips 21, 22 of the seal member 7A are in contact with the inner peripheral surface 2a of the outer ring 2. That is, the inner ring 1 is one of the bearing rings referred to in the claims, and the outer ring 21 is the other bearing ring referred to in the claims.
On the other hand, in the seal structure at the lower end, a seal attachment portion 20 for attaching the seal member 7B is provided on the outer ring 2, and the seal lips 21, 22 of the seal member 7B are in contact with the outer peripheral surface 1a of the inner ring 1. That is, the outer ring 2 is one of the bearing rings referred to in the claims, and the inner ring 1 is the other bearing ring referred to in the claims.

  9 and 10 show an example of a wind power generator. This wind power generator 51 is provided with a nacelle 53 on a support base 52 so as to be able to turn horizontally, and a main shaft 55 is rotatably supported in a casing 54 of the nacelle 53, and at one end of the main shaft 55 protruding outside the casing 54. The blade 56 which is a swirl wing is attached. The other end of the main shaft 55 is connected to a speed increaser 57, and the output shaft 58 of the speed increaser 57 is coupled to the rotor shaft of the generator 59.

  The nacelle 53 is rotatably supported by the slewing bearing BR1. In the slewing bearing to which any one of the seal structures of the above embodiments is applied, for example, a slewing bearing BR1 for the nacelle 53 having a gear or the like provided on the outer peripheral surface of the outer ring 2 is used. As shown in FIG. 9, a plurality of drive sources 60 are installed in the casing 54, and a pinion gear is fixed to each drive source 60 via a speed reducer (not shown). It arrange | positions so that the said gear of the outer ring | wheel 2 (FIG. 1) may mesh | engage with the said pinion gear. For example, the outer ring 2 is connected and fixed to the support base 52 by a plurality of through holes 5 (FIG. 1), and the inner ring 1 (FIG. 1) is fixed to the casing 54 by the through holes 4 (FIG. 1). The plurality of drive sources 60 are driven in synchronization, and this turning driving force is transmitted to the outer ring 2. Therefore, the nacelle 53 can turn relative to the support base 52.

  The blade 56 is rotatably supported by the swing bearing BR2. This slewing bearing BR2 is a slewing bearing to which any one of the seal structures of the above-described embodiments is applied. For example, a bearing provided with a gear on the inner circumferential surface of the inner ring 1 is applied. A driving source for rotating the blade 56 is provided at the protruding end portion 55 a of the main shaft 55. The outer ring 2 of the slewing bearing is connected and fixed to the distal end portion 55a, and a gear provided on the inner peripheral surface of the inner ring 1 meshes with the pinion gear of the drive shaft. By driving this drive source and transmitting this turning drive force to the inner ring 1, the blade 56 can turn. Therefore, the slewing bearing BR2 supports the blade 56 of the wind power generator with respect to the main shaft 55 so as to be rotatable about an axis L2 substantially perpendicular to the main shaft axis L1. In this way, the angle of the blade 56 and the direction of the nacelle 53 are changed at any time according to the wind state.

  The slewing bearing of the present invention can be applied to, for example, construction machines such as hydraulic excavators and cranes, rotary tables of machine tools, gun seats, parabolic antennas and the like in addition to wind power generators.

  As mentioned above, although the form for implementing this invention based on the Example was demonstrated, embodiment disclosed here is an illustration and restrictive at no points. The scope of the present invention is defined by the terms of the claims, rather than the description above, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.

1 ... Inner ring (one raceway)
1a ... outer peripheral surface (opposing peripheral surface)
1b ... raceway groove 1c ... upper end surface (end surface)
2. Outer ring (other race)
2a ... Inner peripheral surface (opposing peripheral surface)
2b ... raceway groove 3 ... ball (rolling element)
6 ... Bearing space 7A, 7B ... Seal member 11 ... Circular notch 12 ... Fitting recess 16 ... Peripheral surfaces 21, 22 ... Seal lip 23 ... Base 24 ... Fitting protrusion 40 ... Mark recess 41 ... Mark 42 ... Adhesion Agent 43 ... Tool 53 ... Nacelle 56 ... Blades BR1, BR2 ... Slewing bearing

Claims (9)

A raceway groove is formed on each of the circumferential surfaces of the inner ring and the outer ring that are raceways opposite to each other, and a plurality of rolling elements are provided between the raceway grooves of the inner and outer rings, and an axial end portion of the bearing space between the inner and outer rings is provided. In a seal structure of a slewing bearing provided with a sealing member made of an elastic body for sealing,
Any one of the inner and outer rings has a stepped annular notch formed from the end surface to the opposed peripheral surface, and extends from the annular notch inward in the axial direction of the bearing ring. A fitting recess,
The seal member includes a base portion that fits into the annular notch, a seal lip that extends from the base portion toward the other raceway of the inner and outer rings and contacts the opposing circumferential surface of the other raceway, A projection protruding from the base inward in the axial direction and fitted into the fitting recess in a fixed state;
A plurality of mark recesses opened in the end face are provided at a plurality of locations in the circumferential direction on the circumferential surface of the annular notch, and a mark whose circumferential position coincides with the mark recess is provided on the seal member. A seal structure for a slewing bearing.   2. The seal structure for a slewing bearing according to claim 1, wherein the mark recess is deeper in the axial direction than the annular notch and communicates with the fitting recess.   The seal structure of the slewing bearing according to claim 1 or 2, wherein a tool used for removing the seal member can be inserted into the mark recess. 4. The seal structure of a slewing bearing according to claim 1, wherein the mark recess is an arc shape when viewed from the axial direction of the one bearing ring. 5. .   5. The seal structure of the slewing bearing according to claim 1, wherein the axial depth of the mark concave portion is from the outer end in the axial direction of the base portion of the seal member. A seal structure for a slewing bearing that is at least ½ the height of the fitting convex portion to the inner end in the axial direction. In the seal structure of the slewing bearing according to any one of claims 1 to 5, when the diameter of the circumference in which the plurality of mark recesses are arranged is φmm and the number of the mark recesses is N,
φ × π / N ≦ 1000
Slewing bearing seal structure that satisfies the above relationship.   The seal structure of the slewing bearing according to any one of claims 1 to 6, wherein an inner surface of the fitting concave portion of the one bearing ring and an outer surface of the fitting convex portion of the seal member are adhesives. The seal structure of the slewing bearing bonded by.   A slewing bearing having the seal structure according to any one of claims 1 to 7, wherein the slewing bearing supports the blade of the wind power generator with respect to the main shaft so as to be rotatable about an axis substantially perpendicular to the main shaft axis. .   A slewing bearing having the seal structure according to any one of claims 1 to 7, wherein the slewing bearing supports the nacelle of the wind power generator so as to be pivotable with respect to a support base.

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