JP2007064465A - Rotation transmission device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent a lubricating oil sealed in a housing from leaking to the outside in a rotation transmission device in which a wet multi-disc clutch controlled by a clutch controller is installed between an outer ring assembled in the housing and an inner ring assembled on the inside of the outer ring. <P>SOLUTION: The outer ring 3 is rotatably supported by a bearing 4 assembled in the opening end part of the housing 1, and the wet multi-disc clutch 30 is installed between the outer ring 3 and the inner ring 13 assembled on the inside of the outer ring. The clutch controller 40 controlling the engagement and the disengagement of the wet multi-disc clutch 30 is installed on the axial one side of the wet multi-disc clutch 30. A seal space 6 is formed at the outer end of the bearing 4 rotatably supporting the outer ring 3, and an oil seal 9 is assembled in the seal space 6. Consequently, even if the oil in the outer ring 3 flows into an annular space 12 formed between the outer ring 3 and the housing 1 by a centrifugal force and the pressure therein is increased, the oil is prevented from leaking to the outside by the oil seal 9 assembled in the seal space 6. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a rotation transmission device used for switching between power transmission and cutoff on a power transmission path.

  In an FR-based four-wheel drive vehicle, a rotation transmission device described in Patent Document 1 is conventionally known as a rotation transmission device that transmits and blocks driving force to a front wheel as an auxiliary driving wheel.

  The rotation transmission device rotatably supports an input member to which a driving force from a transmission is input by a bearing incorporated in an opening end portion of the housing, and an output member is incorporated in the input member and is relatively supported by the bearing. A wet multi-plate clutch that couples the input member and the output member with a loaded axial force is incorporated between the input member and the output member, and on one side in the axial direction of the wet multi-plate clutch, A clutch control device for controlling the coupling and decoupling of the wet multi-plate clutch is provided.

  Here, the clutch control device includes an electromagnetic clutch unit, and an axial force load unit that converts the rotational torque of the input member into an axial force when the electromagnetic clutch unit is engaged, and loads the axial force on the wet multi-plate clutch. The electromagnetic clutch portion includes an armature that is guided by the inner diameter surface of the input member and is movable in the axial direction, a rotor that is attached to the input member and faces the armature in the axial direction, and faces the rotor in the axial direction. The armature is attracted to the rotor by energizing the electromagnetic coil of the electromagnet to couple the input member and the armature.

  On the other hand, the axial force load section incorporates a pressure plate between the armature and the wet multi-plate clutch, prevents the pressure plate from rotating around the output member, and supports it so that it can move in the axial direction. The opposing surface of the pressure plate and the armature Each cam groove is provided with a groove depth that gradually decreases from the center toward both ends in the circumferential direction. Balls are assembled between the cam grooves, and the pressure plate is moved in the axial direction by the relative rotation of the armature with respect to the pressure plate. An axial force is applied to the multi-plate clutch.

  In the rotation transmission device, in order to lubricate each contact portion of the wet multi-plate clutch and the electromagnetic clutch portion and the axial load portion with the oil enclosed in the housing, to prevent the lubricating oil from leaking to the outside, A seal is incorporated in a bearing that rotatably supports the input member to seal the open end of the housing, a seal groove is formed on the bearing press-fitting surface of the input member, and an O-ring is incorporated in the seal groove. The gap between the press-fitting surface and the fitting surface of the bearing is sealed.

In addition, a seal is incorporated in a bearing that rotatably supports the input member and the output member to seal between the input member and the output member, and a seal groove is formed on the bearing press-fitting surface of the input member. An O-ring is incorporated into the bearing to seal between the bearing press-fit surface and the fitting surface of the bearing.
JP 2005-48788 A

  By the way, in the rotation transmission device as described above, when the input member is rotated at a high speed, oil flows into an annular space formed between the input member and the housing by centrifugal force, and the pressure rises. At this time, in the conventional rotation transmission device, the seal is incorporated in the bearing that supports the outer ring to seal the opening of the annular space, but it is difficult to ensure the sealing performance with the degree of sealing in the bearing, Oil may leak to the outside.

  Further, since the bearing press-fitting surface and the fitting surface of the bearing are sealed by the O-ring, there is a disadvantage that the O-ring hinders the assembly of the bearing and the assembling property is poor.

  An object of the present invention is to provide a rotation transmission device capable of reliably preventing leakage of lubricating oil to the outside.

  In order to solve the above-mentioned problems, in the first invention, a bearing is fitted into an open end of a housing that is open at one end and closed at the other end, and the outer ring incorporated in the housing is rotated by the bearing. The bearing is incorporated between one end of the outer ring and the inner ring incorporated in the outer ring, and is supported relatively rotatably. By the axial force applied between the outer ring and the inner ring, A wet multi-plate clutch for coupling the outer ring and the inner ring is incorporated, and a clutch control device for controlling the coupling and release of the wet multi-plate clutch is provided on one side in the axial direction of the wet multi-plate clutch. An electromagnetic clutch that attracts the armature to the rotor attached to the outer ring by energizing the electromagnet, and converts the rotational torque of the outer ring into an axial force when the armature is attracted. A rotation transmission device comprising an axial force load portion loaded on a clutch, wherein each contact portion of the axial force load portion, the wet multi-plate clutch and the electromagnetic clutch portion is lubricated with oil sealed in a housing; Among the outer end side of the bearing that supports the outer ring and the outer end side of the bearing that relatively rotatably supports the outer ring and the inner ring, at least the outer end side of the outer ring support bearing, the outer diameter side is a seal press-fitting surface. Thus, a configuration was adopted in which a seal space having an inner diameter side as a seal surface was formed, and an oil seal was incorporated in the seal space.

  In the second aspect of the invention, a bearing is fitted into the open end of the housing that is open at one end and closed at the other end, and the outer ring incorporated in the housing is rotatably supported by the bearing. A bearing is incorporated between one end of the inner ring incorporated in the outer ring and the inner ring is relatively rotatably supported, and the outer ring and the inner ring are coupled between the outer ring and the inner ring by a loaded axial force. A wet multi-plate clutch is incorporated, and a clutch control device for controlling the coupling and decoupling of the wet multi-plate clutch is provided on one side in the axial direction of the wet multi-plate clutch. The clutch control device is attached to the outer ring by energizing the electromagnet. An electromagnetic clutch portion that attracts the armature to the attached rotor, and a shaft that converts the rotational torque of the outer ring into an axial force when the armature is attracted and loads the axial force on the wet multi-plate clutch A bearing for supporting the outer ring in a rotation transmission device comprising a load portion, wherein each contact portion of the axial force load portion, the wet multi-plate clutch and the electromagnetic clutch portion is lubricated with oil sealed in a housing The outer end side of the outer ring and the outer end side of the bearing that relatively rotatably supports the outer ring and the inner ring, at least on the outer end side of the outer ring support bearing, the outer diameter side is a seal press-fitting surface, and the inner diameter side is a seal surface An elastic seal in which an outer diameter portion is press-fitted into the seal press-fitting surface, and an L-shaped slinger that is press-fitted into the seal surface. The inward radial lip and the outward radial lip formed on the inner diameter portion of the elastic seal are in elastic contact with the outer diameter surface of the cylindrical portion of the slinger and are formed on the outer surface of the elastic seal. Rip it had adopted a configuration in which are elastically in contact with the inner surface of the outward flange of the slinger.

  In the rotation transmission device according to the first aspect of the present invention, when the outer diameter of the seal surface is smaller than the outer diameter of the bearing press-fit surface formed on the inner end side of the seal surface, when the bearing is pressed into the bearing press-fit surface, It is possible to prevent the sealing surface from being damaged, and it is possible to ensure good sealing performance by contact of the oil seal with the sealing surface.

  As described above, in the first invention, since the seal space is formed on the outer end side of the outer ring support bearing and the oil seal is incorporated in the seal space, the oil in the outer ring is separated from the housing by centrifugal force. Even if it moves into the annular space formed between the outer rings and the pressure in the annular space increases, the oil seal can reliably prevent the oil from leaking to the outside.

  In addition, since it is not necessary to seal between the bearing press-fit surface and the fitting surface of the bearing with an O-ring by incorporating an oil seal, the assembly of the bearing can be facilitated.

  In the rotation transmission device according to the second invention, a cylindrical portion of a slinger in which a seal space is formed on the outer end side of the outer ring support bearing, and two radial lips of an elastic seal are press-fitted into the seal surface in the seal space. Incorporating a seal with elastic contact with the outer diameter surface and with the side lip provided on the outer surface of the elastic seal in contact with the inner surface of the outward flange of the slinger, the oil is released to the outside by the elastic seal. Leakage can be prevented more reliably.

  Moreover, since the elastic seal can be protected by the slinger by press-fitting the sealer into the seal surface, it is possible to prevent the elastic seal from being damaged by the collision of foreign matter such as pebbles, and muddy water etc. Can be prevented from entering.

  Embodiments of the present invention will be described below with reference to the drawings. As shown in FIG. 1, a housing 1 that is fixedly arranged has a cylindrical shape, one end of which is open and the other end is closed by an end wall 2.

  An outer ring 3 is incorporated in the housing 1. The outer ring 3 is rotatably supported by a bearing 4 incorporated in the open end of the housing 1. Reference numeral 5 denotes a bearing press-fitting surface formed on the outer periphery of the outer ring 3.

  As shown in FIG. 4, a seal space 6 is provided on the outer end side of the bearing 4, the outer diameter side of the seal space 6 is a seal press-fitting surface 7, and the inner diameter side is a seal surface 8. An oil seal 9 is incorporated in the seal space 6. The outer surface of the oil seal 9 is press-fitted into the seal press-fitting surface 7, and an elastic seal piece 9 a provided on the inner diameter portion is pressed against the seal surface 8 by its own elasticity and tightening of the garter spring 10. The seal space 6 is hermetically sealed by incorporating the oil seal 9.

  The seal surface 8 with which the seal piece 9 a of the oil seal 9 is elastically contacted has an outer diameter smaller than the outer diameter of the bearing press-fit surface 5 so as not to be damaged by the bearing 4 press-fitted into the bearing press-fit surface 5.

  As shown in FIG. 1, the first shaft 11 is inserted into one end of the outer ring 3. The first shaft 11 is locked to the outer ring 3 via a serration 12.

  An inner ring 13 is incorporated inside the outer ring 3, and the inner ring 13 and the outer ring 3 are relatively rotatable by a bearing 14 incorporated between one end portions of both wheels. Here, a sealed bearing is employed as the bearing 14, and the end portion of the outer ring 3 and the inner ring 13 is sealed by the sealed bearing 14. Further, a ring groove 25 is formed on the seal bearing press-fitting surface of the outer ring 3, and a space between the fitting surfaces of the outer ring 3 and the seal bearing 14 is sealed by a seal ring 26 incorporated in the ring groove 25.

  A second shaft 15 is inserted inside the inner ring 13. The second shaft 15 is locked to the inner ring 13 by a serration 16.

  The second shaft 15 is inserted into a shaft insertion hole 17 formed in the end wall 2. The shaft insertion hole 17 has a bearing fitting hole 17a on the outer side, and the second shaft 15 is rotatably supported by a bearing 18 incorporated in the bearing fitting hole 17a.

  Further, a seal fitting hole 17b is formed in the inner portion of the shaft insertion hole 17, and the oil seal 19 press-fitted into the seal fitting hole 17b is brought into elastic contact with the outer diameter surface of the second shaft 15 so that the outer ring The oil sealed in 3 is prevented from leaking from the shaft insertion hole 17. On the other hand, an oil seal 20 is incorporated in the end portion of the inner ring 13, and the inner diameter portion of the oil seal 20 is in elastic contact with the outer diameter surface of the tip end portion of the second shaft 15, so that the oil in the outer ring 3 is discharged from the inner ring 13. Prevents leakage to the outside.

  A wet multi-plate clutch 30 is incorporated between the outer ring 3 and the inner ring 13. The wet multi-plate clutch 30 includes a large number of outer clutch plates 31 and a large number of inner clutch plates 32. The outer clutch plate 31 and the inner clutch plate 32 are alternately assembled in the axial direction, and the outer clutch plate 31 is supported with respect to the outer ring 3 so as to be movable in the axial direction. On the other hand, the inner clutch plate 32 is supported by the inner ring 13 so as to be movable in the axial direction.

  The outer clutch plate 31 and the inner clutch plate 32 are brought into close contact with each other by a loaded axial force and are connected to each other, and transmit rotational torque between the outer ring 3 and the inner ring 13.

  On one side in the axial direction of the wet multi-plate clutch 30, a clutch control device 40 that controls the coupling and decoupling of the wet multi-plate clutch 30 is provided.

  The clutch control device 40 includes an electromagnetic clutch portion 40A and an axial force load portion 40B that converts the rotational torque of the outer ring 3 into an axial force and loads the wet multi-plate clutch 30 when the electromagnetic clutch portion 40A is engaged.

  The electromagnetic clutch portion 40 </ b> A includes an armature 41, a rotor 42 provided on one side of the armature 41, and an electromagnet 43 provided on one side of the rotor 42.

  The armature 41 is guided by the inner surface of the outer ring 3 and is movable in the axial direction.

  The rotor 42 has an outer cylinder part 42a and an inner cylinder part 42b, and a male screw 44 is formed on the outer periphery of the outer cylinder part 42a. The rotor 42 is fixed to the outer ring 3 by screwing a male screw 44 into a female screw 45 formed on the inner periphery of one end of the outer ring 3, and is loosened by tightening a lock nut 46 that is screw-engaged with the female screw 45. A minute air gap 47 is formed between the rotor 42 and the armature 41, and the air gap 47 can be adjusted by adjusting the screwing amount of the rotor 42. A separation spring 48 that urges the armature 41 in a direction away from the rotor 42 is incorporated between the rotor 42 and the armature 41.

  The electromagnet 43 is incorporated between the outer cylinder part 42a and the inner cylinder part 42b of the rotor 42. The electromagnet 43 includes an electromagnetic coil 43 a and a core 43 b that supports the electromagnetic coil 43 a and is supported by the housing 1. Magnetic flux flows through the core 43 b, the rotor 42, and the armature 41 when the electromagnetic coil 43 a is energized. Thus, the armature 41 is adsorbed to the rotor 42. By the adsorption, the armature 41 is coupled to the outer ring 3, and the armature 41 rotates together with the outer ring 3.

  As shown in FIGS. 1 to 3, the axial force load portion 40 </ b> B is provided with a pressure plate 51 between the armature 41 and the wet multi-plate clutch 30, and prevents the pressure plate 51 from rotating around the inner ring 13, and the axial direction The ball cam 52 is provided between the opposing surfaces of the pressure plate 51 and the armature 41. Here, the ball cam 52 is provided with cam grooves 52a and 52b in which the groove depth gradually decreases from the center to both ends in the circumferential direction on the opposing surfaces of the pressure plate 51 and the armature 41, and the ball cam 52 is provided between the cam grooves 52a and 52b. 53, and the armature 41 is rotated relative to the pressure plate 51 to move the pressure plate 51 toward the wet multi-plate clutch 30 to push the wet multi-plate clutch 30 in the axial direction. .

  Oil is sealed inside the housing 1. The oil lubricates the contact portion of the outer clutch plate 31 and the inner clutch plate 32 of the wet multi-plate clutch 30, the contact portion of the rotor 42 and the armature 41 of the electromagnetic clutch portion 40A, and the contact portion of the ball cam 52 of the axial force load portion 40B.

  The rotation transmission device shown in the embodiment has the above-described structure, and FIG. 1 shows a state in which the energization is interrupted with respect to the electromagnetic coil 43a of the electromagnet 43, and the wet multi-plate clutch 30 is in a disengaged state. For this reason, even if the outer ring 3 rotates, the rotation is not transmitted to the inner ring 13, and only the outer ring 3 rotates freely.

  When the electromagnetic coil 43a of the electromagnet 43 is energized in the rotating state of the outer ring 3, magnetic flux flows through the core 43b, the rotor 42, and the armature 41, and a magnetic attractive force acts between the rotor 42 and the armature 41. 41 is attracted to the rotor 42, the outer ring 3 and the armature 41 are coupled, and the armature 41 rotates together with the outer ring 3.

  Further, the armature 41 rotates relative to the pressure plate 51, and by the relative rotation, as shown in FIG. 3 (II), the cam groove 52b formed in the armature 41 and the cam groove 52a formed in the pressure plate 51. However, the pressure plate 51 moves to the wet multi-plate clutch 30 side and presses the wet multi-plate clutch 30 in the axial direction. The outer clutch plate 31 and the inner clutch plate 32 are brought into close contact with each other by the pressing.

  Therefore, the rotation of the outer ring 3 is transmitted to the inner ring 13 via the wet multi-plate clutch 30, and the inner ring 13 rotates in the same direction as the outer ring 3.

  Here, when the pressure plate 51 presses the wet multi-plate clutch 30 in the axial direction, the armature 41 is pressed against the rotor 42 by the reaction force. Therefore, once the electromagnetic clutch portion 40A is fastened, the subsequent electromagnetic coil Even if the current passed through 43a is reduced, the armature 41 is held in the attracted state, and the current consumption can be reduced.

  In a state where rotational torque is transmitted from the outer ring 3 to the inner ring 13, when the energization of the electromagnetic coil 43a is released, the armature 41 is released from the suction. When releasing the suction, the separation spring 48 presses the armature 41 toward the pressure plate 51 and the pressure plate 51 is pressed from the wet multi-plate clutch 30, so that the cam grooves 52 a and 52 b press the ball 53. The armature 41 and the pressure plate 51 rotate relative to each other, and the ball 53 is returned to the neutral position arranged at the center of the cam grooves 52a and 52b (FIG. 3I).

  For this reason, the load of the axial force on the wet multi-plate clutch 30 is released, and the wet multi-plate clutch 30 is brought into a disengaged state, and transmission of rotational torque from the outer ring 3 to the inner ring 13 is cut off.

  In the free rotation state of the outer ring 3, the contact portions of the wet multi-plate clutch 30, the electromagnetic clutch portion 40 </ b> A, and the axial force load portion 40 </ b> B are lubricated by oil sealed in the housing 1.

  When the rotation speed of the outer ring 3 becomes high, the oil flows to the outer peripheral portion in the outer ring 3 by centrifugal force. At this time, the inner space of the outer ring 3 and the annular space 21 formed between the outer diameter surface of the outer ring 3 and the inner diameter surface of the housing 1 communicate with each other via a slit 42 c formed in the rotor 42. The oil that has flowed to the outer periphery of the gas flows into the annular space 21, and the pressure in the annular space 21 increases.

  The annular space 21 is normally sealed at the opening end of the housing 1, but if the sealing is incomplete, oil leaks to the outside.

  However, in the embodiment, the seal space 6 is formed on the outer end side of the bearing 4 that supports the outer ring 3, and the oil seal 9 is incorporated in the seal space 6 to seal the seal space 6. , Leakage of oil to the outside can be reliably prevented.

  Further, since the seal space 6 is sealed by the oil seal 9, it is not necessary to seal between the fitting surfaces of the bearing 4 and the bearing press-fitting surface 5 with an O-ring or the like. Therefore, the bearing 4 can be easily incorporated into the bearing press-fitting surface 5. be able to.

  Further, by making the outer diameter of the seal surface 8 smaller than the outer diameter of the bearing press-fitting surface 5, the seal surface 8 is not damaged when the bearing 4 is press-fitted into the bearing press-fitting surface 5. For this reason, good sealing performance can be ensured by the contact of the oil seal 9 with the seal surface 8.

  In the embodiment shown in FIG. 1, the bearing 14 that rotatably supports the outer ring 3 and the inner ring 13 is used as a seal bearing, and the one end portion of the outer ring 3 and the inner ring 13 is sealed. Similarly, a seal space having an outer diameter side as a seal press-fitting surface and an inner diameter side as a seal surface is formed on the outer end side of the bearing 14, and an oil seal is incorporated in the seal space to seal the seal space. It may be.

  FIG. 5 shows another example of a sealing means for sealing the seal space 6. In this example, the seal space 6 is sealed with a seal S. The seal S is reinforced by a metal core 23, and includes an elastic seal 22 having an outer diameter surface press-fitted into the seal press-fitting surface 7, and a slinger 24 having an L-shaped cross section that is press-fitted into the seal surface 8 on the inner diameter side of the seal space 6. The inward radial lip 22 a and the outward radial lip 22 b provided on the inner diameter portion of the elastic seal 22 are in elastic contact with the outer diameter surface of the cylindrical portion 24 a of the slinger 24, and on the outer surface of the elastic seal 22. The provided side lip 22 c is in elastic contact with the inner surface of the outward flange 24 b of the slinger 24.

  In the sealing means, the three lips 22a, 22b and 22c provided on the elastic seal 22 are in elastic contact with the cylindrical portion 24a and the outward flange 24b of the slinger 24, so that the oil sealed in the outer ring 3 is removed. Leakage to the outside can be prevented more reliably, and mud etc. can be prevented from entering the inside by the slinger 24.

  In the embodiment, rotational torque is input to the outer ring 3, and the rotational torque is transmitted to the inner ring 13 and output from the inner ring 13. However, the rotational torque is input to the inner ring 13 and transmitted to the outer ring 3. You may make it output from the outer ring | wheel 3.

Cross-sectional plan view showing an embodiment of a rotation transmission device according to the present invention Sectional view along the line II-II in FIG. (I) is a cross-sectional view showing an axial force load portion, (II) is a cross-sectional view showing a state when an axial force is generated 1 is an enlarged cross-sectional view of the oil seal assembly shown in FIG. Sectional drawing which shows the other example of a sealing means

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Housing 3 Outer ring 4 Bearing 6 Seal space 7 Seal press-fit surface 8 Seal surface 13 Inner ring 14 Bearing 22 Elastic seal 22a Inward radial lip 22b Outward radial lip 22c Side lip 24a Cylindrical part 30 Wet multi-plate clutch 40 Clutch control device 40A Electromagnetic Clutch part 40B Axial force load part 41 Armature 42 Rotor

Claims (3)

A bearing is fitted in the open end of the housing with one end open and the other end closed, and the outer ring incorporated in the housing is rotatably supported by the bearing, and the outer ring and the inner ring incorporated in the outer ring. A wet multi-plate clutch is incorporated between the outer ring and the inner ring to couple the outer ring and the inner ring by a loaded axial force. A clutch control device that controls the coupling and decoupling of the wet multi-plate clutch is provided on one side of the multi-plate clutch in the axial direction, and the clutch control device attracts the armature to the rotor attached to the outer ring by energizing the electromagnet. The electromagnetic clutch unit and an axial force load unit that converts the rotational torque of the outer ring into an axial force when the armature is attracted and loads the axial force on the wet multi-plate clutch, and the axial force Load unit, the rotation transmitting device that the respective contact portions of the wet multiple disk clutch and an electromagnetic clutch and so lubricated with oil sealed in the housing,
Among the outer end side of the bearing that supports the outer ring and the outer end side of the bearing that relatively rotatably supports the outer ring and the inner ring, at least the outer end side of the outer ring support bearing, the outer diameter side is a seal press-fitting surface. A rotation transmission device characterized in that a seal space having an inner diameter side as a seal surface is formed, and an oil seal is incorporated in the seal space.   The rotation transmission device according to claim 1, wherein an outer diameter of the seal surface is smaller than an outer diameter of a bearing press-fitting surface formed on an inner end side of the seal surface. A bearing is fitted in the open end of the housing with one end open and the other end closed, and the outer ring incorporated in the housing is rotatably supported by the bearing, and the outer ring and the inner ring incorporated in the outer ring. A wet multi-plate clutch is incorporated between the outer ring and the inner ring to couple the outer ring and the inner ring by a loaded axial force. A clutch control device that controls the coupling and decoupling of the wet multi-plate clutch is provided on one side of the multi-plate clutch in the axial direction, and the clutch control device attracts the armature to the rotor attached to the outer ring by energizing the electromagnet. The electromagnetic clutch unit and an axial force load unit that converts the rotational torque of the outer ring into an axial force when the armature is attracted and loads the axial force on the wet multi-plate clutch, and the axial force Load unit, the rotation transmitting device that the respective contact portions of the wet multiple disk clutch and an electromagnetic clutch and so lubricated with oil sealed in the housing,
Among the outer end side of the bearing that supports the outer ring and the outer end side of the bearing that relatively rotatably supports the outer ring and the inner ring, at least the outer end side of the outer ring support bearing, the outer diameter side is a seal press-fitting surface. Forming a seal space having an inner diameter side as a seal surface, incorporating the seal into the seal space, the seal being press-fitted into the seal press-fit surface, and an elastic seal with an outer diameter portion press-fitted into the seal press-fit surface The inward radial lip and the outward radial lip formed on the inner diameter portion of the elastic seal are in elastic contact with the outer diameter surface of the cylindrical portion of the slinger and formed on the outer surface of the elastic seal. A rotation transmission device characterized in that the side lip formed is brought into elastic contact with the inner surface of the outward flange of the slinger.

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