JP6635861B2 - Rolling bearing unit - Google Patents

Description

  The present invention relates to a rolling bearing lubricated with oil, 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 machines, and other various equipment. Some of these devices have an operating mechanism that requires lubrication in addition to the oil-lubricated rolling bearing, and the operating mechanism and the rolling bearing are structured to be lubricated with a common oil. There is something. Examples of the operating mechanism include a meshing portion between gears and a sliding contact portion between members.

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

  Incidentally, foreign matters such as abrasion powder (iron powder and the like) may be generated from the bearing space of the rolling bearing. When 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 foreign matter being caught. In some cases, this may lead to malfunction, failure, or breakage of the device.

  Therefore, for example, in Patent Document 1, when foreign matter such as iron powder is mixed into lubricating oil flowing in the circulation path, the foreign matter is adsorbed by a magnet provided in the sensor, and the adsorbed foreign matter is deposited. Thus, a method of detecting iron powder contamination of lubricating oil that issues an alarm when a metal casing and a magnet are electrically connected to each other is disclosed (for example, see Patent Document 1).

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

JP-A-7-280180 JP 2012-102767 A

  As described above, it is not preferable that foreign matter such as abrasion powder (iron powder or the like) generated from the rolling bearing enters the operating mechanism part in the middle of the lubricating oil circulation path. In particular, in a rolling bearing unit for an oil pump, a large separation piece generated from a bearing may be generated by an operating mechanism of the oil pump itself or another operating mechanism in a circulation path of lubricating oil sent out by the oil pump. It may cause malfunction, failure or breakage of 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 substances from flowing out from inside the rolling bearing to the operating mechanism.

  By the way, when the seal member is fixed to the outer ring side, the inner diameter side end of the seal member slides on the outer diameter surface of the inner ring or faces through a slight gap. The gap in the radial direction between the inner diameter side end portion of the seal member and the outer diameter surface of the inner ring is referred to as “last clearance”.

  The last clearance must be set to a size equal to or smaller than the mesh size of the filter of the seal member so that foreign matter does not flow out from inside the rolling bearing to the operation mechanism. For this reason, the dimension of the last clearance must be controlled when or after the seal member is mounted on the rolling bearing.

  However, a dimensional error within the tolerance occurs at the time of manufacturing the seal member. This dimensional error becomes relatively large when the seal member is made of resin.

  Due to this dimensional error, the inner diameter side end of the seal member may slide on the outer diameter surface of the inner race. In addition, the last clearance may be reduced due to thermal expansion of the seal member, and the inner end of the seal member may slide on the outer surface of the inner race. If the seal member and the inner ring are in strong sliding contact with each other, the seal member is worn, and the last clearance may be further increased, which is not preferable.

  Therefore, an object of the present invention is to make it possible to more appropriately manage the size of the last clearance, which is a gap in the radial direction between the inner diameter side end portion of the seal member and the outer diameter surface of the inner ring.

  In order to solve the above problems, the present invention provides an outer ring and an inner ring, a rolling element disposed in a bearing space between the outer ring and the inner ring, and a member fixed to the outer ring or a member fixed to the outer ring. An annular seal member that covers a side opening of the bearing space, wherein the seal member has an annular connector in which a plurality of divided seal members divided along a circumferential direction are connected by connecting pieces. A rolling bearing provided with a gap adjusting means that can adjust the gap in the circumferential direction between the connecting portions of the divided sealing members and the connecting pieces adjacent in the circumferential direction is adopted.

  Here, the gap adjusting means includes a locking portion provided on the connecting piece, and a locked portion provided on the split seal member and locked by the locking portion. A configuration in which a plurality of portions are provided along the circumferential direction at the circumferential end of the divided seal member can be adopted.

Alternatively, the interval adjusting means includes a locking portion provided on the divided seal member, and a locked portion provided on the connecting piece and locking the locking portion,
A configuration in which a plurality of the locked portions are provided on the connecting piece along the circumferential direction can be adopted.

  In each of the aspects, it is possible to adopt a configuration in which one of the locking portion and the locked portion is a convex portion, and the other is a concave portion in which one is fitted.

  A configuration may be employed in which the protrusion or the recess is provided with a retaining protrusion for preventing the protrusion from coming out of the recess.

  The seal member includes a cylindrical portion that comes into contact with an end surface of the outer ring, and a wall portion that rises from one end of the cylindrical portion in the axial direction toward the inner diameter side, and each of the divided seal members that are adjacent in the circumferential direction is It is possible to adopt a configuration in which the opposing wall portion or the opposing cylindrical portion includes a key-shaped portion that meshes with each other.

  The seal member includes a cylindrical portion that abuts an end surface of the outer ring, and a wall portion that rises from one end of the cylindrical portion in the axial direction toward the inner diameter side, and each of the divided seal members that are adjacent in the circumferential direction. The gap between the circumferential ends of the opposed cylindrical portions may be closed by the connecting piece.

  According to the present invention, an annular seal member that covers a side opening of a bearing space between an outer ring and an inner ring is connected to a plurality of divided seal members divided along a circumferential direction by a connection piece. Since it is provided with a gap adjusting means configured as a body and capable of adjusting the gap in the circumferential direction between the connecting portions of the divided sealing members and the connecting pieces adjacent to each other in the circumferential direction, the inner ring side end of the seal member and the inner ring are provided. The dimension of the last clearance, which is a gap in the radial direction with respect to the outer peripheral surface, can be managed more appropriately.

1A and 1B show an embodiment of the present invention, in which FIG. 1A is a side view of a bearing unit having a plurality of rolling bearings, and FIG. (A) is a plan view of a main part of a rolling bearing provided with a seal member, and (b) is a perspective view thereof. (A) is a side view of a rolling bearing provided with a sealing member, (b) is a front view Exploded perspective view of a seal member 5A and 5B show connecting pieces for connecting the divided seal members, wherein FIG. 5A is a plan view, FIG. 5B is a front view of FIG. 5A, and FIG. 5C is a right side view of FIG. (A), (b) is an enlarged view of a main part showing a connecting portion between divided seal members, and (c) is a sectional view showing a modification. (A) is a plan view of an enlarged interval state, (b) is a cross-sectional view of (a), (c) is a plan view of a reduced interval state, (d) is (c) Cross section of

  An embodiment of the present invention will be described with reference to the drawings. 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 an oil pump 60.

  The bearing unit 20 includes three oil-lubricated rolling bearings 21, 22, 23 arranged in parallel inside the housing 11. By these rolling bearings 21, 22, and 23, the shaft member 32 communicating with the operation mechanism 30 of the oil pump 60 is rotatably supported around the axis with respect to the fixed housing 11.

  In each of the rolling bearings 21, 22, and 23, a rolling element 3 is incorporated between the respective raceway surfaces 1a and 2a of the outer race 1 and the inner race 2. The rolling element 3 is held in a circumferential direction by a holder 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 race 1 is press-fitted into the inner diameter surface of the housing 11 and is fixed to the housing 11 so as not to rotate relative thereto. The inner ring 2 is press-fitted to the outer periphery of the shaft member 32 and is fixed to the shaft member 32 so as not to rotate relative thereto.

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

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

  As shown in FIG. 1, one of the parallel rolling bearings 21, 22, and 23 in the axial direction, that is, the two rolling bearings 21 and 22 that are closer to the operation mechanism 30 are configured such that the small diameter side end faces of the tapered rollers are in the axial direction. Along the same side, that is, on the opposite side of the actuation mechanism 30.

  The other side in the axial direction of the parallel rolling bearings 21, 22, and 23, that is, the rolling bearing 23 farthest from the operation mechanism section 30 is arranged such that the small-diameter side end face of the tapered roller is on the operation mechanism section 30 side. ing. That is, the rolling bearings 21 and 22 and the rolling bearing 23 are arranged such that the small-diameter side end faces of the tapered rollers are back-to-back. For this reason, the raceway surface 2a of the inner race 2 and the raceway surface 1a of the outer race 1 are such that two of the three rows of rolling bearings 21, 22, 23 are arranged from one side in the axial direction to the other side. One of the other sides is provided so that the distance between them increases from one side in the axial direction toward 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 one axial side of the parallel rolling bearings 21, 22, 23, a spacer 5 that abuts the end faces of the inner rings 2, 2 on both sides on the inner diameter side has an outer diameter. On the side, spacers 6 that are in contact with the end surfaces of the outer races 1 and 1 on both sides are arranged.

  Further, between the two rolling bearings 22, 23 on the other side in the axial direction of the parallel rolling bearings 21, 22, 23, a spacer which 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 radial side, spacers 7 that are in contact with the end surfaces of the outer races 1 and 1 on both sides are arranged. In FIG. 1, the inner diameter spacer between the rolling bearings 22 and 23 is not shown, but along the circumferential direction of the rolling bearings 22 and 23, except for the opening on the outer diameter side of the lubricating oil circulation path 13 b. The spacer is arranged at the portion.

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

  The shaft member 32 supported by the housing 11 by the rolling bearings 21, 22, and 23 is connected to an operating mechanism 30 which is a rotating member in an oil pump 60 corresponding to a pump body for sending out oil. The oil pump 60 has a function of sending out the internal lubricating oil toward another external operating mechanism 70 by its driving. The sent lubricating oil flows along the path of the lubricating oil, lubricates the operating mechanism 70 of each part, and then returns to the oil pump 60.

  Further, in the oil pump 60, the operating mechanism 30 in the pump body and the bearing unit 20 supporting the shaft member 32 communicating with the operating mechanism 30 are lubricated with a common lubricating oil. ing. The operation mechanism unit 30 on the oil pump 60 side and the bearing space on the bearing unit 20 side include a side opening D of the bearing space on one axial side of the rolling bearing 21 on one axial side, and the lubricating oil circulation path 12. , 13. 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 13 b extending radially outward and opening to the outer peripheral surface of the shaft member 32 is provided. Since the radial lubrication path 13b is open to the annular space C sandwiched between the rolling bearings 22 and 23, the circulation path 13 passes through the annular space C to one side in the axial direction (left side in the figure). The bearings communicate with the bearing spaces of the rolling bearings 21 and 22, and communicate with the bearing space of the rolling bearing 23 to the other axial side (the right side in the figure).

  The lubricating oil that has passed through the bearing space of the rolling bearing 23 via the annular space C passes through an opening of the bearing space at the other axial end of the rolling bearing 23, and the lubricating oil is provided at the other axial end of the rolling bearing 23. It enters the space B. Thereafter, the oil returns to the operation mechanism 30 side of the oil pump 60 through the lubricating oil circulation path 12 formed in a portion of the housing 11 near the outer diameter.

  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 direction of the shaft member 32 from the radial lubrication path 12b. Prepare.

  Further, the lubricating oil that has passed through the bearing space of the rolling bearings 22 and 21 through the annular space C passes through the side opening D of the bearing space at one axial end side of the rolling bearing 21, and is disposed on the side of the operating mechanism 30 of the oil pump 60. Back to.

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

  Incidentally, foreign matters such as abrasion powder (iron powder and the like) may be generated from the bearing spaces of the rolling bearings 21, 22, and 23. It is not preferable that the foreign matter enters the operating mechanism 30 of the oil pump 60 or another operating mechanism 70 in the circulation path outside the pump. Therefore, the sealing member 40 (hereinafter, referred to as the opening) of the bearing space at the one end in the axial direction of the rolling bearing 21 and the opening 12c of the one end in the axial direction 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 at one axial end of the rolling bearing 21 and the opening 12c at one axial end of the circulation path 12. The lateral opening D of the bearing space at one axial end of the rolling bearing 21 is formed in an annular shape along the raceways 1a, 2a of the outer ring 1 and the inner ring 2, so that the seal ring 40 that covers it is also annular. It has become something.

  As shown in FIGS. 2 and 3, 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, 23, the spacers 5, 6, 7, and the like. You.

  As shown in FIG. 4, the seal ring 40 has a cylindrical portion 42 made of a cylindrical member whose cylindrical axial end surface 41 is in contact with an axial end surface 1 d of the outer race 1, and a cylindrical axial direction of the cylindrical portion 42. And a wall 43 rising from one end toward the inner diameter side.

  A filter 46 is provided on the wall 43. The filter 46 prevents the passage of foreign matter from the bearing spaces of the rolling bearings 21 and 22 by the collection of the filter holes 46a formed of through holes, and allows the passage of lubricating oil. At this time, if the inside diameter of the filter hole 46a is small, it is set to an appropriate size so that the passage of a foreign matter to such an extent that the foreign matter does not affect even if it enters the operation mechanism 30 side is allowed.

  In this embodiment, the seal ring 40 is made of a synthetic resin molded product. Further, the seal ring 40 is formed in 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 shape form a connecting piece 80. Are connected to each other in a ring. The divided seal members 40 ′ adjacent to each other 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 formed by the two divided seal members 40 ′ having a central angle of 180 °, the connecting pieces 80 are located at two places, the upper part and the lower part of the seal ring 40. ing.

  Further, the seal ring 40 is not limited to a two-part configuration using two split seal members 40 ′ having a central angle of 180 °, and is formed into an annular shape 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 °.

  Further, in this embodiment, the seal ring 40 has the hole 46 a for the filter 46 of the wall 43 formed integrally with the body of the seal ring 40. As a separate member from the member of the main body, the separate member may be fixed to the main body of the seal ring 40 by various means such as fitting, fixing, embedding and bonding.

  As the material of the seal ring 40 and the connecting piece 80, other materials such as metal and rubber may be adopted in addition to resin. When the filter 46 is a member separate 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 81 abutting on the outer peripheral surface of the cylindrical portion 42 of the seal ring 40 toward the rolling bearing 21.

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

  In this embodiment, the axial member 82 extends from one end in the axial direction to the other end in the circulation path 12, and the tip 82 a of the axial member 82 has a tapered shape. Therefore, 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 distal end of the axial member 82.

  The axial member 82 is in contact with the outer diameter surface of the outer ring 1, and the inner diameter side projection 83 enters a recess provided in the bearing ring or spacer of the bearing, whereby the axial movement of the seal ring 40 is regulated. You. In this embodiment, the inner diameter side protruding portion 83 is configured to enter into the concave portion 1c formed between the outer ring 1b and the spacer 6 of the rolling bearing 21. The concave portion 1 c is constituted by an end surface 6 a on one end side of the spacer 6, a curved rounded portion, a chamfered portion, and the like formed on the ridgeline of the shoulder of the outer ring 1 b of the rolling bearing 21.

  The opening 12c at one end in the axial direction of the circulation path 12 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 two openings 12c are provided at intervals of 180 ° along the circumferential direction. The number may be increased or decreased as needed.

  The connecting piece 80 includes an outer diameter side protruding portion 84 that protrudes inside the circulation path 12. The outer diameter side protruding portion 84 rises from the outer surface of the axial member 82 toward the outer diameter side, and has a convex portion 84a, a concave portion 84b, and an oil passage hole 84c on the outer diameter surface. The convex portion 84a abuts on the inner surface 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 provide lubrication from the circulation path 12 to the outside of the bearing space. It becomes an oil passage. Similarly, the gap between the concave portion 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 or slits may be provided in the outer-diameter-side protruding portion 84 to provide a filter for capturing foreign matter.

  The width (the width in the circumferential direction of the rolling bearing) of the axial member 82 and the outer diameter side projection 84 is set to the width of the circulation path 12 (the width in the circumferential direction of the rolling bearing) so that the axial member 82 and the outer diameter side projection 84 enter the circulation path 12 and are fixed without play. Similarly, the width in the circumferential direction of the rolling bearing). Thus, 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 and the outer-diameter-side protruding portion 84 function as rotation stopping 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 member along the outer diameter surface of the seal ring 40.

  As shown in FIGS. 6A and 6B, locking projections 88a and 88b are provided at the distal end of each support 85 as locking portions 88 protruding toward the inner diameter side. When the locking projections 88a and 88b enter the locking holes 48a and 48b, which are the locked portions 48 provided at the ends of the divided seal members 40 'that are adjacent in the circumferential direction, the connecting piece 80 is formed. The ends of the circumferentially adjacent divided seal members 40 'are connected to each other. As a result, the split seal member 40 'is formed into an annular connecting body.

  At this time, as shown in FIG. 6 (c), a retaining projection 89 that engages with the edges of the locking holes 48a, 48b may be provided at the tips of the locking projections 88a, 88b. If the retaining projection 89 is provided, it is possible to prevent the connection piece 80 from being separated from the divided seal member 40 '. The retaining projection can be provided on the side of the locking holes 48a and 48b. In this case, it is preferable to provide a retaining recess in which the retaining projection fits on the locking convex portions 88a and 88b.

  The locking portion 88 of the connecting piece 80 and the locked portion 48 of the split seal member 40 ′ are spaced from each other in the circumferential direction between the connecting portions of the circumferentially adjacent split seal members 40 ′ and the connecting piece 80. Function as an interval adjusting means that can adjust. That is, the gap adjusting means is configured to provide a circumferential gap between the connecting portion between one of the opposing split seal members 40 ′ and the connecting piece 80 and the connecting portion between the other split seal member 40 ′ and the connecting piece 80. Can be adjusted.

  As shown in FIGS. 7A and 7B, locking holes 48a and 48b are provided as locked portions 48 at the circumferential ends of the opposed divided seal members 40 ', respectively. The stop holes 48 a and 48 b have a plurality of connection portions with the locking portions 88 along the circumferential direction of the seal ring 40. As shown in the figure, since the locking projections 88a and 88b constituting the locking portion 88 are cylindrical and have a circular cross section, the locking holes 48a and 48b have the locking projections 88a and 88b having the circular cross section. Are provided at a plurality of locations along the circumferential direction of the seal ring 40 (four locations of A, B, C, D, and A ', B', C ', D' in the figure). .

  For this reason, the locking projections 88a, 88b of the connecting piece 80 are replaced with the connecting portions A, B, C, D; A ', B', C 'of the locking holes 48a, 48b of the split seal member 40'. , D ′, the connection interval in the circumferential direction between the divided seal members 40 ′ can be adjusted.

  In FIGS. 7A and 7B, the locking projections 88a and 88b provided on the connecting piece 80 are respectively connected to the connection portions D and D 'closest to the ends of the locking holes 48a and 48b provided in the divided seal member 40'. In this case, the connection distance between the divided seal members 40 'in the circumferential direction is widened as w1. Thereby, the last clearance w between the inner diameter side end of the wall 43 of the seal ring 40 and the outer diameter surface of the inner ring 2 is set relatively wide.

  In FIGS. 7C and 7D, the locking projections 88a and 88b provided on the connecting piece 80 are respectively connected to the connection portions A and A 'furthest from the ends of the locking holes 48a and 48b provided in the split seal member 40'. In this way, the connection distance between the divided seal members 40 'in the circumferential direction is narrowed as w2. Thereby, the last clearance w between the inner diameter side end of the wall 43 of the seal ring 40 and the outer diameter surface of the inner ring 2 is set relatively small.

  At this time, as shown in FIGS. 6A and 6B, the wall portions 43 of the divided seal members 40 'adjacent to each other in the circumferential direction are provided with key-shaped portions 47a and 47b which mesh with each other. Therefore, the key-shaped portions 47a and 47b facing each other mesh with each other, so that the connection between the divided seal members 40 'is further strengthened. Also, irrespective of the state of the distance between the connecting portions of the divided seal members 40 ', harmful foreign substances flow out between the key portions 47a and 47b, that is, between the wall portions 43. It is possible to prevent a gap from being generated.

  Such a key portion may be provided also in the cylindrical portion 42. That is, the cylindrical portions 42 of the divided seal members 40 ′ adjacent to each other in the circumferential direction are provided with the key-shaped portions that mesh with each other, so that the distance between the connection portions of the divided seal members 40 ′ is any state. In addition, it is possible to prevent a gap from flowing out of a harmful foreign substance between the key-shaped portions, that is, between the cylindrical portions.

  However, in this embodiment, a gap between the cylindrical portions 42 of the divided seal members 40 ′ adjacent in the circumferential direction is formed by the notch 49 provided at the circumferential end of the divided seal member 40 ′. Since the gap formed by the notch 49 is closed by the base 81 of the connecting piece 80, it is possible to omit the provision of the above-described key-shaped portion in the cylindrical portion.

  The diameter of the seal ring 40 is adjusted by adjusting the interval in the circumferential direction between the connection portions between the divided seal members 40 ′ adjacent to each other in the circumferential direction and the connecting piece 80 by the interval adjusting means. Thereby, the last clearance w between the inner diameter side end of the wall portion 43 of the seal ring 40 and the outer diameter surface of the inner ring 2 can be adjusted and managed to an appropriate size.

  The size of the last clearance w is allowed to pass through the lubricating oil as in the case of the inner diameter of the hole 46a of the filter 46, but the passage of foreign matters exceeding that size is prevented. For this reason, the last clearance w between the inner diameter side end of the wall 43 and the outer diameter surface of the inner ring 2 is set to be equal to or smaller than the mesh size of the filter 46.

  In the above embodiment, the locking portion 88 is a convex portion, and the locked portion 48 is a concave portion in which the convex portion is fitted. However, the locking portion and the locked portion are other than the combination of the convex portion and the concave portion. You may comprise.

  Further, in the above-described embodiment, the gap adjusting means is constituted by the locking portion 88 provided on the connecting piece 80 and the locked portion 48 provided on the divided seal member 40 ′. Although the split seal member 40 'is provided with a plurality of connecting portions along the circumferential direction on the divided seal member 40', the locking portion 88 and the locked portion 48 may be arranged in reverse. .

  That is, the gap adjusting means is constituted by a locking portion provided on the divided seal member 40 ′ and a locked portion provided on the connecting piece 80 and locked by the locking portion. This is a configuration in which a plurality of pieces are provided along the circumferential direction. The locking portion of the split seal member 40 ′ can be configured with, for example, a convex portion, and the locked portion of the connecting piece 80 can be configured with, for example, a concave portion into which the convex portion fits.

  Also, by preparing connecting pieces 80 having different intervals between the pair of locking portions 88 and using a plurality of types of connecting pieces 80, the connection between each of the divided seal members 40 ′ adjacent to each other in the circumferential direction and the connecting pieces 80 can be achieved. It is also possible to use an interval adjusting means that can adjust the interval in the circumferential direction between the parts. That is, if the connecting piece 80 having a long distance between the pair of locking portions 88 is used, the distance between the connecting portions of the divided seal members 40 ′ adjacent to each other in the circumferential direction is long, and the distance between the pair of locking portions 88 is short. If the piece 80 is used, the interval between the connection portions of the divided seal members 40 ′ adjacent in the circumferential direction can be shortened.

  As described above, the lubricating oil from the bearing spaces of the rolling bearings 21, 22, and 23 has the gap 46 a of the filter 46 provided in the seal ring 40, the hole or gap in the circulation path 12, or the interval of the last clearance. The gas flows out of the bearing space through the gap w between the managed inner diameter end of the wall 43 and the outer diameter surface of the inner ring 2. For this reason, a large foreign substance (abrasion powder made of metal, in particular, a stripped piece, etc.) that affects the operation of the operation mechanism units 30 and 70 does not enter the operation mechanism units 30 and 70 side.

  In each of the above embodiments, a sensor unit for detecting the adhesion of foreign matter such as metal powder may be provided around the hole 46a 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 object by the presence of a foreign object between a pair of electrodes and a change in an electrical output when the foreign object short-circuits between the electrodes. it can.

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

  The seal member of the present invention can be applied to various rolling bearing units other than the embodiment. Further, the rolling bearing unit provided with the seal member can be applied to various devices other than the oil pump 60. In particular, the rolling bearing according to the present invention is required to prevent foreign matter such as abrasion powder (iron powder or the like) generated from the rolling bearing from entering the operating mechanism 70 in the middle of the lubricating oil circulation path. Applicable to equipment.

1 outer ring (outer race)
2 Inner ring (inner race)
Reference Signs List 3 Rolling element 4 Cage 5, 6, 7 Spacer 8 Holding member 10 Oil pump device 11 Housing 12, 13 Circulation path 20 Bearing unit 21, 22, 23 Rolling bearing 30 Operating mechanism 31 Connection member 32 Shaft member 40 Seal ring (Seal member)
40 'Split seal member 46 Filters 47a, 47b Key-shaped portion 48 Locked portions 48a, 48b Lock hole 49 Notch 60 Oil pump 70 Operating mechanism 80 Connecting piece 81 Base 82 Axial member 83 Inner projection 84 Outside Diameter side protruding part 85 Support part 88 Locking parts 88a, 88b Locking convex part 89 Projection for retaining

Claims (7)

Outer ring and inner ring,
A rolling element disposed in a bearing space between the outer ring and the inner ring;
An annular seal member attached to the outer ring or a member fixed to the outer ring and covering a side opening of the bearing space;
With
The seal member has a plurality of divided seal members divided along the circumferential direction connected by a connection piece to form an annular connection body,
A rolling bearing unit including a gap adjusting means that can adjust a gap in a circumferential direction between a connecting portion between each of the divided seal members and the connecting piece that are adjacent to each other in a circumferential direction. The interval adjusting means includes a locking portion provided on the connecting piece, and a locked portion provided on the divided seal member and locked by the locking portion,
The rolling bearing unit according to claim 1, wherein a plurality of the locked parts are provided along a circumferential direction at a circumferential end of the divided seal member. The gap adjusting means includes a locking portion provided on the divided seal member, and a locked portion provided on the connecting piece and locked by the locking portion,
The rolling bearing unit according to claim 1, wherein a plurality of the locked portions are provided on the connecting piece along a circumferential direction. 4. The rolling bearing unit according to claim 2, wherein one of the locking portion and the locked portion is a convex portion, and the other is a concave portion into which one fits. 5. 5. The rolling bearing unit according to claim 4, wherein the protrusion or the recess is provided with a retaining projection for preventing the protrusion from coming out of the recess. The seal member includes a cylindrical portion that abuts on an end surface of the outer ring, and a wall portion that rises from one end of the cylindrical portion in the cylinder axis direction toward the inner diameter side,
The rolling bearing unit according to any one of claims 1 to 5, wherein each of the divided seal members that are adjacent in the circumferential direction includes a key-like portion that meshes with the opposing wall portion or the opposing cylindrical portion. The seal member includes a cylindrical portion that abuts on an end surface of the outer ring, and a wall portion that rises from one end of the cylindrical portion in the cylinder axis direction toward the inner diameter side,
The rolling bearing unit according to any one of claims 1 to 5, wherein a gap between circumferential ends of the cylindrical portions facing each other in the circumferentially adjacent divided seal members is closed by the connecting piece.

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