JP2013053695A - Driving force transmission device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a driving force transmission device in which a lubricating oil is supplied to a bearing in a housing and discharged out of the housing.SOLUTION: The driving force transmission device 1 includes: the cylindrical housing 12 rotated by a driving source of a four-wheel drive vehicle; and an inner shaft 13 supported in a relatively rotatable manner via a needle-like roller bearing 33 in the housing 12, and coupled to the housing 12 via a clutch 8. The inner shaft 13 includes a pump forming part 36a of which an outer peripheral surface and an inner peripheral surface of the housing 12 form a pump therebetween and which supplies the lubricating oil to the needle-like roller bearing 33.

Description

  The present invention relates to a driving force transmission device that transmits a driving force from an input shaft in an automobile to an output shaft, for example.

  As a conventional driving force transmission device, there is one that is mounted on, for example, a four-wheel drive vehicle and connects a pair of rotating members so that torque can be transmitted by a clutch (see, for example, Patent Document 1).

  The driving force transmission device includes a first rotating member that rotates together with an input shaft, a second rotating member that can rotate on the axis of the first rotating member, and the second rotating member and the first rotating member. A friction type first clutch that couples the members so as to transmit torque, an electromagnetic clutch that is parallel to the first clutch along the axes of the first rotating member and the second rotating member, A friction-type second clutch driven by receiving electromagnetic force, and a cam mechanism that converts a rotational force from the first rotating member into a pressing force toward the first clutch by a clutch operation of the second clutch. It consists of and.

  The first rotating member includes a bottomed cylindrical front housing that opens to one side, and an annular rear housing that is attached to the opening of the housing, and is connected to the input shaft. The first rotating member is configured to rotate by receiving a driving force of a driving source such as a vehicle engine from an input shaft.

  The second rotating member is arranged to be rotatable relative to the first rotating member on the rotation axis, and is connected to the output shaft.

  The first clutch has an inner clutch plate and an outer clutch plate, and is disposed between the first rotating member and the second rotating member. The first clutch functions as a main clutch, and the inner clutch plate and the outer clutch plate are frictionally engaged to connect the first rotating member and the second rotating member so as to transmit torque. Has been.

  The electromagnetic clutch is disposed on the axis of the first rotating member and the second rotating member. The electromagnetic clutch is configured to generate an electromagnetic force to drive the second clutch.

  The second clutch has an inner clutch plate and an outer clutch plate, and is disposed on the electromagnetic clutch side of the main clutch. The second clutch functions as a pilot clutch that is driven by receiving the electromagnetic force of the electromagnetic clutch, and is configured to apply the rotational force of the first rotating member to the cam mechanism.

  The cam mechanism has a pressing portion that applies a pressing force to the first clutch by a cam action caused by a rotational force from the first rotating member, and is disposed between the first rotating member and the second rotating member. ing.

  With the above configuration, when the driving force from the engine side is input to the first rotating member via the input shaft, the first rotating member rotates about the axis. Here, when the electromagnetic clutch is energized, the second clutch is driven by the electromagnetic force of the electromagnetic clutch.

  Next, when the cam mechanism receives a rotational force from the first rotating member during driving of the second clutch, the rotational force is converted into a pressing force by the cam mechanism, and this pressing force is applied to the first clutch. The

  Then, the inner clutch plate and the outer clutch plate of the first clutch come close to each other and frictionally engage with each other, and the first rotating member and the second rotating member are connected to each other so that torque can be transmitted. . Thereby, the driving force on the engine side is transmitted from the input shaft to the output shaft via the driving force transmission device.

JP 2003-14001 A

  By the way, according to the driving force transmission device shown in Patent Document 1, in order to reduce the adverse effect caused by the so-called drag torque generated based on the viscosity of the lubricating oil when the four-wheel drive vehicle is driven by two-wheel drive, It is desirable to discharge the outside of the housing.

  On the other hand, if all the lubricating oil in the housing is discharged, the bearing in the housing is not lubricated, and the bearing may be seized.

  Accordingly, an object of the present invention is to provide a driving force transmission device capable of supplying lubricating oil to a bearing in a housing and discharging it out of the housing.

  In order to achieve the above object, the present invention provides the driving force transmission devices (1) to (5).

(1) A cylindrical first rotating member that is rotated by a driving source of a vehicle, and is supported in the first rotating member through a bearing so as to be relatively rotatable, and the first rotating member via a clutch. And a second rotating member connected to each other, wherein the second rotating member forms a pump with an outer peripheral surface of the second rotating member and an inner peripheral surface of the first rotating member, and lubricates the bearing. A driving force transmission device having a pump forming part for supplying.

(2) In the driving force transmission device according to (1), the second rotating member is set to have a dimension in which the outer diameter of the pump forming portion gradually increases from the oil inflow side to the oil outflow side. Yes.

(3) In the driving force transmission device according to (2), the first rotating member has at least two holes having different inner diameters, and the second rotating member is the pump. An annular space for introducing lubricating oil from a hole having a small inner diameter to a hole having a large inner diameter is provided between the outer peripheral surface of the forming portion and the inner peripheral surface of the first rotating member. Have.

(4) In the driving force transmission device according to (3), the first rotating member includes an oil storage space communicating with the annular space, and an oil inflow passage for allowing lubricating oil to flow into the oil storage space. Have

(5) In the driving force transmission device according to (3) or (4), the first rotating member communicates with the annular space and causes the lubricating oil to flow out of the second rotating member. Has an oil spillway for

  According to the present invention, drag torque can be reduced and responsiveness of clutch operation in the first clutch can be enhanced.

The top view shown in order to demonstrate the outline of the vehicle by which the driving force transmission apparatus which concerns on embodiment of this invention is mounted. The disassembled perspective view shown in order to demonstrate the whole driving force transmission device which concerns on embodiment of this invention. Sectional drawing shown in order to demonstrate the whole driving force transmission device which concerns on embodiment of this invention. In the figure, the upper half shows a disconnected state, and the lower half shows a connected state. Sectional drawing shown in order to demonstrate the pump formation part of the driving force transmission apparatus which concerns on embodiment of this invention. Sectional drawing shown in order to demonstrate the oil path of the oil outflow path in the driving force transmission apparatus which concerns on embodiment of this invention. (A)-(c) is the perspective view shown in order to demonstrate the cam member for an input of a 2nd cam mechanism in the driving force transmission device which concerns on embodiment of this invention, its top view, and its AA. Sectional drawing. (A) is a perspective view, (b) is a plan view, and (c) is an AA sectional view. (A)-(c) are the perspective view shown in order to demonstrate the cam member for an output of a 2nd cam mechanism in the driving force transmission device which concerns on embodiment of this invention, a top view, and its BB Sectional drawing. (A) is a perspective view, (b) is a plan view, and (c) is a BB sectional view. (A)-(c) is sectional drawing shown in order to demonstrate operation | movement of the 2nd cam mechanism in the driving force transmission apparatus which concerns on embodiment of this invention. (A) shows the non-operating state, (b) shows the operating state, and the operation end (cam climbing) state.

[Embodiment]
FIG. 1 schematically shows a four-wheel drive vehicle. As shown in FIG. 1, the four-wheel drive vehicle 200 includes a driving force transmission system 201, an engine 202, a transmission 203, front wheels 204L and 204R as main drive wheels, and rear wheels 205L and 205R as auxiliary drive wheels. .

  The driving force transmission system 201 is disposed along with a front differential 206 and a rear differential 207 in a driving force transmission path from the transmission 203 side to the rear wheels 205L and 205R side in the four-wheel drive vehicle 200, and the vehicle body of the four-wheel drive vehicle 200 ( (Not shown).

  The driving force transmission system 201 includes a driving force transmission device 1, a propeller shaft 2, and a driving force interrupting device 3, and the four-wheel drive state of the four-wheel drive vehicle 200 is changed to a two-wheel drive state, and the two-wheel drive state is changed to four. Each is configured to be switchable to a wheel drive state. Details of the driving force transmission device 1 will be described later.

  The front differential 206 is a side gear 209L, 209R connected to the axle shafts 208L, 208R on the front wheel side, a pair of pinion gears 210 that mesh with the side gears 209L, 209R at right angles to each other, and a gear support that supports the pair of pinion gears 210. It has a member 211, a gear support member 211, a pair of pinion gears 210, and a front differential case 212 that accommodates side gears 209L and 209R, and is disposed between the transmission 203 and the driving force interrupting device 3.

  The rear differential 207 includes side gears 214L and 214R connected to the rear axle shafts 213L and 213R, a pair of pinion gears 215 that mesh with the side gears 214L and 214R at right angles to the gear shaft, and a gear support that supports the pair of pinion gears 215. A member 216, a gear support member 216, a pair of pinion gears 215, and a rear differential case 217 that accommodates the side gears 214L and 214R are disposed between the propeller shaft 2 and the driving force transmission device 1.

  The engine 202 drives the front wheels 204L and 204R by outputting a driving force to the axle shafts 208L and 208R on the front wheel side via the transmission 203 and the front differential 206.

  Further, the engine 202 outputs a driving force to one rear wheel side axle shaft 213L via the transmission 203, the driving force interrupting device 3, the propeller shaft 2 and the rear differential 207, thereby transmitting one rear wheel 205L to the transmission. 203, the other rear wheel 205R is driven by outputting the driving force to the axle shaft 213R on the other rear wheel side via the driving force interrupting device 3, the propeller shaft 2, the rear differential 207 and the driving force transmission device 1. .

  The propeller shaft 2 is disposed between the driving force transmission device 1 and the driving force interrupting device 3. The propeller shaft 2 is configured to receive the driving force of the engine 202 from the front differential case 212 and transmit it from the front wheels 204L, 204R to the rear wheels 205L, 205R.

  A front wheel side gear mechanism 6 including a drive pinion 60 and a ring gear 61 that mesh with each other is disposed at the front wheel side end of the propeller shaft 2. A rear wheel side gear mechanism 7 including a drive pinion 70 and a ring gear 71 that mesh with each other is disposed at the rear wheel side end of the propeller shaft 2.

  The driving force interrupting device 3 includes a first spline tooth portion 3a that cannot rotate with respect to the front differential case 212, a second spline tooth portion 3b that cannot rotate with respect to the ring gear 61, a first spline tooth portion 3a, and a first spline tooth portion 3a. For example, it comprises a dog clutch having a sleeve 3c that can be fitted to the spline teeth 2b of the two spline teeth 3b, is arranged on the front wheels 204L and 204R side of the four-wheel drive vehicle 200, and is an ECU for the vehicle via an actuator (not shown). (Not shown). The driving force interrupting device 3 is configured to connect the propeller shaft 2 and the front differential case 212 in an intermittent manner.

(Overall configuration of the driving force transmission device 1)
2 and 3 show the driving force transmission device. FIG. 4 shows the pump forming part. FIG. 5 shows a fitted state between the front housing and the rear housing. As shown in FIGS. 2 and 3, the driving force transmission device 1 includes a main clutch (multi-plate clutch) 8 as a first clutch, an electromagnetic clutch 9, a pilot clutch 10 as a second clutch, a housing 12, and an inner clutch. The shaft 13, the first cam mechanism 15, and the second cam mechanism 16 are disposed on the rear wheel 205 </ b> R side of the four-wheel drive vehicle 200 (shown in FIG. 1) and housed in the device case 4. .

  The driving force transmission device 1 can connect / disconnect the propeller shaft 2 (shown in FIG. 1) and the rear wheel side axle shaft 213R (shown in FIG. 1), and the propeller shaft 2 and the rear wheel side axle shaft 213L. (Shown in FIG. 1) are connected to each other.

  That is, at the time of connection by the driving force transmission device 1, one rear wheel side axle shaft 213L and the propeller shaft 2 are connected via the gear mechanism 7 and the rear differential 207 (both shown in FIG. 1), and the other rear wheel. The side axle shaft 213R and the propeller shaft 2 are connected to each other via the gear mechanism 7 and the rear differential 207 so as to transmit torque. On the other hand, when the connection by the driving force transmission device 1 is released, the rear wheel side axle shaft 213L and the propeller shaft 2 remain connected so as to be able to transmit torque via the gear mechanism 7 and the rear differential 207. The connection between the rear wheel side axle shaft 213R and the propeller shaft 2 is cut off.

  The device case 4 includes a case main body 40 that opens to one side of the rotation axis O (the right side in FIG. 3), and a case lid 41 that closes the opening of the case main body 40. The four-wheel drive vehicle 200 (shown in FIG. 1). Is placed on the car body.

  The case main body 40 is integrally provided with a mounting portion 40a that protrudes from the outer surface of the case main body 40 and for mounting a drive source 5 for operating the cam different from the engine 202 (shown in FIG. 1). The attachment portion 40a is provided with a through hole 400a that opens in an axial direction parallel to the rotation axis O.

  The case lid 41 is attached to the case main body 40 by bolts 42 and is entirely formed by a cap member that allows the inner shaft 13 (described later) to be inserted therethrough.

  The drive source 5 incorporates a speed reduction mechanism (not shown), has an electric motor 50, and is attached to the attachment portion 40 a of the case body 40 by bolts 51. Attachment of the drive source 5 to the case body 40 is performed using positioning pins 52. As the speed reduction mechanism, for example, a gear speed reduction mechanism having a worm wheel (not shown) fixed to the motor shaft 50a of the electric motor 50 and a worm 53 meshing with the worm wheel is used. A transmission member 54 for transmitting a rotational force as an operating force to a second cam mechanism 16 (described later) is attached to the drive source 5 (worm 53) via a coupler 55.

  The transmission member 54 has a curved surface portion 54 a having a predetermined radius of curvature, is disposed above the second cam mechanism 16, and is accommodated in the device case 4. The curved surface portion 54 a is provided with external teeth 540 a that constitute a part of the gear transmission mechanism 56. The transmission member 54 is attached to the coupler 55 using a retaining ring 57.

  The coupler 55 includes a cylindrical portion 55 a that is coupled to the worm 53 of the speed reduction mechanism and a shaft portion 55 b that is coupled to the transmission member 54, and is disposed between the worm 53 and the transmission member 54. The cylindrical portion 55a has a seal mechanism 58 interposed between its outer peripheral surface and the inner peripheral surface of the through hole 400a, and the shaft portion 55b has a retaining ring 57 attached to its outer peripheral surface.

(Configuration of main clutch 8)
The main clutch 8 includes a friction type main clutch having a plurality of inner clutch plates 80 and a plurality of outer clutch plates 81, and includes a housing 12 as a first rotating member and an inner shaft 13 as a second rotating member. Arranged between.

  The main clutch 8 frictionally engages the inner and outer clutch plates of the inner clutch plate 80 and the outer clutch plate 81 that are adjacent to each other, and releases the frictional engagement to intermittently connect the housing 12 and the inner shaft 13. It is comprised so that it may connect.

  The inner clutch plates 80 and the outer clutch plates 81 are alternately arranged along the rotation axis O, and are entirely formed by an annular friction plate. The clearance between two adjacent clutch plates of the inner clutch plate 80 and the outer clutch plate 81 is determined by the drag torque based on the viscosity of the lubricating oil when the four-wheel drive vehicle 200 (shown in FIG. 1) is driven by two wheels. Are set to dimensions that do not frictionally engage.

  The inner clutch plate 80 has a straight spline fitting portion 80a on its inner periphery, and the straight spline fitting portion 80a is fitted to the straight spline fitting portion 132a of the cylindrical portion 13a (inner shaft 13) to form an inner shaft. 13 is connected so as not to be relatively rotatable and relatively movable.

The inner clutch plate 80 is provided with a plurality of oil holes 80b that are arranged in parallel along the circumferential direction and open in the direction of the rotation axis O. Of the plurality of inner clutch plates 80, the inner clutch plate at the end on the electromagnetic clutch side functions as an input portion on one side of the main clutch 8, and from the main cam 151 (described later) of the first cam mechanism 15 to the outer clutch plate 81. pressing force to the side when the (first cam thrust) subjected to P _1, and is configured to frictionally engage the inner clutch plates 80 and the outer clutch plates 81 adjacent to each other by the movement to this pressing direction. The inner clutch plate at the end opposite to the end on the electromagnetic clutch 9 side among the plurality of inner clutch plates 80 functions as the input portion on the other side of the main clutch 8, and the second cam mechanism 16. When through the output of the cam member 161 (described later) pressing the member 162 (described later) pressing force to the side outer clutch plates 81 (second cam thrust) subjected to P _2, next to each other by the movement to this pressing direction The clearance C between the matching inner clutch plate 80 and the outer clutch plate 81 is configured to be shortened to C = 0, for example.

  The outer clutch plate 81 has a straight spline fitting portion 81 a on the outer peripheral portion thereof, and the straight spline fitting portion 81 a is fitted to a straight spline fitting portion 19 b (described later) of the rear housing 19 to rotate relative to the housing 12. It is impossible and relative movement is connected.

(Configuration of housing 12)
The housing 12 includes a front housing 18 and a rear housing 19, and is disposed on the axis (rotation axis O) of the axle shaft 213R (shown in FIG. 1) on the other rear wheel side, and the side gear 214R (shown in FIG. 1). It is connected to.

  The front housing 18 includes first to third housing elements 20 to 22, is attached to the inner peripheral surface of the opening of the rear housing 19, and is rotatably supported by the coil holder 23 via a ball bearing 24.

  The coil holder 23 is attached to the outer peripheral surface thereof with a seal member 25 interposed between the inner peripheral surface of the device case 4 and is entirely formed of a hooked ring member through which the front housing 18 is inserted. The coil holder 23 is attached to the device case 4 using the positioning pins 26. In addition, the coil holder 23 is formed with an annular space 27 that is interposed between the coil holder 23 and the outer peripheral surface of the front housing 18 (first housing element 20). The coil holder 23 is provided with an oil passage 23 a that opens into the device case 4 and an oil passage 23 b that communicates with the oil passage 23 a and opens into the annular space 27. The oil passage 23a is formed with an axis parallel to the axis of the coil holder 23, and the oil passage 23b is formed with an axis orthogonal to the axis of the oil passage 23a. A ball-shaped plug 28 for preventing leakage of lubricating oil to the outside of the coil holder 23 is attached to the oil passage 23b.

  The ball bearing 24 is restricted in movement in the axial direction by retaining rings 29 and 30 and is disposed in the annular space 27.

  As shown in FIG. 4, the front housing 18 is provided with three holes 18 a to 18 c that open toward the rear housing 19 and have different inner diameters. The inner diameter of the hole 18a is the maximum dimension (maximum inner diameter), the inner diameter of the hole 18b is the minimum dimension (minimum inner diameter), and the inner diameter of the hole 18c is the inner diameter of the hole 18a and the inner diameter of the hole 18b. The dimension between them (intermediate inner diameter) is set.

  Among these holes 18a to 18c, the hole 18b having the smallest diameter is directed to the hole 18c from the first space 180b and the first space 180b as an oil storage space having a uniform inner diameter in the axial direction. The second space portion 181b that gradually increases the inner diameter and the third space portion 182b that gradually increases the inner diameter from the first space portion 180b toward the second space portion 181b. Accordingly, the minimum inner diameter of the second space 181b is the same as the maximum inner diameter of the third space 182b, and the minimum inner diameter of the third space 182b is the same as the inner diameter of the first space 180b. Each dimension is set. The portion of the inner peripheral surface of the hole 18b that forms the second space portion 181b is formed by a circumferential surface whose gradient is larger than the gradient of the portion that forms the third space portion 182b. On the inner peripheral surface of the hole 18b, the portion forming the second space 181b and the third space 182b functions as a pump forming portion.

  The first housing element 20 has three body portions 20a to 20c having different outer diameters, is disposed on the inner peripheral side of the front housing 18, and is made of a magnetic material such as soft iron as a whole. Is formed by. The outer diameter of the trunk 20a is the maximum dimension (maximum outer diameter), the outer diameter of the trunk 20b is the smallest (minimum outer diameter), and the trunk 20c is the outer diameter of the trunk 20a and the outer diameter of the trunk 20b. Each is set to a dimension between the outer diameter (intermediate outer diameter). A hole 18a is disposed in the body portion 20a having the maximum outer diameter, a hole portion 18b is disposed in the body portion 20b having the minimum outer diameter, and a hole portion 18c is disposed in the body portion 20c having the intermediate outer diameter. .

  The body portion 20 a is formed with an annular space 31 interposed between the body portion 20 a and the inner peripheral surface of the second housing element 21 on the outer periphery thereof. The trunk portion 20a is provided with an oil passage 200a that opens into the annular space 31 and the hole 18a.

  The body portion 20b is provided with a seal mechanism 32 interposed between the outer periphery of the body portion 20b and the inner peripheral surface of the coil holder 23. An oil inflow path A that opens into the annular space 27 and the hole 18b and that allows the lubricating oil in the device case 4 to flow into the first space 180b is formed in the body 20b and the oil paths 23a and 23b. An oil passage 200b is provided.

  The body portion 20c is provided with a needle roller bearing 33 interposed between the inner periphery of the body portion 20c and the outer peripheral surface of the inner shaft 13.

  The second housing element 21 is disposed on the outer peripheral side of the front housing 18, and the whole is formed of a cylindrical member made of a magnetic material such as soft iron like the first housing element 20. On the outer peripheral surface of the second housing element 21, a plurality (four in the present embodiment) of engaging projections 21 a projecting in the radial direction are provided. The plurality of engaging protrusions 21 a are arranged at equal intervals in the circumferential direction of the second housing element 21. The second housing element 21 has an oil outflow path B that opens to the outer peripheral surface and the annular space 31 and flows out the lubricating oil in the hole 18a into the device case 4 (outside the housing 12). An oil passage 21b configured with 200a is provided.

  The third housing element 22 is disposed between the first housing element 20 and the second housing element 21, and is an annular member for connecting the housing element, which is entirely made of a nonmagnetic material such as stainless steel. Is formed by.

  The rear housing 19 has a housing space 19a that opens to the front housing 18 side and the opposite side, and a straight spline fitting portion 19b that is exposed to the housing space 19a. It is formed by a bottom cylindrical member. The rear housing 19 is configured to rotate around the rotation axis O together with the front housing 18. The rear housing 19 is provided with a flange 19c protruding on the outer peripheral surface thereof on the coil holder 23 side. The rear housing 19 is provided with a plurality (four in this embodiment) of engagement recesses 19d that engage with the engagement protrusions 21a of the front housing 18 (second housing element 21).

  As shown in FIG. 5, the plurality of engaging recesses 19 d are located on the coil holder 23 side of the rear housing 19 at a portion interposed between two adjacent spline teeth among the plurality of spline teeth 190 b in the straight spline fitting portion 19 b. This is formed by cutting out the peripheral edge of the opening and a part of the flange 19c. A retaining ring 34 interposed between the flange 19c and the engaging projection 21a is attached to the outer peripheral surface of the rear housing 19.

(Configuration of inner shaft 13)
The inner shaft 13 is interposed between three cylindrical portions 13a to 13c having different outer diameters, a stepped surface 13d interposed between the cylindrical portions 13a and 13b among the cylindrical portions 13a to 13c, and the cylindrical portions 13a and 13c. It has a stepped surface 13e, is disposed on the rotation axis O of the housing 12, and is entirely formed of a bottomless cylindrical member that opens on both sides in the axial direction. The outer diameter of the cylindrical portion 13a is the maximum dimension (maximum outer diameter), the outer diameter of the cylindrical portion 13b is the minimum dimension (minimum outer diameter), and the outer diameter of the cylindrical portion 13c is the same as the outer diameter of the cylindrical portion 13a. The dimension (intermediate outer diameter) is set between the outer diameter of the portion 13b. And the inner shaft 13 is comprised so that the front-end | tip part of the axle shaft 213L (shown in FIG. 1) of the rear-wheel side may be inserted and accommodated in the opening part. The rear wheel axle shaft 213L is connected to the inner shaft 13 by spline fitting so as not to be relatively rotatable and relatively movable.

  The cylindrical portion 13a having the maximum outer diameter is disposed between the cylindrical portion 13b having the minimum outer diameter and the cylindrical portion 13c having the intermediate outer diameter, and is disposed at the central portion in the axial direction of the inner shaft 13. On the outer peripheral surface of the cylindrical portion 13a having the maximum outer diameter, a flange 130a that protrudes on the front housing 18 side in the hole portion 18a is integrally provided. The flange 130a is provided with an oil flow path 131a that opens at both end faces and allows the lubricating oil to flow between the oil inflow path A and the oil outflow path B.

  Further, a straight spline fitting portion that is exposed to the accommodation space 19a of the rear housing 19 and is fitted to the straight spline fitting portion 80a of the inner clutch plate 80 in the main clutch 8 is formed on the outer peripheral surface of the cylindrical portion 13a having the maximum outer diameter. 132a is provided.

  A cap-like plug body 35 for preventing the lubricating oil in the device case 4 from flowing out of the device case 4 is attached to the inner peripheral surface of the cylindrical portion 13a having the maximum outer diameter. The cylindrical portion 13a having the maximum outer diameter is provided with an oil passage 133a that opens between the plug body 35 and the flange 130a on the inner and outer peripheral surfaces thereof.

  The cylindrical portion 13b having the smallest outer diameter is disposed on one side (the left side in FIG. 3) of the inner shaft 13, and is rotatably supported in the hole 18c of the front housing 18 via a needle roller bearing 33. . A bottomed cylindrical shaft lid 36 that closes the opening on the front housing 18 side is attached to the cylindrical portion 13b having the smallest outer diameter.

  The shaft lid 36 is opposed to a portion forming the second space portion 181b on the inner peripheral surface of the hole portion 18b in the front housing 18 (first housing element 20), and the second space portion 181b. And the pump formation part 36a of the truncated cone shape which has the outer peripheral surface 360a which forms a pump between the site | parts which form the 3rd space part 182b is integrally provided. Between the outer peripheral surface 360a of the pump forming portion 36a and the inner peripheral surface of the first housing element 20, the lubricating oil is introduced into the hole portion 18c from the hole portion 18b (first space portion 180b) side, and needle rollers are introduced. An annular space 37 for supplying to the bearing 33 and the like is formed. The annular space 37 is set so that its inner and outer diameters gradually increase from the oil inflow (introduction) side toward the oil outflow (outflow) side.

Pump forming part 36a is set to be smaller than dimensions of _{R 1} from the oil introduction end 361a to the rotation axis O from the oil outlet side end portion 362a to the axis of rotation _{O R 2 (R 1 <R} 2) Has been. The outer diameter of the pump formation portion 36a is set to a dimension that gradually increases from the oil introduction side end 361a toward the oil discharge side end 362a. For this reason, when the inner shaft 13 rotates, the peripheral speed of the outer peripheral surface 360a of the pump forming portion 36a gradually increases from the oil introduction side end 361a toward the oil discharge side end 362a, and therefore the pressure in the annular space 37 is increased. The outer circumferential surface 360a of the pump forming portion 36a and the inner circumferential surface of the first housing element 20 (sites forming the second space portion 181b and the third space portion 182b are gradually lowered from the introduction side toward the oil outlet side. ), A pumping action having a suction force in the direction of the arrow Y occurs. Thereby, after the lubricating oil that has flowed into the hole 18b (first space 180b) of the front housing 18 is introduced into the second space 181b and the third space 182b (annular space 37), It flows through the annular space 37 and is led into the hole 18c.

  The intermediate outer diameter cylindrical portion 13c is disposed on the other side (right side in FIG. 3) of the inner shaft 13, and is rotatably supported on the inner peripheral surface of the device case 4 (case lid body 41) via a ball bearing 38. ing. A cylindrical receiving member 39 interposed between the ball bearing 38 and the stepped surface 13e is attached to the outer peripheral surface of the intermediate outer diameter cylindrical portion 13c. A seal mechanism 45 interposed between the outer peripheral surface of the intermediate outer diameter cylindrical portion 13 c and the inner peripheral surface of the case lid body 41 is disposed. The movement of the ball bearing 38 in the axial direction is restricted by retaining rings 46 and 47, and is disposed between the outer peripheral surface of the cylindrical portion 13 c having an intermediate outer diameter and the inner peripheral surface of the case lid 41. Yes.

(Configuration of electromagnetic clutch 9)
The electromagnetic clutch 9 has an electromagnetic coil 90 and an armature 91 and is arranged in parallel with the main clutch 8 on the rotation axis O of the housing 12. The electromagnetic clutch 9 operates the first cam mechanism 15 by the movement of the armature 91 toward the electromagnetic coil 90 due to the generation of the electromagnetic force F when the housing 12 rotates, and the inner clutch plate 80 and the outer clutch of the main clutch 8. The plate 81 is configured to frictionally engage with each other.

  The electromagnetic coil 90 is connected to the vehicle ECU and is held in the coil holder 23. The electromagnetic coil 90 forms a magnetic circuit M across the front housing 18 and the armature 91 and the like by energization so as to generate an electromagnetic force F for applying a moving force to the armature 91 toward the front housing 18. It is configured.

  The armature 91 has a straight spline fitting portion 91a on the outer peripheral surface thereof, and the straight spline fitting portion 91a is fitted to the straight spline fitting portion 19b and is connected to the rear housing 19 so as not to be relatively rotatable and relatively movable. The first cam mechanism 15 (main cam 151) is interposed between the pilot clutch 10 and is accommodated in the accommodating space 19a of the rear housing 19, and is formed by an annular plate made entirely of a magnetic material such as iron. Has been. The armature 91 is configured to receive the electromagnetic force F of the electromagnetic coil 90 and move along the rotational axis O toward the front housing 18 side.

(Configuration of pilot clutch 10)
The pilot clutch 10 includes an inner clutch plate 100 and an outer clutch plate 101 that are formed of annular friction plates that can be frictionally engaged with each other when the armature 91 is moved toward the electromagnetic coil 90 by energization of the electromagnetic clutch 9. 91 is disposed between the front housing 18 and the housing space 19 a of the rear housing 19. The pilot clutch 10 frictionally engages the clutch plates adjacent to each other out of the inner clutch plate 100 and the outer clutch plate 101, and releases the frictional engagement so that the rear housing 19 and the first cam mechanism 15 ( The pilot cam 150) is connected to be intermittently connected.

  The inner clutch plates 100 and the outer clutch plates 101 are alternately arranged along the rotation axis O, and are entirely formed by an annular friction plate.

  The inner clutch plate 100 has a straight spline fitting portion 100a on the inner peripheral portion thereof, and the straight spline fitting portion 100a is fitted to the straight spline fitting portion 150a so that the inner clutch plate 100 cannot be relatively rotated and moved relative to the pilot cam 150. It is connected to.

  The outer clutch plate 101 has a straight spline fitting portion 101a on the outer peripheral portion thereof, and the straight spline fitting portion 101a is fitted to the straight spline fitting portion 19b so that it cannot be rotated relative to the rear housing 19 and is relatively movable. It is connected.

(Configuration of the first cam mechanism 15)
The first cam mechanism 15 is an input ball cam member (pilot cam) 150 that rotates in response to a rotational force from the housing 12 (rear housing 19), and an output ball that is parallel to the pilot cam 150 along the rotation axis O. Ball cam member (main cam) 151 and a plurality of (six in this embodiment) spherical cam followers 152 interposed between the main cam 151 and the pilot cam 150. It is disposed in between and is accommodated in the accommodating space 19 a of the rear housing 19. The first cam mechanism 15 is configured to convert the rotational force received from the housing 12 by the clutch operation of the electromagnetic clutch 9 into a pressing force (first cam thrust) P ₁ that becomes the clutch force of the main clutch 8. Has been.

The pilot cam 150 has a straight spline fitting portion 150a fitted to the straight spline fitting portion 100a of the inner clutch plate 100 on the outer peripheral portion thereof, and a needle roller bearing is provided on the flange 130a of the inner shaft 13 (cylindrical portion 13a). It is rotatably supported via 153 and is formed entirely by an annular member through which the inner shaft 13 is inserted. The pilot cam 150 is configured to generate a _first cam thrust P ₁ between the pilot cam 150 and the main cam 151 and output it to the main clutch 8.

  The pilot cam 150 is provided with a plurality of (six in the embodiment) cam grooves 150b that are arranged in parallel in the circumferential direction and open to the cam follower 152 side. The plurality of cam grooves 150 b are arranged at equal intervals in the circumferential direction of the pilot cam 150. The plurality of cam grooves 150b are formed by concave grooves that gradually become shallower in the axial direction along the circumferential direction of the pilot cam 150 from the neutral position.

The main cam 151 has a clutch plate pressing portion 151a on the main clutch 8 side, and is disposed along the rotation axis O so as to be relatively movable on the inner shaft 13 (cylindrical portion 13a having the maximum outer diameter). It is formed by an annular member to be inserted. The main cam 151 receives the _first cam thrust P ₁ generated from the cam follower 152 by the cam action of the first cam mechanism 15 in the energized state of the electromagnetic coil 91, that is, the rotation of the pilot cam 150, and receives the main cam 8 side. And the clutch plate pressing portion 151a is pressed against the inner clutch plate 80 on the input side of the main clutch 8 on one side of the rotation axis O (left side in FIG. 3).

  The main cam 151 is provided with a plurality of (six in the embodiment) cam grooves 151b that are arranged in parallel at equal intervals in the circumferential direction and open to the cam follower 152 side. The plurality of cam grooves 151b are formed as concave grooves whose depth in the axial direction gradually decreases along the circumferential direction of the main cam 151 from the neutral position. Further, the main cam 151 has a plurality (six in the embodiment) of oil holes 151c that open in a direction parallel to the rotation axis O, and a plurality of (opens in the direction opposite to the opening direction of the plurality of cam grooves 151b). Six pin mounting holes 151d are provided in the embodiment. The plurality of oil holes 151 c and the plurality of pin mounting holes 151 d are alternately arranged at equal intervals in the circumferential direction of the main cam 151.

  A guide pin 155 for guiding the spring force of the return spring 154 interposed between the main cam 151 and the pressing member 162 (the output cam member 161 in the second cam mechanism 16) is attached to the pin attachment hole 151d. ing. As a result, the spring force of the return spring 154 acts in a direction in which the main cam 151 and the output cam member 161 are separated from each other, and the clearance between two adjacent clutch plates of the inner clutch plate 80 and the outer clutch plate 81. However, when the four-wheel drive vehicle 200 (shown in FIG. 1) is driven in two wheels, the dimension is set such that the clutch plates are not frictionally engaged by the drag torque based on the viscosity of the lubricating oil.

  The cam follower 152 is disposed between the cam groove 150b of the pilot cam 150 and the cam groove 151b of the main cam 151, and is held by a retainer 156 so as to be able to roll.

(Configuration of the second cam mechanism 16)
As shown in FIGS. 2 to 4, the second cam mechanism 16 is rotated by the input cam member 160 that rotates by receiving the rotational force as the operating force from the drive source 5 and the input cam member 160. The output cam member 161 is arranged in parallel on the axis O, and is arranged at a position facing the first cam mechanism 15 on the rotation axis O via the main clutch 8. The second cam mechanism 16 operates prior to the conversion of the first cam thrust P ₁ by the first cam mechanism 15, and presses the pressing member 162 against the main clutch 8 to cause the inner clutch plate 80 and the outer clutch to move. For example, the second cam thrust P ₂ for shortening the clearance C between the plate 81 and C = 0 is set in the direction opposite to the direction of the first cam thrust P ₁ and the input cam member 160 and the output cam 160. It is comprised so that it may generate | occur | produce between the cam members 161 of this.

  6A to 6C show an input cam member. The input cam member 160 has an uneven surface 163 on the side facing the output cam member 161, is connected to the transmission member 54 via a gear transmission mechanism 56, and has a needle roller bearing 164 on the receiving member 39. And the whole is formed by an annular member through which the inner shaft 13 is inserted.

  The concave / convex surface 163 has concave portions 165 and convex portions 166 alternately arranged along the circumferential direction of the input cam member 160, and the concave / convex surface 163 has a circumferential direction between the concave / convex surface 168 of the output cam member 161. It is formed with a cam surface for relative movement in the axial direction by relative movement. In the present embodiment, the concavo-convex surface 163 is formed by a cam surface for moving the output cam member 161 toward the main clutch 8 along the axis (rotation axis O) by the rotation of the input cam member 160. ing.

  The concave portion 165 includes a pair of cut-out side surfaces 165a and 165b that gradually increase the cut-out width from one axial side of the input cam member 160 toward the other axial side (the output cam member 161 side). It is formed by a notch having a trapezoidal cross section having a notch bottom surface (x surface) 165c interposed between the notch side surfaces 165a and 165b.

  One notch side surface 165a is inclined with respect to the notch bottom surface 165c on one side around the rotation axis O as a cam, and the other notch side surface 165b is orthogonal to the notch bottom surface 165c on the other side around the rotation axis O. And each function as a stopper.

  The convex portion 166 includes a notched side surface 165a that functions as a cam in one of the two recessed portions 165 adjacent to each other, a notched side surface 165b that functions as a stopper in the other recessed portion, and a space between the notched side surfaces 165a and 165b. It is formed by a projection having a trapezoidal cross section having an interposing end face (◯ face) 166a.

  The input cam member 160 is integrally provided with a fan-shaped convex piece 167 protruding along the outer peripheral edge. The convex piece 167 is provided with external teeth 167 a that mesh with the external teeth 540 a of the transmission member 54.

  FIGS. 7A to 7C show an output cam member. As shown in FIGS. 3 and 7A to 7C, the output cam member 161 has an uneven surface 168 that can be fitted to the uneven surface 163 of the input cam member 160. The cam member 160 and the pressing member 162 are interposed between the cam member 160 and the pressing member 162 so as to be movable in the axial direction (impossible to move in the circumferential direction), and are entirely formed by an annular member through which the inner shaft 13 is inserted.

  The concave / convex surface 168 includes concave portions 169 and convex portions 170 that are alternately arranged along the circumferential direction of the output cam member 161, and the concave / convex surface 168 has a circumferential direction between the concave / convex surface 163 of the input cam member 160. It is formed with a cam surface for relative movement in the axial direction by relative movement. In the present embodiment, the uneven surface 168 is formed by a cam surface for moving the output cam member 161 toward the main clutch 8 along the axis (rotation axis O) by the rotation of the input cam member 160. ing.

  The recess 169 includes a pair of cut side surfaces 169a and 169b that increase the cut width from one axial direction of the output cam member 161 toward the other axial direction side (input cam member 160 side), and a pair of It is formed by a notch having a trapezoidal cross section having a notch bottom surface (x surface) 169c interposed between the notch side surfaces 169a and 169b.

  One notch side surface 169a corresponds to the notch side surface 165a of the concave and convex surface 163 in the input cam member 160 and is inclined with respect to the notch bottom surface 169c on the other side around the rotation axis O so as to function as a cam. It has been configured. The other notched side surface 169b corresponds to the notched side surface 165b of the uneven surface 163 of the input cam member 160, and functions as a stopper perpendicular to the notched bottom surface 169c on one side around the rotation axis O. It is configured.

  The convex portion 170 includes a notched side surface 169a that functions as a cam in one of the two recessed portions 169 adjacent to each other, a notched side surface 169b that functions as a stopper in the other recessed portion, and a space between the notched side surfaces 169a and 169b. It is formed by a projection having a trapezoidal cross section having an interposing end face (◯ face) 170a.

Thus, in the initial state in which the concave and convex surface 163 of the input cam member 160 and the concave and convex surface 168 of the output cam member 161 are notched and the bottom surfaces 165c and 169c are in contact with each other, the input cam member 160 is rotated. When rotating in one direction around O, the input cam member 160 moves around the rotation axis O with the notched side surface 165a abutting against the notched side surface 169a of the output cam member 161. Therefore, cam action occurs between the side surface 165a, 169a lacks double-pole has a function as a cam, the second cam thrust P ₂ involves this acts on the cam member 161 for output from the cam member 160 for input The output cam member 161 moves along the rotation axis O in a direction away from the input cam member 160. In this case, the output cam member 161 is moved until the end surface 166 a of the uneven surface 163 of the input cam member 160 rides on the end surface 170 a of the uneven surface 168.

  When the input cam member 160 rotates in the other direction around the rotation axis O, the notched side surface 165b and the notched side surface 169b, which function as a stopper, come into contact with each other, so that the cam action acts between the notched side surfaces 165a and 169a. Does not occur, and the output cam member 161 does not move in the axial direction as described above.

  The pressing member 162 has a straight spline fitting portion 162a on the inner peripheral edge thereof and a clutch plate pressing portion 162b on the main clutch 8 side. The straight spline fitting portion 162a is connected to the straight of the inner shaft 13 (cylindrical portion 13a). The spline fitting portion 132a is fitted to the inner shaft 13 so as to be relatively unrotatable and relatively movable, and supported by the output cam member 161 via a needle roller bearing 171 so that the entire inner shaft 13 is rotatable. It is formed by an annular member through which the shaft 13 is inserted.

Then, the pressing member 162 receives from the second cam member 161 of the output cam P ₂ generated by the operation of the second cam mechanism 16 moves to the main clutch 8 side, the other side (Fig rotation axis O 3 on the right side of 3), the clutch plate pressing portion 162b is pressed against the inner clutch plate 80 on the input side of the main clutch 8.

(Operation of the driving force transmission device 1)
Next, the operation of the driving force transmission apparatus shown in the present embodiment will be described with reference to FIGS. 1, 3, 4, and 8A to 8C. FIGS. 8A to 8C show the operating states of the input cam member and the output cam member in the second cam mechanism.

  In FIG. 1, when the engine 202 is started during the two-wheel drive of the four-wheel drive vehicle 200, the rotational driving force of the engine 202 is transmitted to the front differential 206 via the transmission 203, and the front differential axle shaft 208L, It is transmitted to the front wheels 204L and 204R via 208R, and the front wheels 204L and 204R are rotationally driven. At this time, the driving force interrupting device 3 cannot transmit power between the first spline tooth portion 3a and the second spline tooth portion 3b.

  In this case, in FIG. 3 (upper half), since the electromagnetic coil 90 of the electromagnetic clutch 9 is in a non-energized state, the magnetic circuit M based on the electromagnetic coil 90 is not formed, and the armature 91 moves to the electromagnetic coil 90 side. Thus, it is not connected to the housing 12.

Therefore, first without the first cam thrust P ₁ as the clutch force of the main clutch 8 is not generated in the cam mechanism 15, not combined with the inner clutch plates 80 and the outer clutch plates 81 of the main clutch 8 together friction The rotational driving force of the engine 202 is not transmitted from the housing 12 to the inner shaft 13.

  Here, the lubrication action with respect to the ball bearing 24 and the needle roller bearings 33 and 153 by the pump formation part 36a accompanying the two-wheel drive of the four-wheel drive vehicle 200 is demonstrated. Since the inner shaft 13 is rotated by the rotation of the rear wheel 205L during the two-wheel drive of the four-wheel drive vehicle 200, the outer peripheral surface 360a of the pump forming portion 36a and the inner peripheral surface of the first housing element 20 (second space portion 181b and A pumping action having a suction force in the direction of arrow Y (shown in FIG. 4) occurs between the third space 182b and the third space 182b. In the two-wheel drive state, the inner shaft 13 rotates in the direction opposite to the rotation direction of the housing 12, so that the suction force by the pump action is larger than that in the four-wheel drive state.

  As a result, as shown in FIG. 4, the lubricating oil in the device case 4 flows through the oil inflow path A (oil paths 200b, 23a, 23b) and the annular space 27, and the first space 180b in the hole 18b. Flow into. At this time, the ball bearing 24 is lubricated with the lubricating oil between the oil passage 23b and the oil passage 200b.

  Next, the lubricating oil that has flowed into the first space portion 180b is introduced into the second space portions 181b and 182b (annular space 37), and then flows through the annular space 37 and is led into the hole portion 18c. It flows into the hole 18a and the oil flow path 131a from the hole 18c. At this time, the needle roller bearing 33 is lubricated with the lubricating oil in the hole 18c and the needle roller bearing 153 is lubricated in the hole 18a.

  The lubricating oil that has flowed into the hole 18a and the oil flow path 131a flows into the oil outflow path B (the oil paths 200a and 21b and the annular space 31) by its own weight or by the centrifugal force generated with the rotation of the inner shaft 13. Then, it flows out from the oil outflow path B into the device case 4.

  On the other hand, in order to switch the four-wheel drive vehicle 200 in the two-wheel drive state to the four-wheel drive state, the driving force transmission device 1 connects the propeller shaft 2 and the rear axle shafts 213L and 213R so as to transmit torque, Subsequently, the front differential case 212 and the propeller shaft 2 are connected by the driving force interrupting device 3 so that torque can be transmitted.

  Here, when the propeller shaft 2 and the axle shafts 213L and 213R on the rear wheel side are connected, first, the driving force of the driving source 5 is applied to the second cam mechanism 16 to operate the second cam mechanism 16. In this case, when the second cam mechanism 16 is operated, the input cam member 160 rotates about the rotation axis O.

For this reason, as shown in FIG. 8A, the uneven surface 163 of the input cam member 160 and the uneven surface 168 of the output cam member 161 are brought into contact with the notched bottom surfaces 165c and 169c. Then, the input cam member 160 moves around the rotation axis O (shown in FIG. 3) with the notched side surface 165a abutting against the notched surface 169a of the output cam member 161. At this time, cam action occurs double-pole-away side 165a, between 169a, the second cam thrust _{P 2} involves this acts on the cam member 161 for output from the cam member 160 for input. As a result, as shown in FIG. 8B, the output cam member 161 moves along the rotation axis O in the direction of the arrow X <b> ₂ away from the input cam member 160. In this case, the output cam member 161 is moved until the end surface 166a of the uneven surface 163 of the input cam member 160 rides on the end surface 170a of the uneven surface 168, as shown in FIG.

The main clutch 8 the pressing member 162 by moving the cam member 161 for output to the direction of arrow X ₂ is moved against the return spring 154 to the main clutch 8 side, pressing member 162 in the clutch plate pressing unit 162b Is moved against the first cam mechanism 15 side. As a result, the clearance C between two adjacent clutch plates of the inner clutch plate 80 and the outer clutch plate 81 becomes, for example, C = 0.

  Next, when the electromagnetic coil 90 is energized, a magnetic circuit M based on the electromagnetic coil 90 is formed across the coil holder 23, the armature 91 and the front housing 18, and the armature 91 is based on the energization of the electromagnetic coil 90. It moves in the direction approaching the front housing 18 by the electromagnetic force F (attraction force) generated in this way. For this reason, the armature 91 is connected to the front housing 18 via the pilot clutch 10, the rotational force of the housing 12 is transmitted to the pilot cam 150, and the pilot cam 150 rotates.

Accordingly, the first cam mechanism 15 is operated, and is converted into a _first cam thrust P ₁ that becomes a clutch force of the main clutch 8 by a cam action generated in the first cam mechanism 15, and this first cam main cam 151 in a direction (direction of arrow _{X 1)} frictionally engaged clutch plates 80, 81 between the main clutch 8 is moved against the spring force of the return spring 154 by the thrust _{P 1.}

Then, pressing the main clutch 8 in the clutch plate pressing portion 151a main cam 151 by the movement of the arrow _{X 1} direction to the second cam mechanism 16 side.

  As a result, two adjacent clutch plates of the inner clutch plate 80 and the outer clutch plate 81 are frictionally engaged, and the rotational driving force of the engine 202 is transmitted from the housing 12 to the inner shaft 13 and further from the inner shaft 13 to the rear. This is transmitted to the rear wheels 205L and 205R via the axle shafts 213L and 213R on the wheel side, and the rear wheels 205L and 205R are rotationally driven.

[Effect of the embodiment]
According to the embodiment described above, the following effects can be obtained.

(1) The drag torque can be reduced and the responsiveness of the clutch operation in the main clutch 8 can be enhanced.

(2) Lubricating oil can be supplied to the bearings (the ball bearing 24 and the needle roller bearings 33 and 153) by a pump action and discharged out of the housing 12.

  The driving force transmission device of the present invention has been described based on the above embodiment, but the present invention is not limited to the above embodiment, and may be implemented in various modes without departing from the gist thereof. For example, the following modifications are possible.

(1) In the above embodiment, the case where the pump forming portion 36a is provided on the inner shaft 13 and a part of the inner peripheral surface of the hole 18b in the housing 12 functions as the pump forming portion has been described. However, the pump forming portion may be provided on either the inner shaft or the housing. That is, in short, the present invention has a pump forming portion that forms a pump between the inner peripheral surface of the first rotating member and the outer peripheral surface of the second rotating member and supplies lubricating oil to the bearing. Good.

(2) In the above embodiment, the case where the housing 12 is connected to the input shaft side and the inner shaft 13 is connected to the output shaft side has been described. However, the present invention is not limited to this, and the housing is connected to the output shaft. Even when the inner shaft and the inner shaft are connected to the input shaft side, the same effects as in the present embodiment can be obtained.

DESCRIPTION OF SYMBOLS 1 ... Driving force transmission device, 2 ... Propeller shaft, 3 ... Driving force interruption device, 3a ... 1st spline tooth part, 3b ... 2nd spline tooth part, 3c ... Sleeve, 4 ... Device case, 40 ... Case main body , 40a ... mounting portion, 400a ... through hole, 41 ... case cover, 42 ... bolt, 5 ... drive source, 50 ... electric motor, 50a ... motor shaft, 51 ... bolt, 52 ... positioning pin, 53 ... worm, 54 ... Transmission member, 54a ... curved surface part, 540a ... external teeth, 55 ... connector, 55a ... cylindrical part, 55b ... shaft part, 56 ... gear transmission mechanism, 57 ... retaining ring, 58 ... sealing mechanism, 6 ... gear mechanism, 60 ... Drive pinion, 61 ... Ring gear, 7 ... Gear mechanism, 70 ... Drive pinion, 71 ... Ring gear, 8 ... Main clutch, 80 ... Inner clutch plate, 80a ... Straight spline Joint part, 80b ... Oil hole, 81 ... Outer clutch plate, 81a ... Straight spline fitting part, 9 ... Electromagnetic clutch, 90 ... Electromagnetic coil, 91 ... Armature, 91a ... Straight spline fitting part, 10 ... Pilot clutch, 100 ... Inner clutch plate, 100a ... Straight spline fitting part, 101 ... Outer clutch plate, 101a ... Straight spline fitting part, 12 ... Housing, 13 ... Inner shaft, 13a-13c ... Cylindrical part, 13d, 13e ... Stepped surface, 130a ... Flange, 131a ... Oil flow path, 132a ... Straight spline fitting portion, 133a ... Oil passage, 14 ... Side gear shaft, 15 ... First cam mechanism, 150 ... Pilot cam, 150a ... Straight spline fitting portion, 150b ... Cam groove, 151 ... Mei Cam, 151a ... clutch plate pressing portion, 151b ... cam groove, 151c ... oil hole, 151d ... pin mounting hole, 152 ... cam follower, 153 ... needle roller bearing, 154 ... return spring, 155 ... guide pin, 156 ... retainer 16 ... second cam mechanism, 160 ... input cam member, 161 ... output cam member, 162 ... pressing member, 162a ... straight spline fitting portion, 162b ... clutch plate pressing portion, 163 ... uneven surface, 164... Needle roller bearing, 165... Recessed, 165 a, 165 b. ... concave portion, 169a, 169b ... notched side surface, 169c ... notched bottom surface, 170 ... convex portion, 170a ... end face, 171 ... needle Tapered roller bearing, 18 ... front housing, 18a-18c ... hole, 180b ... first space, 181b ... second space, 182b ... third space, 19 ... rear housing, 19a ... housing space, 19b ... Straight spline fitting portion, 190b ... Spline teeth, 19c ... Flange, 19d ... Engaging recess, 20 ... First housing element, 20a-20c ... Body, 200a, 200b ... Oil passage, 21 ... Second Housing element, 21a ... engagement projection, 21b ... oil passage, 22 ... third housing element, 23 ... coil holder, 23a, 23b ... oil passage, 24 ... ball bearing, 25 ... sealing member, 26 ... positioning pin, 27 ... annular space, 28 ... plug, 29, 30 ... retaining ring, 31 ... annular space, 32 ... sealing mechanism, 33 ... needle roller bearing, 34 ... retaining ring, 35 ... Body 36... Shaft cover 36 a pump formation part 360 a outer peripheral surface 361 a oil introduction side end 362 a oil extraction side end 37 annular space 38 ball bearing 39 receiving member 45 ... Sealing mechanism, 46, 47 ... Retaining ring, 200 ... Four-wheel drive vehicle, 201 ... Driving force transmission system, 202 ... Engine, 203 ... Transmission, 204L, 204R ... Front wheel, 205L, 205R ... Rear wheel, 206 ... Front differential 207: Rear differential, 208L, 208R: Front axle shaft, 209L, 209R: Side gear, 210: Pinion gear, 211: Gear support member, 212: Front differential case, 213L, 213R: Rear axle axle shaft, 214L, 214R ... side gear, 215 ... pinion gear, 216 ... gear support Member, 217 ... rear differential case, A ... oil inflow passage, B ... oil spill passage, P 1 _... first cam thrust, P 2 _... second cam thrust, C ... clearance, M ... magnetic circuit, O ... Rotation axis

Claims (5)

A cylindrical first rotating member that is rotated by a drive source of the vehicle;
A second rotating member supported in the first rotating member via a bearing so as to be relatively rotatable, and connected to the first rotating member via a clutch;
The second rotating member has a pump forming portion for supplying a lubricant to the bearing by forming a pump between the outer peripheral surface of the second rotating member and the inner peripheral surface of the first rotating member. .   2. The driving force transmission device according to claim 1, wherein the second rotating member is set to have a dimension in which an outer diameter of the pump forming portion gradually increases from an oil inflow side toward an oil outflow side. The first rotating member has at least two holes having different inner diameters from each other,
The second rotating member is configured such that the outer peripheral surface of the pump forming portion is between the inner peripheral surface of the first rotating member and the hole portion having a smaller inner diameter from the hole portion having the smaller inner diameter among the at least two holes. The driving force transmission device according to claim 2, further comprising an annular space for introducing the lubricating oil.   4. The driving force transmission device according to claim 3, wherein the first rotating member includes an oil storage space communicating with the annular space, and an oil inflow passage for allowing lubricating oil to flow into the oil storage space.   5. The driving force transmission device according to claim 3, wherein the first rotating member has an oil outflow passage that communicates with the annular space and allows the lubricating oil to flow out of the second rotating member.

Images