JP2016095023A - Bearing device, mechanical device, and bearing - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a bearing device which inhibits abnormality from being caused by a static load received thereby to achieve long bearing life, and to provide a mechanical device and a bearing.SOLUTION: A bearing device includes a housing 20 and a bearing 30 attached to the housing 20. The bearing 30 includes an outer ring 32 contacting with the housing 20. A part of the outer ring 32 in a circumferential direction is formed as a load area which receives a radial load when the bearing 30 is in a stationary state. The bearing device further includes a moving part 40 which may move the load area in the outer ring 32.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a bearing device, a mechanical device, and a bearing, and particularly relates to a bearing device including a bearing that is difficult to exchange, a mechanical device including the bearing device, and the bearing.

  A load associated with the rotational operation is applied to the bearing device, but a radial load (static load) due to its own weight or the like is applied even when the operation is stopped (at rest). The static load applied to the bearing device is applied to a partial region in the circumferential direction on the rolling surface of the inner ring or the outer ring depending on the configuration of the bearing device.

  In a bearing device including a rolling bearing, for example, when an inner ring and a rotating shaft are fitted together, a static load (outer ring stationary load) is applied to the outer ring when the outer ring and a housing of the bearing device are fitted together. A region that receives a static load in the outer ring (hereinafter referred to as a load region) is formed in a part of the outer ring in the circumferential direction. For this reason, the outer ring load region is most frequently subjected to a load at the rolling contact portion formed between the rolling elements and the outer ring compared to other regions other than the outer ring load region, and abnormalities such as peeling due to metal fatigue occur. It's easy to do.

  Further, in a bearing device including a slide bearing, a static load (bearing static load) is applied to the bearing when the bearing is fitted to the housing of the bearing device. Here, the outer ring static load in the rolling bearing can be replaced with the bearing static load in the sliding bearing, and the sliding surface of the sliding bearing has a longer sliding distance than the sliding surface of the shaft, and thus wear easily proceeds.

  In such a bearing device, if the bearing can be replaced easily and at low cost, it is common to replace the bearing assuming that the bearing has reached the end of its service life due to occurrence of abnormalities such as peeling and the progress of wear. . For example, Japanese Patent Application Laid-Open No. 2002-235754 describes a split bearing for easily performing bearing replacement. Japanese Patent Application Laid-Open No. 2004-011737 describes a self-aligning roller bearing having an inner ring that has been subjected to shot peeling treatment in order to reduce the frequency of bearing replacement in a wind turbine.

JP 2002-235754 A JP 2004-011737 A

  However, in a large-sized bearing device and a bearing device installed in a place where replacement work is difficult, there are cases where the replacement of the bearing is not easy and the cost is high. Examples of such bearing devices include a wind turbine generator bearing device, a tidal power generator bearing device, a large marine bearing device, a large truck bearing device, and a large turbine bearing device.

  In particular, since the main bearing constituting the drive train of the bearing device for a wind turbine generator is provided in a nacelle arranged at a high place, it is necessary to lower the entire drive train to the ground in order to perform replacement work. In addition, it is necessary to re-install the drive train after replacing the main bearing in the nacelle. Therefore, bearing replacement is very expensive, and the wind power generator in a stopped state may be left as it is without performing bearing replacement.

  The present invention has been made to solve the above-described problems. A main object of the present invention is to provide a bearing device, a mechanical device, and a bearing in which the occurrence of abnormality due to receiving a static load is suppressed and the bearing life is long.

  The bearing device of the present invention includes a housing and a bearing attached to the housing, and the bearing includes an outer ring in contact with the housing, and a part in a circumferential direction of the outer ring is when the bearing is stationary. It is a load area which receives a radial load in, and further comprises a moving part which can move the load area in the outer ring.

  According to the present invention, it is possible to provide a bearing device, a mechanical device, and a bearing in which occurrence of abnormality due to receiving a static load is suppressed and the bearing life is long.

It is sectional drawing for demonstrating the bearing apparatus which concerns on this Embodiment. It is sectional drawing seen from the arrow II-II in FIG. It is sectional drawing seen from the arrow III-III in FIG. In the bearing device according to the present embodiment, it is a diagram for explaining a modification of the outer ring. In the bearing device according to the present embodiment, it is a diagram for explaining another modification of the outer ring. It is sectional drawing for demonstrating the modification of the bearing apparatus which concerns on this Embodiment. It is sectional drawing seen from the arrow VII-VII in FIG. It is sectional drawing for demonstrating the other modification which concerns on this Embodiment. It is sectional drawing seen from arrow IX-IX in FIG. It is the elements on larger scale of the area | region X in FIG. It is sectional drawing which shows the axial direction seal | sticker part shown in FIG. It is the side view seen from the arrow XII in FIG. It is a side view which shows the circumferential direction seal part shown in FIG. It is sectional drawing seen from the arrow XIV-XIV in FIG. It is sectional drawing seen from the arrow XV-XV in FIG.

  Embodiments of the present invention will be described below with reference to the drawings. In the following drawings, the same or corresponding parts are denoted by the same reference numerals, and description thereof will not be repeated.

First, the outline of the embodiment of the present invention will be enumerated.
(1) In one embodiment, the bearing device 1 includes a housing 20 and a bearing 30 attached to the housing 20, and the bearing 30 includes an outer ring 32 in contact with the housing 20. Part of the bearing 30 is a load region that receives a radial load when the bearing 30 is stationary. The bearing device 1 further includes a moving unit 40 that can move the load region in the outer rings 32 and 72.

  Here, referring to FIG. 1 and FIG. 6, when the bearings are rolling bearings 30, the outer rings 32, 72 indicate the outer rings 32 having rolling surfaces that come into contact with a plurality of rolling elements 33. In the case of the sliding bearing 70, the outer ring 72 having a sliding surface with the rotating shaft (rolling shaft) 10 is indicated. In the outer rings 32 and 72, a load region that receives a radial load (hereinafter simply referred to as a static load) when the bearings 30 and 70 are stationary is formed in a part of a circumferential direction (hereinafter simply referred to as a circumferential direction) of the bearings 30 and 70. Therefore, the bearings 30 and 70 in this embodiment are so-called outer ring static load bearings in which a static load is applied to the outer rings 32 and 72.

  By moving the load areas in the outer rings 32 and 72 of the bearings 30 and 70 by the moving unit 40, a static load is continuously applied to a part of the specific area in the circumferential direction of the outer rings 32 and 72 (in other words, the load It is possible to avoid that the area is fixed at a specific position in the circumferential direction of the outer rings 32 and 72. As a result, the bearing device 1 having a long bearing life can be obtained. In addition, the movement of the load region in the inner ring 31 by the moving unit 40 may be performed so that a region that does not overlap with the load region at the time of previous use in which metal fatigue has progressed may be a new load region. A region that partially overlaps a region other than a portion (maximum surface pressure portion) that has received the largest static load in the load region at the time may be moved as a new load region.

  Further, the movement of the load region by the moving unit 40 may be performed, for example, before local metal fatigue progresses in the load region and an abnormality such as peeling occurs, or local metal fatigue occurs in the load region. It may be carried out after progress and confirmation of an abnormality such as peeling.

  In any case, one bearing device 1 is continuously used without performing replacement work, with the load area (at least the maximum surface pressure part) that does not overlap with the load area (at least the maximum surface pressure part) at the time of previous use where metal fatigue has progressed. Thus, the bearing device 1 having a long bearing life can be provided.

  (2) In another Example, the moving part 40 is provided in the outer ring | wheels 32 and 72 so that a load area can be moved to the circumferential direction.

  In this way, the load region can be moved over, for example, the entire circumference of the outer rings 32, 72. Therefore, the bearing device 1 until the load region is formed at least once in the entire circumferential region of the outer rings 32, 72. Can be used continuously. As a result, it is possible to provide the bearing device 1 having an extremely long bearing life compared to the conventional bearing device.

  (3) In another embodiment, outer ring grooves 34, 74 extending in the circumferential direction are formed on the contact surfaces 32A of the outer rings 32, 72 with the housing 20, and the insides of the outer ring grooves 34, 74 are The projecting member 22 projecting from the housing 20 is divided into a first space 34A and a second space 34B that are arranged in the circumferential direction independently of each other, and the moving unit 40 extends into the first space 34A so as to expand the first space 34A. The first medium is provided so as to be supplied.

  In this way, since the outer ring groove portions 34 and 74 are formed on surfaces other than the rolling surfaces of the outer rings 32 and 72, the moving portion 40 can move in the load region without hindering the rotation operation of the rolling bearing 30. It is. Furthermore, since the first space 34 </ b> A and the second space 34 </ b> B are separated by the protruding member 22, one end in the circumferential direction of the first space 34 </ b> A is fixed at the fixed end in the bearing device 1 by the protruding member 22 fixed to the housing 20. It is configured as. The other end of the first space 34 </ b> A is an end of an outer ring groove 34, 74 provided on a contact surface 32 </ b> A between the outer rings 32, 72 and the housing 20, and the outer rings 32, 72 are circumferential with respect to the housing 20. Since it is relatively movable, the bearing device 1 is configured to be movable in the circumferential direction. Therefore, the moving unit 40 moves the other end away from the protruding member 22 (the one end) in the circumferential direction by supplying the first medium (gas, liquid, etc.) to the first space 34A. it can. As a result, an area different from the load area at the time of previous use in which metal fatigue has progressed can be set as the load area. Therefore, one bearing device 1 can be continuously used without performing the replacement work of the bearing 30, and the bearing device 1 having a long bearing life can be provided.

  (4) In another embodiment, the housing 20 includes a flow passage (second through hole 24) that connects the second space 34 </ b> B and the outside of the housing 20.

  The first space 34A and the second space 34B are formed in regions other than the region where the protruding member 22 is disposed inside the outer ring groove portions 34 and 74, and the volume of the first space 34A and the volume of the second space 34B. Is constant regardless of the position of the load region in the outer rings 32 and 72 (relative positional relationship between the outer ring groove portions 34 and 74 and the protruding member 22 from a different viewpoint). Therefore, when the first medium is supplied to the first space 34A so as to expand the first space 34A by the moving unit 40, the first space 34A expands in the circumferential direction and the volume of the first space 34A increases and the second volume increases. The volume of the space 34B becomes small. Therefore, when the bearing device 1 includes the second through hole 24 that connects the second space 34B and the outside of the housing 20, the first medium (gas, liquid, etc.) filled in the second space 34B is released to the outside. be able to. As a result, when the volume of the second space 34B decreases, the first medium in the second space 34B is compressed, the pressure of the second space 34B is increased, and the movement of the load area by the moving unit 40 is prevented from being hindered. can do.

(5) In another embodiment, the moving unit 40 includes a hydraulic actuator.
The hydraulic actuator is an arbitrary device that converts energy input as hydraulic pressure into power of the outer rings 32 and 72, and may be, for example, a hydraulic pump or a hydraulic jack. Since the moving unit 40 includes a hydraulic actuator, the moving unit 40 moves (rotates) the large outer rings 32 and 72 even if the outer ring 32 and 72 has a large bearing device 1 having an outer diameter of, for example, 1 meter or more. It is possible to easily generate a large torque necessary for the generation. The moving unit 40 including the hydraulic actuator has high stability, controllability, and the like. Therefore, the moving unit 40 including the hydraulic actuator is suitable as the moving unit 40 of the bearing device 1 including the bearings 30 and 70 that are difficult to exchange due to the restrictions on the size and the installation location as described above.

  (6) In another embodiment, the bearing device 1 further includes a friction force reducing unit 50 that reduces the friction force between the outer rings 32 and 72 and the housing 20 on the contact surface 20A.

  For example, when the weights of the bearings 30 and 70 are loaded on a portion of the contact surface between the outer rings 32 and 72 and the housing 20 that is positioned below in the vertical direction, the movement of the load region by the moving unit 40 is prevented at that portion. A frictional force is generated. In such a case, by reducing the frictional force by the frictional force reducing unit 50, the movement of the load region by the moving unit 40 can be easily performed.

  (7) In another embodiment, the housing groove portion 25 is formed in a portion of the housing 20 where the outer ring 32 contacts, and the frictional force reduction portion 50 is provided in the housing groove portion 25 so as to be able to supply the second medium. It has been.

  In this way, since the outer rings 32 and 72 and the housing 20 are connected to each other through at least a part of these contact surfaces via the second medium (gas, liquid, etc.), the outer rings 32 and 72 and the housing 20 are connected to each other. The frictional force can be reduced. As a result, the load area can be easily moved by the moving unit 40. The first medium supplied to the first space 34A by the moving unit 40 and the second medium supplied to the inside of the housing groove 25 by the frictional force reducing unit 50 are the same medium (gas, liquid, etc.). It may be a different medium (gas, liquid, etc.).

(8) A mechanical device in an embodiment includes the bearing device 1.
The bearing device 1 described above may be provided in any mechanical device, but is provided in, for example, a wind power generator, a tidal power generator, a large ship, a large truck, a large turbine, and the like. Since such a mechanical device includes the bearing device 1 having a long bearing life, it is possible to reduce the frequency of replacement work of the bearings 30 and 70 due to reaching the bearing life as compared with the conventional mechanical device. Further, in a mechanical device such as a wind turbine generator, since the replacement work of the bearings 30 and 70 is extremely expensive and difficult to perform, the life of the device depends on the bearing life, and the mechanical device itself is extended. be able to.

(9) The bearings 30 and 70 in an embodiment are provided in the bearing device 1.
The bearing device 1 described above includes the bearings 30 and 70 including the outer rings 32 and 72 in which a load region that receives a radial load when the bearings 30 and 70 are stationary is formed in a part of the circumferential direction. The bearings 30 and 70 may have any configuration as long as they are provided so as to be movable in the load region by the moving unit 40, and may be rolling bearings 30 or sliding bearings 70. Good. For example, the sliding bearing 70 including the bearing 70 in which the outer ring groove portions 34 and 74 are formed may be used. Such bearings 30 and 70 are provided in a conventional bearing device in which the load area is fixed at a predetermined position in the outer rings 32 and 72 because the load area can be moved by the moving unit 40. Longer life than bearings.

  Next, with reference to FIGS. 1-3, the bearing apparatus 1 which concerns on this Embodiment is demonstrated. The bearing device 1 includes a rotating shaft 10, a housing 20, and a rolling bearing 30.

  The rotating shaft 10 is a shaft that is rotatably provided in the bearing device 1. The housing 20 is a member provided in the bearing device 1 so as not to rotate.

  Although the rolling bearing 30 should just be provided with arbitrary structures, it is a self-aligning roller bearing, for example. Rolling bearing 30 includes an inner ring 31, an outer ring 32, and a plurality of rolling elements 33 (for example, spherical rollers). The inner ring 31 has a rolling surface in contact with the plurality of rolling elements 33 on its outer peripheral surface, and the outer ring 32 has a rolling surface in contact with the plurality of rolling elements 33 on its inner peripheral surface. ing.

  The inner ring 31 is fitted to the rotating shaft 10 on the inner side of the rolling surface, and the outer ring 32 is fitted to the housing 20 on the outer side of the rolling surface. The inner ring 31 and the rotating shaft 10 are provided so as to be integrally rotatable. The outer ring 32 and the housing 20 are arranged such that their relative positions do not change when the rolling bearing 30 is in operation, but are relatively movable in the circumferential direction during maintenance as described later. That is, the rolling bearing 30 is a so-called outer ring static load rolling bearing.

  An outer ring groove 34 extending in the circumferential direction is formed on the contact surface 32 </ b> A of the outer ring 32 with the housing 20. As long as the outer ring groove portion 34 extends in the circumferential direction and has an end portion in the circumferential direction (not connected to the entire circumference), the outer ring groove portion 34 is formed in any region in the circumferential direction over an arbitrary length. Just do it. Preferably, the outer ring groove 34 is formed over most of the contact surface 32 </ b> A between the outer ring 32 and the housing 20. In this way, since the outer ring groove 34 is widely formed in the circumferential direction, the movable range of the outer ring 32 in the circumferential direction can be increased. More preferably, a plurality of outer ring groove portions 34 are formed in the circumferential direction, and the plurality of outer ring groove portions 34 are arranged so as to face each other with the rotation shaft 10 interposed therebetween. In this way, even when the first medium is supplied to the outer ring groove part 34 (the first space 34A formed inside) by the moving part 40, the force exerted by the first medium on the outer ring 32 in the radial direction. And the force exerted by the first medium on the outer ring 32 in the circumferential direction can be effectively utilized.

  At least one outer ring groove 34 may be formed in the axial direction of one rolling bearing 30 (hereinafter simply referred to as the axial direction), and a plurality of outer ring grooves 34 may be formed.

  The outer ring groove portion 34 may be formed at an arbitrary position on the contact surface 32A of the outer ring groove portion 34 with the housing 20 in the axial direction, but is formed at the center in the axial direction, for example.

  One end portion in the circumferential direction of the outer ring groove portion 34 constitutes an end portion other than a fixed end (connection end surface between the protruding member 22 and the first space 34A) in the circumferential direction of the first space 34A described later, and the other side. The end portion constitutes an end portion other than a fixed end (a connecting end surface between the protruding member 22 and the second space 34B) in the circumferential direction of the second space 34B described later.

  The inside of the outer ring groove portion 34 is divided into a first space 34A and a second space 34B that are independent from each other and are arranged in the circumferential direction by the protruding member 22 protruding from the housing 20. That is, the first space 34A is formed so as to extend in the circumferential direction, and one end portion in the circumferential direction is a connection end surface between the protruding member 22 and the first space 34A, and the other end portion is an outer ring groove portion. 34 is one end in the circumferential direction. The second space 34B is formed so as to extend in the circumferential direction, and one end in the circumferential direction is a connection end surface between the protruding member 22 and the second space 34B, and the other end is an outer ring groove portion. 34 is the other end in the circumferential direction.

  The angle formed between both end portions in the circumferential direction of the first space 34 </ b> A when the first space 34 </ b> A is most expanded and the axis of the bearing 30 corresponds to an angle at which the moving unit 40 can move the outer ring 32 with respect to the housing 20. For example, it can be set to about 160 degrees.

  The protruding member 22 protrudes toward the rotating shaft 10 from the contact surface 32A between the outer ring 32 and the housing 20. Although the protrusion member 22 should just be provided with arbitrary structures, it is provided so that the outer ring groove part 34 can be fitted in the circumferential direction of the rolling bearing 30, for example. At this time, the region in which the protruding member 22 and the outer ring groove 34 can be fitted is formed wide in the circumferential direction. In other words, the cross-sectional shape perpendicular to the circumferential direction of the outer ring groove portion 34 is equally provided in the circumferential direction, and the cross-sectional shape perpendicular to the circumferential direction of the outer ring groove portion 34 and the cross-sectional shape perpendicular to the circumferential direction of the protruding member 22 are Equally provided. In this way, the projecting member 22 and the outer ring can also be used when the first medium 34 (for example, oil having a high pressure) is supplied to the first space 34A by the moving unit 40 described later to expand the first space 34A in the circumferential direction. The outer ring 32 can be moved relative to the housing 20 while maintaining the fitting state with the groove 34.

  The protruding member 22 has a first through hole 23 for connecting the first space 34A and the outside, and a second through hole 24 for connecting the second space 34B and the outside. That is, the opening end of the first through hole 23 inside the outer ring groove portion 34 and the opening end of the second through hole 24 inside the outer ring groove portion 34 are formed in opposite directions in the circumferential direction. The first through hole 23 and the second through hole 24 are independent of each other.

  The moving part 40 is connected to the first space 34 </ b> A via the first through hole 23 in the protruding member 22. The second space 34 </ b> B is connected to the outside of the housing 20 through the second through hole 24. The moving unit 40 is provided so that the first medium can be supplied to the first space 34A via the protruding member 22 so as to expand the first space 34A. The moving unit 40 may have an arbitrary configuration as long as it can move the load region in the outer ring 32, and includes, for example, a hydraulic actuator. That is, the first medium can be arbitrarily selected from gas and liquid, but is, for example, high pressure oil.

  Next, the effect of the bearing device 1 according to the present embodiment will be described. In the bearing device 1, an outer ring groove portion 34 extending in the circumferential direction is formed on the contact surface 32 </ b> A of the outer ring 32 with the housing 20, and the inside of the outer ring groove portion 34 is independent of each other by the protruding members 22 protruding from the housing. The first space 34A and the second space 34B are arranged in the circumferential direction, and the moving unit 40 supplies the first medium to the first space 34A via the protruding member 22 so as to expand the first space 34A. It is provided as possible.

  Therefore, since the outer ring groove 34 is formed on a surface other than the rolling surface of the outer ring 32, the moving unit 40 can move in the load region without hindering the rotation operation of the rolling bearing 30. Furthermore, since the first space 34 </ b> A and the second space 34 </ b> B are separated by the protruding member 22, one end in the circumferential direction of the first space 34 </ b> A is fixed at the fixed end in the bearing device 1 by the protruding member 22 fixed to the housing 20. It is configured as. The other end of the first space 34A is an end portion of the outer ring groove portion 34 provided on the contact surface with the housing 20 in the outer ring 32, and the outer ring 32 moves relative to the housing in the circumferential direction. The bearing device 1 is configured to be movable in the circumferential direction. Therefore, the moving unit 40 moves the other end away from the protruding member 22 (the one end) in the circumferential direction by supplying the first medium (gas, liquid, etc.) to the first space 34A. it can. As a result, for example, a region that does not overlap with a load region (at least the maximum surface pressure portion) at the time of use where metal fatigue has progressed can be set as a load region, and one bearing device 1 can be continued without replacement work. Can be used.

  In addition, since the moving unit 40 includes a through hole that connects the second space 34B and the outside, the first space 34A expands in the circumferential direction and the volume of the first space 34A increases, so that the volume of the second space 34B increases. Even if the volume is reduced, the first medium (gas, liquid, etc.) filled in the second space 34B can be released to the outside. As a result, when the volume of the second space 34B decreases, the first medium in the second space 34B is compressed, the pressure of the second space 34B is increased, and the movement of the load area by the moving unit 40 is prevented from being hindered. can do.

  Moreover, since the moving part 40 includes a hydraulic actuator, for example, even when the large outer ring 32 having an outer diameter of 1 meter or more is slightly moved (rotated), a sufficiently large torque can be easily generated. it can. In addition, since the moving unit 40 has high stability, controllability, and the like, it is possible to suppress the bearing life of the bearing device 1 from being limited by the moving unit 40.

  The bearing device 1 according to the present embodiment can be applied to various mechanical devices including the bearing 30, but is advantageously applied particularly to a mechanical device in which the bearing 30 cannot be easily replaced. As shown in FIG. 1, the bearing device 1 may be provided in, for example, a wind power generator 100, and the rotary shaft 10 may be configured as the central axis of the swirl blade 60.

  As described above, the bearing 30 provided in the bearing device 1 according to the present embodiment is formed such that the outer ring groove 34 extends in the circumferential direction on the contact surface 32A of the outer ring 32 with the housing 20.

  Referring to FIG. 1, bearing device 1 according to the present embodiment may further include a friction force reducing unit 50 that reduces the friction force on contact surface 20 </ b> A between outer ring 32 and housing 20.

  In the housing 20, a housing groove portion 25 is formed on the contact surface 20 </ b> A with the outer ring 32, and the frictional force reducing portion 50 is provided in the housing groove portion 25 so that the second medium can be supplied.

  The housing groove 25 is a region where frictional force is generated between the outer ring 32 and the housing 20 when the outer ring 32 and the housing 20 are relatively moved by the moving unit 40 (for example, a region positioned vertically below the bearing 30). ). The housing groove portion 25 may be formed to extend in the circumferential direction of the bearing 30, for example. The housing groove portion 25 only needs to be formed in an arbitrary number of one or more in one bearing 30, but a plurality of housing groove portions 25 are formed in a region that does not overlap with the outer ring groove portion 34, for example.

  In this way, the outer ring 32 and the housing 20 are connected via the second medium (gas, liquid, etc.) in at least a part of the contact surface 20A, so that the frictional force between the outer ring 32 and the housing 20 is reduced. Can be reduced. As a result, the load area can be easily moved by the moving unit 40.

  In the present embodiment, the outer ring groove portion 34 is formed at the center in the axial direction. However, referring to FIGS. 4 and 5, the outer ring groove portion 34 is provided in a portion where the outer ring 32 is relatively thick in the radial direction. It may be done. For example, when the outer ring 32 is provided with an end portion in the axial direction thicker than the center portion, the outer ring groove portion 34 may be formed in the vicinity of one end or the vicinity of both ends in the axial direction of the outer ring 32.

  By forming the outer ring groove portion 34 and the housing groove portion 25, the deformation amount of the outer ring 32 when a radial load is applied is slightly increased. In the case where such a slight increase in the deformation amount cannot be allowed, the increase in the deformation amount can be suppressed by forming the outer ring groove portion 34 in the thick portion of the outer ring 32 as shown in FIGS. .

  Further, the outer ring groove portion 34 may be formed on any surface other than the rolling surface in the outer ring 32, and may be provided, for example, on the outer ring width surface (end surface in the axial direction). Even if it does in this way, the increase in the deformation | transformation amount of the outer ring | wheel 32 when a radial load is loaded can be suppressed, and the load area | region in the outer ring | wheel 32 can be moved by the moving part 40. FIG.

  Moreover, although the bearing apparatus 1 which concerns on this Embodiment is provided with the rolling bearing 30, you may provide the sliding bearing 70 with reference to FIG. 6 and FIG. In this case, the movement part 40 should just be provided so that the load area | region in the outer ring | wheel 72 can be moved. For example, what is necessary is just to provide the outer ring | wheel 72 which carries out sliding contact with the rotating shaft (rolling shaft) 10 as a structure similar to the outer ring | wheel 32 (refer FIG. 1) in this Embodiment. That is, in the outer ring 72, an outer ring groove portion 74 extending in the circumferential direction is formed on the contact surface 72 </ b> A with the housing 20, and the inside of the outer ring groove portion 74 is surrounded by the protruding members 22 protruding from the housing 20. It is divided into a first space 74A and a second space 74B arranged in the direction, and the moving unit 40 can supply the first medium to the first space 74A via the protruding member 22 so as to expand the first space 74A. It may be provided. Even if it does in this way, there can exist an effect similar to bearing device 1, machine device 100, and bearing 30 concerning this embodiment.

<Modification>
8-10, 11 and 12, the bearing device 1 according to the present embodiment further includes an axial seal member 35 that closes the first space 34A in the axial direction. preferable.

  Referring to FIGS. 9, 10, and 13 to 15, the bearing device 1 preferably further includes circumferential seal members 36 and 37 that close the first space 34 </ b> A in the circumferential direction.

  The axial seal member 35 is provided so as to cover at least a connection portion between a contact surface between the housing 20 and the outer ring 32 and an inner peripheral surface extending in a direction (for example, radial direction) intersecting the axial direction in the outer ring groove portion 34. ing. The axial seal member 35 includes, for example, seal portions 351 and 352 and a connection portion 353 that connects between the seal portions 351 and 352. The material constituting the axial seal member 35 may be any material having elasticity and resistance to the first medium. For example, nitrile rubber, hydrogenated nitrile rubber, acrylic rubber, silicone rubber, fluorine Rubber such as rubber, ethylene propylene rubber, styrene butadiene rubber, natural rubber, fluorine resin, polyimide resin, polyamide imide resin, polyether ether ketone resin, polyphenylene sulfide resin, polyamide resin, polyethylene resin, polyacetal resin, polyethylene terephthalate resin, polyurethane Examples thereof include resins such as resins, epoxy resins, unsaturated polyester resins, phenol resins, and ABS resins, materials obtained by reinforcing the above materials with fibers, and materials laminated with different materials.

  The seal portions 351 and 352 are provided such that the outer peripheral end and the inner peripheral end in the radial direction of the axial seal member 35 can be configured. The seal portions 351 and 352 include an outer peripheral end E1 that is in surface contact or line contact with the housing 20 in the radial direction, and an outer ring 32 (at least part of an inner peripheral surface that extends along the axial direction and the circumferential direction of the outer ring groove portion 34). It has an inner peripheral end E2 in surface contact or line contact, and a side end E3 in surface contact or line contact with the inner peripheral surface of the outer ring groove 34. The seal portions 351 and 352 are opposed to each other across the first space 34A and the second space 34B in the axial direction. In other words, the side end located on the opposite side of the side end E3 in the seal portions 351 and 352 faces the first space 34A and the second space 34B.

  The connecting portion 353 is provided so as to connect, for example, the inner peripheral ends E2 of the seal portions 351 and 352, and has an inner peripheral end E2 that is continuous with the inner peripheral ends E2 of the seal portions 351 and 352. The outer peripheral surface located on the opposite side of the inner peripheral surface E2 in the connection portion 353 faces the first space 34A and the second space 34B. The inner peripheral surface E2 of the axial seal member 35 may be provided so as to be in surface contact with the entire inner peripheral surface extending along the axial direction in the outer ring groove portion 34.

  A portion of the axial seal member 35 exposed inside the outer ring groove portion 34 (a side end located on the opposite side of the side end E3 in the seal portions 351 and 352 and a side opposite to the inner peripheral surface E2 in the connection portion 353) The outer peripheral edge) is in line contact or surface contact with the protruding member 22 and the circumferential seal members 36 and 37, and is provided so as to be slidable at least with the protruding member 22 and the circumferential seal member 36. The axial seal member 35 may be provided so as to be slidable with the circumferential seal member 37.

  One end and the other end of the axial seal member 35 in the circumferential direction are respectively connected to one end and the other end of the outer ring groove portion 34 in the circumferential direction. One end of the axial seal member 35 on the side where the first space 34A is formed in the circumferential direction is also connected to a circumferential seal member 37 described later. The axial seal member 35 is preferably slidably connected to the circumferential seal member 36.

  When a plurality of outer ring groove portions 34 are formed in the bearing device 1, the axial seal member 35 is preferably provided in each outer ring groove portion 34 as described above. The two axial seal members 35 shown in FIGS. 8 to 10, 11, and 12 are disposed in the two outer ring groove portions 34, respectively, and seal the first space 34 </ b> A in the outer ring groove portion 34 in the axial direction. ing.

  As described above, if the axial seal member 35 is provided so as to cover the connection portion between the first space 34A and the inner peripheral surface of the housing 20 and the outer ring 32, the first medium supplied to the first space 34A is stored. Leakage from the connection part to the outside can be suppressed. Therefore, the moving part 40 can move the other end of the first space 34 </ b> A with a smaller amount of the first medium than in the case where the bearing device does not include the axial seal member. As a result, the bearing device 1 including the axial seal member 35 can realize a longer bearing life more efficiently than a bearing device not including the axial seal member 35.

  The circumferential seal member 36 and the circumferential seal member 37 are provided so as to sandwich the first space 34A in the circumferential direction. The circumferential seal member 36 is provided so as to cover at least a connection portion between the contact surface of the housing 20 and the protruding member 22 that partitions the first space 34A, the first space 34A, and the second space 34B. The circumferential seal member 36 has one end E4 in the circumferential direction facing the first space 34A and the other end E5 in the circumferential direction connected to the protruding member 22. As described above, the circumferential seal member 36 is slidably connected to the axial seal member 35. The material constituting the circumferential seal members 36 and 37 may be any material having elasticity and resistance to the first medium. For example, nitrile rubber, hydrogenated nitrile rubber, acrylic rubber, silicone rubber , Rubbers such as fluorine rubber, ethylene propylene rubber, styrene butadiene rubber, natural rubber, fluorine resin, polyimide resin, polyamideimide resin, polyetheretherketone resin, polyphenylene sulfide resin, polyamide resin, polyethylene resin, polyacetal resin, polyethylene terephthalate resin Examples thereof include resins such as polyurethane resins, epoxy resins, unsaturated polyester resins, phenol resins and ABS resins, or materials obtained by fiber-reinforced or laminated with different materials.

  The circumferential seal member 37 is provided so as to cover at least a connection portion between the contact surface between the housing 20 and the outer ring 32 and the inner circumferential surface extending along the radial direction in the outer ring groove portion 34. One end E4 in the circumferential direction of the circumferential seal member 37 faces the first space 34A, and faces the one end E4 of the circumferential seal member 36 with the first space 34A interposed therebetween. The other end E5 in the circumferential direction of the circumferential seal member 37 is connected to an end in the circumferential direction of the outer ring groove 34, and is fixed to the end, for example. The circumferential seal member 37 may be fixed to the axial seal member 35.

  For example, one end E4 of the circumferential seal members 36 and 37 is provided wider than the other end E5. The one end E4 is formed with a recess 38 that is recessed toward the other end E5. As described above, the circumferential seal members 36 and 37 are arranged so that one end E4 thereof faces the first space 34A. At this time, the portion located on the outer peripheral side in the radial direction at the one end E4 of the circumferential seal members 36 and 37 is in line contact or surface contact with the housing 20, and the portion located on the inner peripheral side is the axial seal member 35. Line contact or surface contact with Further, portions of the circumferential seal members 36 and 37 located on one and the other sides in the axial direction at the one end E4 are in line contact or surface contact with the axial seal member 35.

  The concave portions 38 of the circumferential seal members 36 and 37 constitute a part of the first space 34 </ b> A, and the first medium is also supplied into the concave portions 38. Thus, the circumferential seal members 36 and 37 are pressed against the housing 20 or the axial seal member 35 by the first medium supplied into the recess 38.

  As described above, if the circumferential seal members 36 and 37 are provided so as to cover the connection portion between the first space 34A and the inner peripheral surface of the housing 20 and the outer ring 32 and the connection portion between the housing 20 and the protruding member 22. The first medium supplied to the first space 34A can be prevented from leaking to the connection portion. Therefore, the moving part 40 can move the other end of the first space 34 </ b> A with a smaller amount of the first medium than in the case where the bearing device does not include the axial seal member. As a result, the bearing device 1 including the axial seal member 35 can realize a longer bearing life more efficiently than a bearing device not including the axial seal member 35.

  Further, since the recess 38 is formed at one end E4 of the circumferential seal members 36 and 37, the circumferential seal members 36 and 37 are pressed from the inside of the recess 38 by the first medium supplied to the first space 34A. Will be. Therefore, the portion in contact with the housing 20 and the axial seal member 35 at one end E4 of the circumferential seal members 36 and 37 is stronger than the case where the recess 38 is not formed. 35 can be contacted.

  8 to 10 show an example in which the axial seal member 35 and the circumferential seal members 36 and 37 are applied to the bearing device 1 including the rolling bearing 30. However, the axial seal member 35 and the circumferential direction described above are illustrated. The seal members 36 and 37 can be similarly applied to the bearing device 1 including the sliding bearing 70 shown in FIGS. 6 and 7.

  Although the embodiment of the present invention has been described as above, the embodiment disclosed this time should be considered as illustrative in all points and not restrictive. The scope of the present invention is defined by the terms of the claims, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.

  The present invention is particularly advantageously applied to a bearing device, a mechanical device, and a bearing including a bearing that is difficult to exchange.

  DESCRIPTION OF SYMBOLS 1 Bearing apparatus, 10 Rotating shaft, 20 Housing, 22 Protruding member, 23 1st through-hole, 24 2nd through-hole, 25 Housing groove part, 30, 70 Bearing, 31 Inner ring, 32, 72 Outer ring, 33 Rolling body, 34, 74 outer ring groove part, 34A, 74A first space, 34B, 74B second space, 40 moving part, 50 frictional force reducing part, 100 mechanical device.

Claims (11)

A housing;
A bearing attached to the housing,
The bearing includes an outer ring contacting the housing;
A portion of the outer ring in the circumferential direction is a load region that receives a radial load when the bearing is stationary,
The bearing device further includes a moving part that can move the load region in the outer ring.   The bearing device according to claim 1, wherein the moving unit is provided in the outer ring so as to be movable in the circumferential direction in the load region. An outer ring groove portion extending in the circumferential direction is formed on a contact surface with the housing in the outer ring,
The inside of the outer ring groove is divided into a first space and a second space that are independent of each other by a protruding member that protrudes from the housing and is arranged in the circumferential direction.
The bearing device according to claim 2, wherein the moving unit is provided to be able to supply the first medium to the first space so as to expand the first space.   The bearing device according to claim 3, further comprising an axial seal member connected to the outer ring and the housing in the outer ring groove portion and closing the first space in the axial direction of the bearing.   The bearing device according to claim 3, further comprising a circumferential seal member that is connected to the outer ring and the housing in the outer ring groove portion and closes the first space in a circumferential direction of the bearing.   The bearing device according to any one of claims 3 to 5, wherein the housing includes a flow passage that connects the second space and the outside of the housing.   The bearing device according to claim 1, wherein the moving unit includes a hydraulic actuator.   The bearing device according to any one of claims 3 to 5, further comprising a friction force reducing unit that reduces a friction force between the outer ring and the housing on the contact surface. A housing groove is formed in a portion of the housing that contacts the outer ring,
The bearing device according to claim 8, wherein the frictional force reduction unit is provided so as to be able to supply the second medium inside the housing groove portion.   A mechanical apparatus provided with the bearing apparatus of any one of Claims 1-9.   The bearing with which the bearing apparatus of any one of Claims 1-9 is equipped.

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