JP2017190866A - Rolling bearing unit - Google Patents

Abstract

PROBLEM TO BE SOLVED: To enable a seal member to be firmly fixed to an outer ring, the seal member configured to close a lateral opening of a bearing space of a rolling bearing.SOLUTION: A rolling bearing unit includes: an outer ring 1 fixed into a housing 11; an inner ring 2 opposite to the outer ring 1; a toric seal member 40 covering a lateral opening D of a bearing space between the outer ring 1 and the inner ring 2; an oil passage 12 for lubricant arranged along an axial direction between an inner diameter surface of the housing 11 and an outer diameter surface of the outer ring 1; and a connection piece 80 inserted into the oil passage 12 and fixing the seal member 40 to the outer ring 1. The seal member 40 comprises a toric connection body formed by connecting a plurality of split seal members 40' split along a circumferential direction with the connection pieces 80. The connection piece 80 and the split seal member 40' include folding prevention means of regulating bending of connection parts between the split seal members 40' adjacent in the circumferential direction.SELECTED DRAWING: Figure 1

Description

  The present invention relates to an oil-lubricated rolling bearing, and more particularly to a rolling bearing unit having a function of capturing foreign matter contained in lubricating oil.

  Rolling bearings are incorporated in movable parts of transportation equipment, industrial machinery, and other various equipment. In such a device, there is an operation mechanism portion that requires lubrication in addition to the oil-lubricated rolling bearing, and the operation mechanism portion and the rolling bearing have a structure that is lubricated with a common oil. There is something. As an operation mechanism part, the meshing part of gears, the sliding contact part of members, etc. are mentioned, for example.

  For example, an oil pump or the like has a rolling bearing and an operating mechanism part inside the device. In particular, the oil pump has a function of feeding the internal lubricating oil toward another operating mechanism portion outside the device including the rolling bearing and the operating mechanism portion.

  Incidentally, foreign matter such as wear powder (iron powder or the like) may be generated from the bearing space of the rolling bearing. If the foreign matter enters the operating mechanism part in the middle of the lubricating oil circulation path, the durability of the device may be reduced due to the biting of the foreign matter. In some cases, it may lead to malfunction / failure / damage of the equipment.

  Therefore, for example, in Patent Document 1, when a foreign matter made of iron powder or the like is mixed in the lubricating oil flowing in the circulation path, the foreign matter is attracted to a magnet provided in the sensor, and the attracted foreign matter is accumulated. Thus, there is disclosed a method for detecting iron powder contamination of lubricating oil that issues an alarm when a metal casing and a magnet are electrically connected (see, for example, Patent Document 1).

  Patent Document 2 discloses a technique in which a filter for capturing foreign matter is provided on a seal ring that closes an end of a bearing space located between inner and outer rings of a rolling bearing.

JP 7-280180 A JP 2012-102767 A

  As described above, it is not preferable for foreign matter such as wear powder (iron powder or the like) generated from the rolling bearing to enter the operating mechanism portion in the middle of the lubricating oil circulation path. In particular, in a rolling bearing unit for an oil pump, a large peeling piece generated from the bearing is caused by an operating mechanism portion of the oil pump itself or other operating mechanism portions in a circulation path of lubricating oil sent out by the oil pump. It may cause malfunction, failure or damage to the parts. For this reason, by installing an annular seal member with a filter as shown in Patent Document 2, it is necessary to prevent foreign matter from flowing out of the rolling bearing into the operating mechanism.

  By the way, when the seal member is fixed to the outer ring side, the seal member needs to be firmly fixed to the outer ring. If the seal member is not firmly fixed to the outer ring, a gap is formed between the seal member and the outer ring, leading to a situation where foreign matter flows out of the bearing space to the outside of the bearing space.

  Then, the subject of this invention is enabling it to fix firmly the sealing member which closes the side opening of the bearing space of a rolling bearing with respect to an outer ring | wheel.

  In order to solve the above problems, the present invention provides an outer ring fixed in a housing, an inner ring facing the outer ring, a rolling element disposed in a bearing space between the outer ring and the inner ring, An annular seal member that is attached to one end of the outer ring in the axial direction and covers a side opening of the bearing space, and is disposed along the axial direction between the inner diameter surface of the housing and the outer diameter surface of the outer ring. An oil passage for lubricating oil; and a connecting piece that enters the oil passage and fixes the seal member to the outer ring. The seal member includes a plurality of divided seal members that are divided along a circumferential direction. A rolling bearing unit is provided that is connected by a piece to form an annular coupling body, and the coupling piece and the divided seal member are provided with a bending preventing means for restricting bending of a connection portion between the divided seal members adjacent in the circumferential direction. Adopted.

  The engaging protrusion provided on one of the connecting piece and the split seal member enters the engaging hole provided on the other, so that the end portions of the split seal members adjacent to each other in the circumferential direction are in the circumferential direction. It is possible to adopt a configuration that is slidably connected to each other.

  Here, it is possible to adopt a configuration in which the locking projection is provided in the connecting piece and the locking hole is provided in the divided seal member.

  The connecting piece includes a base portion that abuts against an end portion of the divided seal member adjacent in the circumferential direction, and a pair of support portions extending from the base portion to both sides in the circumferential direction, and the locking convex portion is provided on the support portion. The provided structure can be adopted.

  In each of these aspects, the break prevention means includes a plurality of the locking projections between the at least one of the divided seal members adjacent to each other in the circumferential direction and the connecting piece. It is possible to adopt a configuration in which the holes are connected and connected.

  Further, in each of these aspects, the break prevention means includes a non-circular locking projection between at least one of the divided seal members adjacent to the circumferential direction and the connecting piece. It is possible to adopt a configuration that is configured to enter and be connected to the locking hole having the same shape.

  In the present invention, when a plurality of divided seal members divided along the circumferential direction are connected by a coupling piece to form a sealing member made of an annular coupling body, the coupling piece and the divided sealing member are adjacent to each other in the circumferential direction. Since the structure is provided with a break prevention means for restricting the bending of the connecting portion between the matching divided seal members, the seal member that closes the side opening of the bearing space of the rolling bearing can be firmly fixed to the outer ring.

1 shows a first embodiment of the present invention, in which (a) is a side view of a bearing unit including a plurality of rolling bearings, and (b) is a longitudinal sectional view. (A) is a principal part top view of the rolling bearing provided with the sealing member, (b) is the perspective view. (A) is a side view of a rolling bearing provided with a seal member, and (b) is a front view. Exploded perspective view of seal member The coupling piece which connects division | segmentation sealing members is shown, (a) is a top view, (b) is a front view of (a), (c) is a right view of (a). (A) (b) which shows the connection part of division | segmentation sealing members is an enlarged view of the principal part, (c) is sectional drawing. The modification of a connection piece is shown, (a) (b) is the top view and sectional drawing which show the state which enlarged the diameter, (c) (d) is the top view and sectional drawing which shows the state which reduced the diameter (A) (b) is a top view which shows a modification, respectively, (c) (d) is a top view and sectional drawing which show the further modification. (A) is sectional drawing which shows the detail of a connection piece vicinity, (b) is a principal part expanded perspective view of a sealing member, (c) is principal part sectional drawing of (b). Explanatory drawing which shows the load which acts on a seal ring, and the deformation | transformation of the member with respect to it Exploded perspective view showing a modification of the connecting piece (A) (b) is sectional drawing which shows the detail of each connection piece vicinity, (c) is an enlarged view of (b), (d) is a perspective view which shows the further modification of a connection piece. The second embodiment of the present invention is shown, (a) is a side view of a bearing unit provided with a plurality of rolling bearings, (b) is a longitudinal sectional view. (A) is a principal part top view of the rolling bearing provided with the sealing member, (b) is the perspective view. (A) is a side view of a rolling bearing provided with a seal member, and (b) is a front view. The coupling piece which connects division | segmentation sealing members is shown, (a) is a top view, (b) is a front view of (a), (c) is a right view of (a). (A) (b) is a principal part enlarged view which shows the connection part of division | segmentation seal members. Exploded perspective view showing a modification of the connecting piece (A) (b) is sectional drawing which shows the detail of each connection piece vicinity, (c) is an enlarged view of (b), (d) is a perspective view which shows the further modification of a connection piece. (A) (b) is sectional drawing which shows the comparative example of a connection piece

  Embodiments of the present invention will be described with reference to the drawings. 1 to 12 show a first embodiment of the present invention. This embodiment is an oil pump device 10 including a bearing unit 20 to which a seal member 40 is attached.

  The oil pump device 10 includes a bearing unit 20 having a plurality of rolling bearings inside the device, and an operating mechanism 30 of the oil pump 60.

  The bearing unit 20 includes three rolling bearings 21, 22, and 23 that are oil-lubricated in parallel inside the housing 11. By these rolling bearings 21, 22, and 23, the shaft member 32 that communicates with the operating mechanism portion 30 of the oil pump 60 is supported by the fixed housing 11 so as to be rotatable about the axis.

  In each of the rolling bearings 21, 22, and 23, a rolling element 3 is incorporated between the raceway surfaces 1 a and 2 a of the outer raceway ring 1 and the inner raceway ring 2. The rolling element 3 is held in the circumferential direction by a cage 4. Hereinafter, the outer race 1 is referred to as an outer race 1 and the inner race 2 is referred to as an inner race 2.

  The outer ring 1 is press-fitted into the inner diameter surface of the housing 11 and fixed to the housing 11 so as not to rotate relative to the housing 11. The inner ring 2 is press-fitted into the outer periphery of the shaft member 32 and is fixed to the shaft member 32 so as not to rotate relative to the shaft member 32.

  In this embodiment, as the rolling bearings 21, 22, and 23, tapered roller bearings using tapered rollers are employed as the rolling elements 3, but rolling bearings other than tapered roller bearings may be employed. The parallel number of the rolling bearings 21, 22, and 23 can be freely set according to the specifications of the apparatus.

  The operating mechanism 30 of the oil pump 60 includes a pump rotor (not shown) that sends lubricating oil to the circulation path by rotating relative to each other in the pump casing. The pump rotor is connected to the connection member 31 provided at the end of the shaft member 32, and is thus rotatable around the shaft of the shaft member 32. The driving force to the rotor is input by a separate route from a driving source (not shown).

  As shown in FIG. 1, two rolling bearings 21, 22 near one side of the rolling mechanism 21, 22, 23 in parallel, that is, closer to the operating mechanism portion 30, have smaller diameter side end surfaces of the tapered rollers in the axial direction. Are arranged so as to be on the same side, that is, on the opposite side of the operating mechanism portion 30.

  The rolling bearings 23, 22, 23 arranged in parallel to each other in the axial direction, that is, the rolling bearing 23 farthest from the operating mechanism portion 30 is arranged so that the end surface on the small diameter side of the tapered roller is on the operating mechanism portion 30 side. ing. That is, the rolling bearings 21 and 22 and the rolling bearing 23 are disposed so that the small diameter side end surfaces of the tapered rollers are back to back. For this reason, the raceway surface 2a of the inner raceway ring 2 and the raceway surface 1a of the outer raceway ring 1 are two on one side of the three rows of rolling bearings 21, 22, 23 from the one side in the axial direction to the other side. The other side is provided so that the mutual distance increases from one side in the axial direction to the other side.

  As shown in FIG. 1, spacers 5, 6, 7 are arranged between the rolling bearings 21, 22, 23 adjacent in the axial direction.

  Between the two rolling bearings 21, 22 on the one side in the axial direction of the rolling bearings 21, 22, 23 that are arranged in parallel, a spacer 5 that is in contact with the end faces of the inner rings 2, 2 on both sides is provided on the inner diameter side. On the side, a spacer 6 is disposed that contacts the end faces of the outer rings 1 and 1 on both sides.

  In addition, between the two rolling bearings 22, 23 on the other axial side of the rolling bearings 21, 22, 23 arranged in parallel, a spacer that contacts the end surfaces of the inner rings 2, 2 on both sides is provided on the inner diameter side. A spacer 7 is disposed on the radial side so as to contact the end surfaces of the outer rings 1 and 1 on both sides. In FIG. 1, the inner diameter side spacer between the rolling bearings 22 and 23 is not shown, but along the circumferential direction of the rolling bearings 22 and 23, other than the opening on the outer diameter side of the lubricating oil circulation path 13 b. A spacer is arranged in the portion.

  Both ends of the rolling bearings 21, 22, and 23 that are arranged in parallel are on the one side in the axial direction by the end face of the flange-shaped connection member 31 provided at the end of the shaft member 32, and on the other side in the axial direction, The end face is fixed so as not to move in the axial direction with respect to the shaft member 32. By preliminarily fixing the connecting member 31 and the pressing member 8, a preload is applied to each rolling bearing.

  The shaft member 32 supported by the housing 11 by the rolling bearings 21, 22, and 23 is connected to an operating mechanism unit 30 that is a rotating member in the oil pump 60 corresponding to a pump body for sending out oil. The oil pump 60 has a function of sending the internal lubricating oil toward the other operating mechanism portion 70 located outside by driving. The delivered lubricating oil flows along the lubricating oil path to lubricate the operating mechanism 70 of each part, and then returns to the oil pump 60.

  In the oil pump 60, the operating mechanism 30 in the pump body and the bearing unit 20 that supports the shaft member 32 that communicates with the operating mechanism 30 are lubricated with a common lubricating oil. ing. The operating mechanism 30 on the oil pump 60 side and the bearing space on the bearing unit 20 side are the side opening D of the bearing space on one axial end side of the rolling bearing 21 on the one axial side, and the circulation path 12 of the lubricating oil. , 13 communicate with each other. The lubricating oil is also sent out to the operating mechanism 70 outside the pump.

  In this embodiment, the circulation path 13 includes an axial lubrication path 13a provided along the axial direction so as to be concentric with the axis of the shaft member 32 from the oil pump side, and an end of the lubrication path 13a. A radial lubrication path 13b that extends radially outward and opens on the outer peripheral surface of the shaft member 32 is provided. Since the radial lubrication path 13b opens to the annular space C sandwiched between the rolling bearings 22 and 23, the circulation path 13 passes through the annular space C on one side in the axial direction (left side in the figure). Is connected to the bearing spaces of the rolling bearings 21 and 22, and the other axial side (the right side in the figure) is connected to the bearing space of the rolling bearing 23.

  The lubricating oil that has passed through the bearing space of the rolling bearing 23 through the annular space C passes through the opening of the bearing space on the other end side in the axial direction of the rolling bearing 23 and the housing end provided on the other end side in the axial direction of the rolling bearing 23. Enter the subspace B. Thereafter, the oil returns to the operating mechanism 30 side of the oil pump 60 by the lubricating oil circulation path 12 formed in the portion near the outer diameter in the housing 11.

  The circulation path 12 includes a radial lubrication path 12b extending radially outward from the housing end space B, and an axial lubrication path 12a provided along the axial center direction of the shaft member 32 from the radial lubrication path 12b. Prepare.

  The lubricating oil that has passed through the annular space C and the bearing space of the rolling bearings 22, 21 passes through the side opening D of the bearing space on one end side in the axial direction of the rolling bearing 21, and is on the side of the operating mechanism 30 of the oil pump 60. Go back to.

  Thereby, the operation mechanism part 30 of the oil pump and the rolling bearings 21, 22, and 23 of the bearing unit 20 are lubricated by the common lubricating oil.

  By the way, foreign matter such as wear powder (iron powder or the like) may be generated from the bearing space of the rolling bearings 21, 22, and 23. It is not preferable for this foreign matter to enter the operating mechanism 30 of the oil pump 60 or another operating mechanism 70 in the circulation path outside the pump. Therefore, the seal member 40 (hereinafter, referred to as the side opening D of the bearing space on one axial end side of the rolling bearing 21 and the opening 12c on one axial end side of the circulation path 12, that is, the opening 12c of the axial lubrication path 12a). In the embodiment, since the annular seal member 40 is used, this is referred to as a seal ring 40).

  The seal ring 40 is attached to the housing 11 and the outer ring 1 so as to cover the side opening D of the bearing space on one end side in the axial direction of the rolling bearing 21 and the opening 12c on one end side in the axial direction of the circulation path 12. Since the side opening D of the bearing space on one end side in the axial direction of the rolling bearing 21 is formed in an annular shape along the raceway surfaces 1a and 2a of the outer ring 1 and the inner ring 2, the seal ring 40 covering the ring D also forms an annular shape. It has become a thing.

  As shown in FIG. 1, the seal ring 40 is brought into contact with the end face of the rolling bearing 21 and is housed in the housing 11 together with the other rolling bearings 22 and 23 and spacers 5, 6, and 7.

  As shown in FIG. 9, the seal ring 40 has a cylindrical axial portion 42 whose cylindrical axial end surface 41 is in contact with the end surface 1 d on the axial end of the outer ring 1, and the cylindrical axial direction of the cylindrical portion 42. A wall 43 that rises from the one end toward the inner diameter side.

  A filter 46 is provided on the wall 43. The filter 46 prevents foreign substances from passing through the bearing space of the rolling bearings 21 and 22 by the assembly of the filter holes 46a including through holes, and allows the passage of lubricating oil. At this time, if the inner diameter of the filter hole 46a is small, the filter hole 46a is set to an appropriate size so as to allow the passage of foreign matter to the extent that it does not affect even if it enters the operating mechanism 30 side.

  In this embodiment, the seal ring 40 is made of a molded product of synthetic resin. Further, the seal ring 40 forms an annular shape along the side opening D of the bearing space of the rolling bearing 21, and a plurality of divided seal members 40 ′ divided along the circumferential direction of the annular ring are connected pieces 80. It is the coupling body connected by the annular | circular shape by. The split seal members 40 ′ adjacent in the circumferential direction are connected by a connecting piece 80. The connecting piece 80 is also made of a synthetic resin molded product.

  In this embodiment, since the annular seal ring 40 is constituted by two divided seal members 40 ′ having a central angle of 180 °, the connecting piece 80 is located at two locations, the upper portion and the lower portion of the seal ring 40. ing.

  Furthermore, the seal ring 40 is not limited to a two-divided configuration using two split seal members 40 ′ having a central angle of 180 °, but, for example, by using four split seal members 40 ′ having a central angle of 90 °, The seal ring 40 may be configured, or the annular seal ring 40 may be configured by using six divided seal members 40 ′ having a central angle of 60 °.

  In this embodiment, the seal ring 40 integrally forms the filter 46 of the wall portion 43 with the main body of the seal ring 40, but the filter 46 of the wall portion 43 is connected to the main body member of the seal ring 40. As another member, the separate member may be fixed to the main body of the seal ring 40 by various means such as fitting and fixing, embedding and adhesion.

  As a material for the seal ring 40 and the connecting piece 80, other materials such as metal and rubber may be employed in addition to the resin. Even when the filter 46 is a separate member from the seal ring 40, other materials such as resin, metal, and rubber can be used as the material of the filter 46.

  Further, the connecting piece 80 is provided with an axial member 82 extending in the axial direction from the base portion 81 contacting the outer peripheral surface of the cylindrical portion 42 of the seal ring 40 toward the rolling bearing 21 side.

  The axial member 82 extends between the inner diameter surface of the housing 11 and the outer diameter surface of the outer ring 1 and extends toward the rolling bearing 21, and the axial member 82 engages with a bearing member such as a bearing ring or a spacer. Thus, the seal ring 40 is fixed to the housing 11 and the outer ring 1.

  In this embodiment, the axial member 82 extends from the axial direction one end side to the other end side through the axial lubrication path 12a of the circulation path 12, and the distal end 82a of the axial direction member 82 is tapered. It has a shape. For this reason, the insertion into the housing 11 is smooth. Further, an inner diameter side protruding portion 83 extending toward the inner diameter side is provided near the tip of the axial member 82. The axial lubrication path 12 a is an oil path for lubricating oil disposed along the axial direction between the inner diameter surface of the housing 11 and the outer diameter surface of the outer ring 1.

  The axial member 82 is in contact with the outer diameter surface of the outer ring 1, and the inner diameter side protruding portion 83 enters the retaining recess 50 provided in the bearing ring or spacer of the bearing, whereby the axial direction of the seal ring 40 is increased. Movement is restricted. In this embodiment, the retaining recess 50 includes an end surface 6a on one end side of the spacer 6 and a shoulder portion of the outer ring 1 of the rolling bearing 21, that is, an outer diameter surface of the outer ring 1 and an end surface 1b on the other end side in the axial direction. It is comprised by the curved-shaped round part 1c and chamfering part formed in the ridgeline part between.

  The spacer 6 is an adjacent member disposed adjacent to the other end side in the axial direction of the outer ring 1. The spacer 6 that is an adjacent member has a function of positioning the outer rings 1 of the rolling bearings 21 and 22 adjacent in the axial direction in the axial direction.

  Further, the opening 12c on one end side in the axial direction of the axial lubrication path 12a is located on the outer diameter side with respect to the side opening D of the bearing space of the rolling bearing 21 having an annular shape in a side view. In this embodiment, two axial lubrication paths 12a of the circulation path 12 are provided and have openings 12c at two positions with an interval of 180 ° along the circumferential direction. The number may be increased or decreased as necessary.

  The connecting piece 80 includes a first outer diameter side protruding portion 84 that protrudes toward the circulation path 12 and abuts against the inner wall of the circulation path 12. The first outer diameter side protruding portion 84 rises from the outer surface of the axial member 82 toward the outer diameter side, and includes a convex portion 84a, a concave portion 84b, and an oil passage hole 84c on the outer diameter surface. The convex portion 84a contacts the inner wall of the circulation path 12 to support the connecting piece 80, and the gap between the concave portion 84b and the inner surface of the circulation path 12 and the oil passage hole 84c are lubricated from the circulation path 12 to the outside of the bearing space. It becomes an oil passage. The clearance between the recess 84b and the inner surface of the circulation path 12 and the inner diameter of the oil passage hole 84c are set to be equal to or smaller than the mesh size of the filter 46. A plurality of through holes and slits may be provided in the first outer diameter side protruding portion 84 to provide a filter for capturing foreign matter.

  Further, the connecting piece 80 has a second outer-diameter-side protruding portion 90 that protrudes toward the circulation path 12 on the one end side in the axial direction from the first outer-diameter-side protrusion 84 and contacts the inner wall of the circulation path 12. Prepare. The second outer diameter side protruding portion 90 rises from the outer surface of the axial member 82 toward the outer diameter side, and includes a convex portion 90a, a concave portion 90b, and an oil passage hole 90c on the outer diameter surface. The convex portion 90a contacts the inner wall of the circulation path 12 to support the connecting piece 80, and the gap between the concave portion 90b and the inner surface of the circulation path 12 and the oil passage hole 90c are lubricated from the circulation path 12 to the outside of the bearing space. It becomes an oil passage. The clearance between the recess 90b and the inner surface of the circulation path 12 and the inner diameter of the oil passage hole 90c are set to be the same as or smaller than the mesh size of the filter 46. A plurality of through holes and slits may be provided in the second outer diameter side protruding portion 90 to provide a filter for capturing foreign matter.

  Further, the axial direction member 82, the first outer diameter side protruding portion 84, and the second outer diameter side protruding portion 90 have their widths so as to enter the circulation path 12 and fix the connecting piece 80 without rattling. The (width in the circumferential direction of the rolling bearing) matches the width of the circulation path 12 (also in the circumferential direction of the rolling bearing). Thereby, the seal ring 40 is prevented from rotating with respect to the housing 11 and the outer ring 1. That is, the axial member 82, the first outer diameter side protruding portion 84, and the second outer diameter side protruding portion 90 function as a detent means for the seal ring 40.

  As shown in FIG. 5, the connecting piece 80 is provided with a pair of support portions 85 extending from the base portion 81 to both sides in the circumferential direction. The support portion 85 is a cylindrical surface member along the outer diameter surface of the seal ring 40. Each support portion 85 is provided with a locking projection 88 that protrudes toward the inner diameter side. The engaging protrusions 88 enter the engaging holes 48 provided at the end portions of the divided seal members 40 ′ adjacent in the circumferential direction, so that the connecting piece 80 is divided into the divided seal members 40 ′ adjacent in the circumferential direction. Connect the ends of each other. Thereby, the division | segmentation sealing member 40 'is comprised by the annular connection body.

  Further, as shown in FIG. 6, the end portions of the split seal member 40 ′ are engaged with the key-like portions 47 a and 47 b provided on the wall portion 43 and facing each other, so that the connection is further strengthened. .

  Further, the inner diameter side end of the wall 43 of the seal ring 40 faces the outer surface of the large collar of the inner ring 2 with a slight gap w, and a gap (final clearance) is formed between the wall 43 and the inner ring 2. ) Forming a labyrinth seal structure having w. In this gap, the lubricating oil is allowed to pass, but the passage of foreign matter exceeding the size of the gap w is blocked. The gap w between the inner diameter side end of the wall 43 and the outer diameter surface of the large collar of the inner ring 2 is set to be the same as or smaller than the mesh size of the filter 46. As shown in FIG. 4, the gap w is set so as not to be smaller than the predetermined gap w <b> 1 by the convex portion 44 provided on the inner diameter surface of the seal ring 40. In the drawing, the symbol w2 is the width of the convex portion 44 with respect to the axial direction of the seal ring 40, and the symbol w3 is the width of the convex portion 44 with respect to the circumferential direction of the seal ring 40.

  In this embodiment, the connecting piece 80 and the divided seal member 40 ′ are provided with a fold prevention means for restricting the bending (generation of fold points) of the connecting portion between the divided seal members 40 ′ adjacent in the circumferential direction. When the connecting portions of the divided seal members 40 ′ are bent, the surface directions of the axial end surfaces of the divided seal members 40 ′ are different from each other, and a gap is formed between the end surface of the seal ring 40 and the end surface 1d of the outer ring 1. Such a breakage prevention means is effective.

  In the example shown in FIGS. 6 (a) and 6 (b), each of the split seal members 40 ′ adjacent to each other in the circumferential direction and the connecting piece 80 serve as a break prevention means, and a plurality of locking projections 88 (88a, 88a) are mutually connected. 88b, 88b) and the corresponding number of locking holes 48 (48a, 48a; 48b, 48b) are connected by locking. Here, the two locking projections 88 arranged in parallel fit into the corresponding two locking holes 48, respectively, and relative rotation, rattling, etc. occur between the connecting piece 80 and the divided seal member 40 ′. It is difficult to occur. In particular, by providing a plurality of locking projections 88 and a plurality of locking holes 48 corresponding thereto in the circumferential direction, the connection between the divided seal members 40 'becomes strong, and the connection portion Prevents bending. At this time, it is desirable that the width of the locking projection 88 (width with respect to the axial direction of the seal ring 40) and the width of the locking hole 48 (width with respect to the axial direction of the seal ring 40) are equal.

  In addition, the some latching convex part 88 and the some latching hole 48 corresponding to it can also be arrange | positioned so that it may mutually parallel in an axial direction.

  Moreover, in the example shown to Fig.6 (a) (b), although the latching convex part 88 and the latching hole 48 are each circular in cross section, they are good also as having a non-circular cross section.

  Further, if the break prevention means is provided between at least one of the circumferentially adjacent divided seal members 40 ′ and the connecting piece 80, the axial end surface of the seal ring 40 and the end surface 1 d of the outer ring 1 are provided. Although it can contribute to the prevention of gaps between them, it is desirable that the gap is provided between each of the divided seal members 40 ′ adjacent in the circumferential direction and the connecting piece 80.

  As shown in FIG. 6C, a retaining projection 88 c is provided at the tip of the latching projection 88. The retaining protrusion 88 c engages with the edge of the locking hole 48 and exhibits a retaining function that prevents the locking protrusion 88 from slipping out of the locking hole 48.

  Further, by making the connection position of the divided seal member 40 ′ and the connecting piece 80 variable along the circumferential direction, the diameter of the seal ring 40 configured by connecting the plurality of divided seal members 40 ′ can be adjusted. it can. In the example of FIG. 7, the locking hole 48 into which the locking projection 88 enters can be arbitrarily selected from a plurality of locations set along the circumferential direction.

  In the example of FIGS. 7A and 7B, the gap w1 is increased by using the locking hole 48 on the side far from the end of the divided seal member 40 ′, and the diameter of the ceiling 40 is set relatively large. In the example of FIGS. 7C and 7D, the gap w2 is reduced by using the locking hole 48 on the side close to the end of the divided seal member 40 ′, and the diameter of the seal ring 40 is relatively set. Is set smaller.

  Further, in the example shown in FIG. 7, by making the locking hole 48 a long hole extending in the circumferential direction, the locking projection 88 can move in the locking hole 48 along the length direction of the long hole. It is like that. Specifically, while the locking projection 88 has a circular cross section, the shape of the locking hole 48 extends at an equal width along the circumferential direction of the seal ring 40, and the closed edges at both ends thereof are semicircular. It has a long hole shape. For this reason, the engaging protrusion 88 moves in the engaging hole 48 along the longitudinal direction of the long hole, so that the connecting piece 80 connects the ends of the divided seal members 40 ′ adjacent to each other in the circumferential direction. Can be slidably connected. Thereby, when the seal ring 40 is thermally expanded due to a temperature rise or when the seal ring 40 is contracted due to a temperature drop, the distance between the end portions of the divided seal members 40 ′ connected by the connecting piece 80 is changed. Thus, the expansion and contraction can be dealt with.

  In the example shown in FIG. 8A, as in the previous example, each of the circumferentially adjacent divided seal members 40 ′ and the connecting piece 80 are each a plurality of locking projections 88, and the number corresponding to that is the number. It is connected by being locked in the locking hole 48 to constitute a break prevention means.

  Here, of the two locking projections 88 related to the connection between the divided seal member 40 ′ and the connecting piece 80, the locking projection 88 on the side far from the end of the divided seal member 40 ′ is the locking hole 48. Is in contact with the inner wall on the outer ring 1 side, and a gap is interposed between the inner wall on the opposite side. Further, the locking projection 88 on the side close to the end of the split seal member 40 ′ has a gap between the locking hole 48 and the inner wall on the outer ring 1 side, and abuts against the opposite inner wall. Yes. With such a configuration, the width of the locking projection 88 (the width of the seal ring 40 with respect to the axial direction) is made smaller than the width of the locking hole 48 (the width of the seal ring 40 with respect to the axial direction). It is possible to prevent the seal ring 40 from being bent in the direction indicated by the arrow x in the drawing while ensuring proper locking and unlocking.

  That is, since the vicinity of the connecting portion between the split seal members 40 ′ is restrained by the outer ring 1 by the function of preventing the connecting piece 80 from coming off, a portion away from the connecting piece 80 in the circumferential direction is shown in FIG. It is effective to prevent the outer ring 1 from detaching from the end surface 1d as indicated by an arrow x in FIG.

  In the example shown in FIG. 8B, each of the circumferentially adjacent divided seal members 40 ′ and the connecting piece 80 are formed by one locking projection 88 and one locking hole 48 corresponding thereto. It is connected by locking. Here, the cross-sectional shape of the locking projection 88 and the locking hole 48 is made non-circular to constitute a break prevention means, and the bending of the seal ring 40 in the direction indicated by the arrow x in FIG. 8B is prevented. doing. Here, the cross-sectional shapes of the locking projection 88 and the locking hole 48 are rectangular, but various shapes such as a pentagon, a hexagon, and an ellipse can be employed.

  8C and 8D, the length of the long hole-like locking hole 48 in the example of FIG. 7 is increased along the circumferential direction of the seal ring 40. For this reason, it has a mode in which a plurality of locking projections 88 arranged in parallel in the circumferential direction are inserted into and locked in one long hole-shaped locking hole 48.

  As described above, at least one locking protrusion 88 may be provided for each of the divided seal members 40 ′ adjacent in the circumferential direction, but two or more than two may be provided. At this time, the bend prevention means can exhibit the effect of preventing the bending at the connecting portion if there are two or more locking projections 88 for each of the divided seal members 40 ′. Further, if the folding preventing means has one locking projection 88 for each of the divided seal members 40 ′, the sectional shape of the locking projection 88 is non-circular, and the sectional shape of the locking hole 48. In addition, by adopting the same shape in which the locking projection 88 fits snugly, the relative rotation between the divided seal member 40 ′ and the connecting piece 80 can be restricted, and the effect of preventing bending at the connecting portion can be exhibited.

  In the example shown in FIG. 9, FIG. 9A shows a longitudinal section of the seal ring 40 and the like in the direction in which the connecting piece 80 exists. A plurality of connecting pieces 80 are provided along the circumferential direction (in this example, a total of two places every 180 °). And between the connection pieces 80 adjacent to the circumferential direction, as shown in FIG. 9B, the seal ring 40 has an outer ring locking projection that restricts the movement of the seal ring 40 relative to the outer ring 1 to the outer diameter side. 45 is provided. The outer ring locking projection 45 is preferably provided at the center between the adjacent connecting pieces 80. As shown in FIG. 9 (c), the outer ring locking convex portion 45 is locked to the jaw portion between the raceway surface 1 a and the end surface 1 d of the outer ring 1 to move the seal ring 40 toward the outer diameter side. regulate.

  As shown in FIG. 10, connecting pieces 80 are positioned on the upper side in the vertical direction and the lower side in the vertical direction of the housing 11. Here, it is assumed that the seal ring 40 is about to thermally expand in the outer diameter direction due to the temperature rise of the member. This thermal expansion in the outer diameter direction is restrained from the upper side and the lower side in the vertical direction as indicated by an arrow P in the drawing. This is because the first outer diameter side protruding portion 84 and the second outer diameter side protruding portion 90 of the connecting piece 80 are in contact with the housing 11. That is, the connecting piece 80 restricts the movement of the seal ring 40 relative to the housing 11 toward the outer diameter side.

  For this reason, the thermal expansion of the seal ring 40 acts in the circumferential direction in the direction of arrow R in FIG. Therefore, between the connecting pieces 80 adjacent to each other in the circumferential direction, as indicated by an arrow Q, a force acts to expand the seal ring 40 in the outer diameter direction. At this time, the outer ring locking projection 45 can regulate the movement of the seal ring 40 relative to the housing 11 to the outer diameter side. Thereby, the gap w set on the inner diameter side of the seal ring 40 is appropriately secured.

  FIG. 11 shows a modified example of the connecting piece 80. The connecting piece 80 of this modification includes a locking piece 89 that protrudes toward the inner diameter side at one end in the axial direction of the base 81 that contacts the outer diameter surface of the cylindrical portion 42. The locking piece 89 comes into contact with the end face on the one end side in the axial direction of the cylindrical portion 42, and the connecting piece 80 is fixed to the seal ring 40. For this reason, installation of the support part 85 is abbreviate | omitted. The seal ring 40 is formed in an annular shape as an integral member.

  Here, the retaining structure of the connecting piece 80 will be described. FIG. 12 illustrates the operation of the present invention by taking the connecting piece 80 of FIG. 11 provided with the locking piece 89 without the support portion 85 as an example. The connecting piece 80 is shown in FIGS. Even if it is the aspect provided with the support part 85 as shown, the same effect can be exhibited.

  As shown in FIG. 12A, the connecting piece 80 has an end surface on the other end side in the axial direction of the retaining recess 50 with which the outer diameter side protruding portion 84 provided on the axial member 82 contacts the inner diameter side protruding portion 83. It is located further on the other axial end side than 6a. That is, the outer diameter side protruding portion 84 is located further on the other end side in the axial direction than the curved rounded portion 1c formed on the ridge line portion between the outer diameter surface of the outer ring 1 and the end surface 1b.

  As a result, when the connecting piece 80 integrated with the seal ring 40 is inserted into the axial lubrication path 12a, the axial member 82 is the edge on the other axial end side of the outer diameter side protruding portion 84, that is, the outer side. The chamfered portion 84c provided in the ridge line portion between the outer diameter surface 84b of the radial side protruding portion 84 and the end surface 84a on the other end side abuts on the inner diameter side edge of the end surface 11a of the housing 11, so that FIG. As shown by the arrow a, it is pressed from the housing 11 side toward the inner diameter side. Since the inner diameter side projecting portion 83 and the outer diameter side projecting portion 84 are set to overlap with each other in the axial direction, the inner diameter side projecting portion 83 is moved along the inclined surface of the rounded portion 1c by pressing the arrow a. It is smoothly guided to the recess 50.

  Subsequently, when the seal ring 40 and the connecting piece 80 are pushed into the other end side in the axial direction, the connecting piece 80 is pressed from the housing 11 side to the inner diameter side as shown by an arrow c in FIG. The inner diameter side protruding portion 83 enters deeply into the retaining recess 50.

  At this time, since the outer diameter side protruding portion 84 is located on the other end side in the axial direction from the rounded portion 1c, the inner diameter side protruding portion 83 is pulled toward the other end side in the axial direction so as to go down the inclined surface of the rounded portion 1c ( (See arrow b in FIG. 12B). A surface 83b facing the one end side in the axial direction of the inner diameter side protruding portion 83 and an inner wall (the rounded portion 1c) on one end side in the axial direction of the retaining recess 50 with which the inner diameter side protruding portion 83 abuts are formed from one end side in the axial direction. Since it is inclined toward the inner diameter side toward the other end side in the axial direction, such an action can be expected.

  Further, the inner diameter side protruding portion 83 is pulled toward the other end side in the axial direction so as to go down the inclined surface of the rounded portion 1c (see the arrow b in FIG. 12B), so that the axial direction of the inner diameter side protruding portion 83 and the like. The end surface 83 a on the end side is in surface contact with the end surface 6 a on the other end side in the axial direction of the retaining recess 50. An end surface 83a on the other end side in the axial direction of the inner diameter side protruding portion 83 and an end surface 6a on the other end side in the axial direction of the retaining recess 50 have a surface direction orthogonal to the axial direction. Thereby, the connecting piece 80 is positioned in the axial direction by the end surface 6a on the other end side in the axial direction of the retaining recess 50 and is more firmly fixed.

  The effect of the curved rounded portion 1c provided on the ridgeline portion of the outer ring 1 is the same even when the ridgeline portion of the outer ring 1 is replaced with the rounded portion 1c and a chamfered portion with a corner of the ridgeline portion is dropped. It can be demonstrated. That is, it is desirable that the inner wall on one end side in the axial direction of the retaining recess 50 with which the inner diameter side protruding portion 83 abuts is inclined toward the inner diameter side from the one axial end side toward the other axial end side.

  In this regard, if the outer-diameter-side protruding portion 84 is located on one end side in the axial direction with respect to the end surface 6a on the other end side in the axial direction of the retaining recess 50, as shown by an arrow e in FIG. The connecting piece 80 is pulled toward one end in the axial direction. For this reason, it is desirable that the outer diameter side protruding portion 84 is located on the other end side in the axial direction with respect to the end surface 6 a on the other end side in the axial direction of the retaining recess 50.

  Furthermore, as shown in FIG. 12C, the outer diameter side protruding portion 84 and the spacer 6 are disposed so that their axial positions overlap within the range of the axial width L in the drawing. The spacer 6 has an axial width of a symbol W in the drawing. For this reason, when the outer diameter side protruding portion 84 is pressed from the housing 11 side toward the inner diameter side, the pressing force is easily transmitted to the inner diameter side protruding portion 83 that enters the retaining recess 50.

  In this regard, if the axial positions of the outer diameter side protruding portion 84 and the spacer 6 do not overlap, as shown in FIG. 20B, the outer diameter side protruding portion 84 moves from the housing 11 side to the inner diameter. When pressing toward the side, the pressing force causes the tip 82a of the axial member 82 to become a force that tilts toward the inner diameter side and escapes, and the inner diameter side protruding portion 83 is removed as shown by the arrow f. It will slip out of the stop recess 50. For this reason, it is desirable that the axial positions of the outer diameter side protruding portion 84 and the spacer 6 overlap.

  In addition, it is desirable that the axial positions of the outer diameter side protruding portion 84 and the inner diameter side spacer 5 also overlap. This is because when the outer diameter side protrusion 84 is pressed from the housing 11 side toward the inner diameter side, the pressing force is easily transmitted to the inner diameter side protrusion 83 that enters the retaining recess 50.

  By adopting such a configuration, the lubricating oil from the bearing space of the rolling bearings 21, 22, 23 can be removed from the hole 46 a of the filter 46 provided in the seal ring 40, the hole or gap in the circulation path 12, or the wall. It passes through the gap between the inner diameter side end of the portion 43 and the outer diameter surface of the inner collar 2 and flows out of the bearing space. For this reason, large foreign matters (in particular, wear particles made of metal as well as peeling pieces) that affect the operation of the operating mechanism portions 30 and 70 do not enter the operating mechanism portions 30 and 70 side. Further, since the seal ring 40 is firmly fixed to the outer ring 1 by the connecting piece 80, it is possible to prevent a gap from flowing out foreign matter between the seal ring 40 and the outer ring 1 or the like.

  In the embodiment described above, the retaining recess 50 is formed between the outer ring 1 and the spacer 6 (adjacent member). However, the retaining recess 50 is formed on the outer diameter surface of the outer ring 1 or the spacer 6. You may form in an outer diameter surface. Alternatively, the outer ring 1 of another rolling bearing 22 adjacent to the rolling bearing 21 may be used as an adjacent member, and the retaining recess 50 may be formed on the outer diameter surface of the adjacent member.

  Further, the surface roughness of the outer diameter surfaces 84b and 90b in the first outer diameter side protruding portion 84 and the second outer diameter side protruding portion 90 of the connecting piece 80 is the base portion 81 and the inner diameter surface 82b of the axial member 82, That is, it is smaller (smooth) than the surface roughness of the outer diameter surface 1 d of the outer ring 1 that contacts the connecting piece 80. Thereby, the effect that the connecting piece 80 becomes difficult to come off can be expected.

  Here, as a reference for comparing the surface roughness, for example, centerline average roughness (arithmetic average roughness Ra: numerical value indicated by a centerline obtained by leveling all the surface peaks) defined in JIS (Japanese Industrial Standards) and the like. ), Maximum height roughness (Rmax: height of the highest peak in the surface measurement range), ten-point average height (Rz: average of 10 points extracted from the high peaks in the surface measurement range) Various standards and measurement methods such as (taken values) can be adopted.

  Further, for example, as shown in FIG. 12 (d), a width A + α of the inner diameter side protruding portion 83 of the connecting piece 80 can be larger than the width A of the base portion 81 or the axial member 82. . That is, in this modification, both ends 83c and 83d of the inner diameter side protruding portion 83 protrude outward from the widthwise both ends 82c and 82d of the base portion 81 and the axial member 82. As a result, the connecting piece 80 has a convex shape protruding in the circumferential direction. As a result, the width between the convex portions protruding in the circumferential direction is larger than the width of the opening 12c of the axial lubrication path 12a. Since the projecting portion protruding in the circumferential direction enters a portion of the housing 11 that is not the axial lubrication path 12 at the time of insertion, the shaft connecting piece 80 is axially or radially more than when the inner diameter side protruding portion 83 is inserted into the housing 11. The movement is restricted, and it will not come off during driving.

  Further, in each of the above-described embodiments, a sensor unit that detects adhesion of a foreign substance such as metal powder may be provided around the hole 46 a of the filter 46 provided in the seal ring 40. As the sensor unit, for example, it is possible to employ an electric sensor that detects the presence of a foreign substance by a change in electrical output when the foreign substance is short-circuited between the electrodes due to the presence of a foreign substance between a pair of electrodes. it can.

  For example, when a foreign object made of metal of a size that cannot pass through the hole 46a of the filter 46 adheres between the pair of electrodes, the output detection device connected through the cable from the pair of electrodes is connected between the pair of electrodes. The change in the electrical output of the electric circuit can be detected by the conduction through the foreign matter, and the state (content) of the foreign matter made of a metal contained in the lubricating oil can be detected. The cable connected to the pair of electrodes is drawn out of the housing 11 through the substrate, and an output detection device connected to the cable is provided in any part. A sensor hole for drawing the cable out of the seal ring 40 can be provided in the cylindrical portion 42 or the wall portion 43 of the seal ring 40.

  13 to 19 show a second embodiment of the present invention. In this embodiment, the second outer diameter side protruding portion 90 of the connecting piece 80 in the first embodiment is omitted. Moreover, it differs in that the locking projection 88 provided in the connecting piece 80 is one for each divided seal member 40 '.

  Thus, even when the outer diameter side protruding portion of the connecting piece 80 is only one, that is, the outer diameter side protruding portion is only the first outer diameter side protruding portion 84, the connecting piece 80 is similarly formed of the seal ring 40. The anti-rotation function, the retaining function, and the function of preventing movement to the outer diameter side can be exhibited.

  FIG. 1 in the first embodiment corresponds to FIG. 13 in the second embodiment. 2 corresponds to FIG. 14 and FIG. 3 corresponds to FIG. FIG. 4 is common to the first embodiment and the second embodiment except for the presence / absence of the second outer diameter side protrusion 90. 5 corresponds to FIG. 16, FIG. 6 corresponds to FIG. 17, and FIG. 11 corresponds to FIG. FIG. 12 and FIG. 19 are the contents common to the first embodiment and the second embodiment except for the presence or absence of the second outer diameter side protruding portion 90. For this reason, detailed description is omitted.

  In these embodiments, the locking projection 88 is provided in the connecting piece 80 and the locking hole 48 is provided in the divided seal member 40 ′. The locking hole 48 may be provided in the connecting piece 80.

  In the above embodiment, the filter 46 is provided on the seal ring 40. However, the present invention can be applied to the seal ring 40 that does not include the filter 46. In addition to the split seal ring 40 using the split seal member 40 ′ and the connecting piece 80, the present invention can be applied to an integral annular seal ring 40 that is not a split type.

  The seal member of the present invention can be applied to various rolling bearing units other than the embodiment. Further, the rolling bearing unit including the seal member can be applied to various devices other than the oil pump 60. In particular, the rolling bearing of the present invention requires various types of foreign materials such as wear powder (iron powder, etc.) generated from the rolling bearing to be prevented from entering the operating mechanism 70 in the middle of the lubricating oil circulation path. Applicable to equipment.

1 Outer ring (outer raceway)
1b End face 1c Round portion 2 Inner ring (Inner race)
DESCRIPTION OF SYMBOLS 3 Rolling body 4 Cage 5, 6, 7 Spacer 6a End surface 8 Holding member 10 Oil pump apparatus 11 Housing 12, 13 Circulation path 20 Bearing unit 21, 22, 23 Rolling bearing 30 Actuation mechanism part 31 Connection member 32 Shaft member 40 Seal ring (seal member)
40 'split seal member 44 convex portion 45 outer ring locking convex portion 46 filter 50 retaining recess 60 oil pump 70 operating mechanism portion 80 connecting piece 81 base portion 82 axial member 83 inner diameter side protruding portion 84 outer diameter side protruding portion 85 support portion

Claims (6)

An outer ring fixed in the housing;
An inner ring facing the outer ring;
A rolling element disposed in a bearing space between the outer ring and the inner ring;
An annular seal member attached to one end side in the axial direction of the outer ring and covering a side opening of the bearing space;
An oil passage for lubricating oil disposed along the axial direction between the inner diameter surface of the housing and the outer diameter surface of the outer ring;
A connecting piece that enters the oil passage and fixes the seal member to the outer ring;
With
A plurality of divided seal members divided along the circumferential direction are connected by the connecting pieces to form an annular connecting body,
The connecting piece and the divided seal member are rolling bearing units provided with a bending prevention means for restricting bending of a connection portion between the divided seal members adjacent in the circumferential direction. The engaging protrusion provided on one of the connecting piece and the split seal member enters the engaging hole provided on the other, so that the end portions of the split seal members adjacent to each other in the circumferential direction are in the circumferential direction. The rolling bearing unit according to claim 1, wherein the rolling bearing unit is slidably connected. The rolling bearing unit according to claim 2, wherein the locking projection is provided in the connecting piece, and the locking hole is provided in the divided seal member. The connecting piece has a base that abuts on an end of the split seal member adjacent in the circumferential direction;
A pair of support portions extending from the base portion to both sides in the circumferential direction,
The rolling bearing unit according to claim 3, wherein the locking convex portion is provided on the support portion. The folding preventing means includes a plurality of locking protrusions that are connected to the locking holes between at least one of the divided sealing members adjacent to each other in the circumferential direction and the connecting piece. The rolling bearing unit according to claim 2, which is configured as described above. The fold prevention means includes a non-circular locking projection formed in the locking hole having the same shape between at least one of the divided sealing members adjacent to each other in the circumferential direction and the connecting piece. The rolling bearing unit according to any one of claims 2 to 4, wherein the rolling bearing unit is configured to be inserted and connected.

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