JP7310440B2 - Vehicle transfer device - Google Patents

Description

The present invention relates to a vehicle transfer device.

2. Description of the Related Art A transfer is known that switches between two-wheel drive in which power transmitted from a drive source is transmitted to front wheels and four-wheel drive in which power is transmitted to front and rear wheels (see Patent Document 1).

This transfer is a clutch hub having an inner hub spline-fitted to a power transmission shaft through which power is transmitted from an engine, and an outer hub provided coaxially with the inner hub on the outer periphery of the inner hub and having power transmission teeth on the outer peripheral surface thereof. It has

A power output shaft having an output gear having power transmission teeth and transmitting power to the rear wheels is provided coaxially with the power transmission shaft.

The power transmission teeth of the output gear are always engaged with the shift sleeve for switching between 2WD and 4WD. By engaging both of the power transmission teeth, power can be transmitted from the power transmission shaft to the power output shaft.

A damping member is interposed between the inner hub and the outer hub to rotatably couple the inner hub and the outer hub in the circumferential direction, and the inner hub, the outer hub, and the damping member constitute a damper.

In the transfer, when rotational fluctuation due to engine torque fluctuation or the like occurs between the inner hub and the outer hub, the cushioning member elastically deforms to absorb the rotational fluctuation of the power transmission shaft.

Japanese Utility Model Laid-Open No. 60-23321

As the thickness of the cushioning member in the radial direction increases, the durability of the damper improves. Therefore, the thickness of the damper in the radial direction is increased by the damping member and the inner peripheral spline. Therefore, in order to shorten the radial dimension of the transfer device, the radial thickness of the cushioning member is restricted.

SUMMARY OF THE INVENTION The present invention has been made in view of the above circumstances, and is capable of increasing the radial thickness of the elastic body of the damper member while preventing an increase in the radial dimension of the transfer device. It is an object of the present invention to provide a vehicular transfer device capable of preventing deterioration in durability of members.

The present invention is a vehicular transfer device capable of switching between two-wheel drive in which power is transmitted from a drive source to main drive wheels and four-wheel drive in which power is transmitted from the drive source to the main drive wheels and sub-drive wheels. an input shaft extending in the longitudinal direction of the vehicle to which power is transmitted from the drive source; a first power transmission member having a first outer spline formed on an outer peripheral portion thereof and rotating integrally with the input shaft; a second power transmission member provided coaxially with the first power transmission member, and the first power transmission member having a first inner periphery spline; and the second power transmission member are provided movably in the axial direction, and during two-wheel drive, the first inner peripheral spline is fitted only to the second outer spline, so that from the first power transmission member By interrupting power transmission to the second power transmission member and engaging the first inner peripheral spline with the first outer spline and the second outer spline during four-wheel drive, the second a shift sleeve for transmitting power from one power transmission member to the second power transmission member; an output member provided rotatably relative to the input shaft for transmitting power to the auxiliary drive wheels; a damper member provided between the power transmission member and the output member and rotating integrally with the second power transmission member, wherein a third outer spline is formed on the outer peripheral surface of the output member; A second power transmission member fitted to the third outer spline on the inner peripheral surface of the second power transmission member for restricting relative rotation between the second power transmission member and the output member to a first predetermined angle. An inner peripheral spline is formed on the inner peripheral surface of the damper member, and is fitted to the third outer spline, and the relative rotation between the damper member and the output member is controlled by a third angle smaller than the first predetermined angle. The damper member is provided on an elastic body and on the inner peripheral surface of the elastic body, and the third inner spline is formed. a cylindrical inner peripheral member having a first inner peripheral surface and a second inner peripheral surface facing the outer peripheral surface of the output member in a non-engaged state; The spline is separated from the elastic body in the axial direction of the input shaft.

As described above, according to the present invention, it is possible to increase the radial thickness of the elastic body of the damper member while preventing an increase in the radial dimension of the transfer device, thereby reducing the durability of the damper member. can be prevented.

FIG. 1 is a plan view of a vehicle equipped with a vehicle transfer device according to an embodiment of the present invention. FIG. 2 is an exploded perspective view of a vehicle transfer device according to one embodiment of the present invention. FIG. 3 is a plan view of a vehicle transfer device according to one embodiment of the present invention. FIG. 4 is a right side view of the vehicle transfer device according to one embodiment of the present invention. 5 is a cross-sectional view taken along the line VV in FIG. 3. FIG. 6 is a cross-sectional view taken along the line VI-VI of FIG. 4. FIG. FIG. 7 is an exploded perspective view of a circlip, a cylindrical member, a dog, a damper member and an output member that constitute a vehicle transfer device according to an embodiment of the present invention. FIG. 8 is a diagram showing power transmission paths during four-wheel drive of the vehicle transfer device according to the embodiment of the present invention.

A vehicle transfer device according to an embodiment of the present invention switches between two-wheel drive in which power is transmitted from a drive source to main drive wheels and four-wheel drive in which power is transmitted from a drive source to main drive wheels and auxiliary drive wheels. The transfer device for a vehicle includes an input shaft extending in the longitudinal direction of the vehicle to which power is transmitted from a drive source, and a first outer spline formed on the outer periphery and rotating integrally with the input shaft. a second power transmission member having a second outer spline formed on an outer peripheral portion thereof and provided coaxially with the first power transmission member; and a first inner spline having a second power transmission member The first power transmission member and the second power transmission member are provided movably in the axial direction, and the first power transmission is achieved by fitting the first inner peripheral spline only to the second outer spline during two-wheel drive. The transmission of power from the member to the second power transmission member is cut off, and the first inner peripheral spline is fitted to the first outer spline and the second outer spline during four-wheel drive, whereby the first power is transmitted. a shift sleeve that transmits power from the transmission member to the second power transmission member; an output member that is provided rotatably relative to the input shaft and transmits power to the auxiliary drive wheels; A damper member is provided between and rotates integrally with the second power transmission member, a third outer spline is formed on an outer peripheral surface of the output member, and an inner peripheral surface of the second power transmission member A second inner spline is formed on the inner periphery of the damper member so as to engage with the third outer spline and restrict the relative rotation of the second power transmission member and the output member to a first predetermined angle. a third inner spline is formed on the surface to engage with the third outer spline and restrict the relative rotation of the damper member and the output member to a second predetermined angle smaller than the first predetermined angle; The damper member includes an elastic body and a second damper member which is provided on the inner peripheral surface of the elastic body and faces the first inner peripheral surface on which the third inner peripheral spline is formed and the outer peripheral surface of the output member in a non-fitted state. The third inner peripheral spline is separated from the elastic body in the axial direction of the input shaft.

As a result, the vehicular transfer device according to the embodiment of the present invention can increase the radial thickness of the elastic body of the damper member while preventing an increase in the radial dimension of the transfer device. It is possible to prevent deterioration of the durability of

A vehicle transfer device according to an embodiment of the present invention will be described below with reference to the drawings.
1 to 8 are diagrams showing a vehicle transfer device according to one embodiment of the present invention. In FIGS. 1 to 8, the vertical, front, rear, left, and right directions are the width direction of the vehicle, and the height of the vehicle, when the direction in which the vehicle equipped with the vehicle transfer device advances is the front, and the direction in which the vehicle moves backward is the rear. The direction is vertical.

First, the configuration will be explained.
As shown in FIG. 1, the vehicle 1 includes an engine 2, a power transmission mechanism 10, left and right front wheels 8L and 8R, and left and right rear wheels 9L and 9R. The front wheels 8L and 8R of this embodiment constitute the main driving wheels of the invention, and the rear wheels 9L and 9R constitute the auxiliary driving wheels of the invention.

The vehicle 1 drives left and right front wheels 8L and 8R and left and right rear wheels 9L and 9R with power output from an engine 2 arranged at the front of the vehicle.

The engine 2 is, for example, a four-cycle engine that performs a series of four strokes consisting of an intake stroke, a compression stroke, an expansion stroke and an exhaust stroke while a piston (not shown) makes two reciprocations in a cylinder. placed horizontally.

The piston is connected to a connecting rod (not shown) and a crankshaft, and the power of the engine 2 is output from the crankshaft to the transmission 3 of the power transmission mechanism 10 . The engine 2 of this embodiment constitutes the drive source of the present invention.

The power transmission mechanism 10 includes a transmission 3, a front differential 4, a vehicle transfer device (hereinafter referred to as a transfer device) 5, left and right front drive shafts 6L and 6R, left and right rear drive shafts 7L and 7R, and a propeller. It is configured including a shaft 11 and a rear differential 12 .

The transmission 3 includes a transmission mechanism 31, an input shaft 32, a counter shaft 33, a final drive gear 34, a reverse shaft 35, and a transmission case 36 housing these components.

The transmission mechanism 31 includes a plurality of input gears provided on the input shaft 32, a plurality of counter gears meshing with the input gears provided on the counter shaft 33, and a reverse gear provided on the reverse shaft 35. .

Input shaft 32 , counter shaft 33 and reverse shaft 35 are rotatably supported by transmission case 36 .

The transmission mechanism 31 changes the speed of the power of the engine 2 input to the input shaft 32 via the input gear and the counter gear, and outputs the power to the front differential 4 via the final drive gear 34 of the counter shaft 33 .

The front differential 4 has a final driven gear 37 that meshes with the final drive gear 34 and a differential case 38 that has the final driven gear 37 attached to its outer periphery and rotates together with the final driven gear 37 .

The front differential 4 includes a pinion shaft 40 fixed to the differential case 38, a pair of pinion gears 39A and 39B rotatably supported by the pinion shaft 40, meshing with the pinion gears 39A and 39B, and power transmitted from the pinion gears 39A and 39B. to the front wheels 8L, 8R via the left and right front drive shafts 6L, 6R.

The front drive shaft 6L is connected to the side gear 40A and rotates together with the side gear 40A. An intermediate shaft 41 (see FIG. 2) is connected to the side gear 40B, and the intermediate shaft 41 rotates integrally with the side gear 40B.

The front drive shaft 6R is connected to the intermediate shaft 41, and the front drive shaft 6R rotates together with the intermediate shaft 41. As shown in FIG.

As shown in FIGS. 2 to 4, the transfer device 5 has a transfer case 45 and a switching mechanism case 46. As shown in FIG. The switching mechanism case 46 is attached to the transfer case 45 with bolts 47 , and the transfer case 45 is attached to the transmission case 36 with bolts 48 .

As shown in FIG. 6, the intermediate shaft 41 is inserted through the transfer case 45 and extends in the vehicle width direction.

A hollow reduction drive shaft 51 is accommodated in the transfer case 45, and the reduction drive shaft 51 is rotatably supported by the transfer case 45 via ball bearings 52A and 52B.

An intermediate shaft 41 is inserted through the reduction drive shaft 51, and the intermediate shaft 41 is rotatably supported by a transfer case 45 via a ball bearing 52C.

The left end of the reduction drive shaft 51 is provided with a fitting portion 51A into which the outer peripheral portion of the differential case 38 is spline-fitted.

A reduction drive gear 51B is provided in the axial center of the reduction drive shaft 51 , and the reduction drive gear 51B rotates together with the reduction drive shaft 51 .

A transfer case 45 accommodates a reduction driven shaft 53 and a bevel gear 54 . The reduction driven shaft 53 is rotatably supported by the transfer case 45 by tapered roller bearings 55A and 55B.

A reduction driven gear 53 A is provided on the reduction driven shaft 53 , and the reduction driven gear 53 A rotates together with the reduction driven shaft 53 .

The reduction driven gear 53A meshes with the reduction drive gear 51B, and power is transmitted from the reduction drive gear 51B to the reduction driven gear 53A.

The bevel gear 54 is spline-fitted to the reduction driven shaft 53 and rotates together with the reduction driven shaft 53 .

A transfer pinion shaft 56 is accommodated in the transfer case 45 , and the transfer pinion shaft 56 is rotatably supported by the transfer case 45 via thrust ball bearings 57 .

The transfer pinion shaft 56 is orthogonal to the axial direction of the reduction driven shaft 53 and extends in the longitudinal direction of the vehicle 1 . A transfer pinion gear 56A is provided at the front end of the transfer pinion shaft 56, and the transfer pinion gear 56A meshes with the bevel gear 54. As shown in FIG. The transfer pinion shaft 56 of this embodiment constitutes the input shaft of the present invention.

As shown in FIG. 5, a dog 58 is provided on the opposite side of the thrust ball bearing 57 from the transfer pinion gear 56A. The dog 58 is spline-fitted to the outer peripheral surface of the transfer pinion shaft 56 and rotates together with the transfer pinion shaft 56 .

An outer peripheral spline 58 a is formed on the outer peripheral surface of the dog 58 . A hub 59 is provided on the outer periphery of the transfer pinion shaft 56 . The hub 59 is provided coaxially with the dog 58 so as to face the dog 58 with a gap in the longitudinal direction in the axial direction of the transfer pinion shaft 56 .

As shown in FIG. 7, the hub 59 has a tubular large diameter portion 59A and a tubular small diameter portion 59B having a smaller diameter than the large diameter portion. An outer peripheral spline 59a is formed on the outer peripheral portion of the small diameter portion 59B, and an inner peripheral spline 59b is formed on the inner peripheral portion of the small diameter portion 59B.

As shown in FIG. 6, a shift sleeve 60 (see FIG. 2) is provided on the outer periphery of dog 58 and hub 59. As shown in FIG. An inner peripheral spline 60 a is formed on the inner peripheral surface of the shift sleeve 60 , and the inner peripheral spline 60 a always meshes with the outer peripheral spline 59 a of the hub 59 .

As shown in FIG. 2, shift sleeve 60 is attached to shift fork 61 . The shift fork 61 is attached to a shift shaft 62, and the shift shaft 62 is slidably provided in the transfer case 45 so as to be axially movable.

An electric actuator 63 is provided on the top of the transfer case 45 (see FIG. 5). The electric actuator 63 is composed of, for example, an electric motor. The electric actuator 63 has a motor shaft 63A having a pinion gear 63a at its tip. Rack teeth 62a are formed in the axial direction of the shift shaft 62 (see FIG. 8), and a pinion gear 63a meshes with the rack teeth 62a.

When the pinion gear 63 a is rotated by the electric actuator 63 , the shift shaft 62 can move forward and backward in the axial direction, and the shift sleeve 60 can move in the axial direction of the transfer pinion shaft 56 .

As shown in FIG. 5 , a hollow output member 64 is provided on the outer peripheral portion of the transfer pinion shaft 56 . As shown in FIG. 7 , the output member 64 has a small-diameter cylindrical portion 65 and a cylindrical flange portion 66 protruding radially outward from the rear end of the cylindrical portion 65 . In other words, the cylindrical portion 65 extends away from the flange portion 66 in the axial direction of the output member 64 .

A transfer pinion shaft 56 is inserted through the inner circumference of the output member 64 , the inner circumference of the dog 58 and the inner circumference of the hub 59 . Here, the transfer pinion shaft 56, dog 58, hub 59 and output member 64 are installed so that their axial directions are parallel.

An outer peripheral spline 65 a is formed on the outer peripheral surface of the cylindrical portion 65 , and the outer peripheral spline 65 a is fitted to the inner peripheral spline 59 b of the hub 59 .

A pair of ball bearings 67A and 67B are provided between the output member 64 and the transfer pinion shaft 56. As shown in FIG. The output member 64 is rotatably supported by the transfer pinion shaft 56 via ball bearings 67A and 67B and rotates relative to the transfer pinion shaft 56 .

A gap is formed between the outer spline 65a of the output member 64 and the inner spline 59b of the hub 59 in the circumferential direction. The gap in the circumferential direction regulates the first predetermined angle θ1.

The dog 58 , hub 59 and output member 64 are housed in the switching mechanism case 46 , and the shift shaft 62 protrudes from the transfer case 45 into the switching mechanism case 46 .

As shown in FIG. 1 , the output member 64 is connected to the front end of the propeller shaft 11 , and the propeller shaft 11 rotates together with the output member 64 . A viscous coupling 81 is provided in the middle of the propeller shaft 11 .

A rear differential 12 is provided at the rear end of the propeller shaft 11, and the rear differential 12 distributes the power transmitted from the propeller shaft 11 to the rear wheels 9L, 9R via the rear drive shafts 7L, 7R.

When the electric actuator 63 moves the shift sleeve 60 away from the transfer pinion gear 56A, the inner spline 60a of the shift sleeve 60 is engaged only with the outer spline 59a of the hub 59, as shown in FIG.

At this time, power transmission from the dog 58 to the hub 59 is cut off, and the power of the engine 2 is not transmitted to the propeller shaft 11 .

Specifically, one power distributed by the front differential 4 is transmitted from the front drive shaft 6L to the front wheels 8L, and the other power distributed by the front differential 4 is transmitted from the intermediate shaft 41 via the front drive shaft 6R. is transmitted to the front wheels 8R.

Further, the power transmitted from the differential case 38 to the reduction drive shaft 51 is transmitted from the reduction drive gear 51B to the dog 58 via the reduction driven gear 53A, the reduction driven shaft 53, the bevel gear 54, the transfer pinion gear 56A, and the transfer pinion shaft 56. .

When the inner spline 60 a of the shift sleeve 60 is fitted only to the outer spline 59 a of the hub 59 , the transmission of power from the dog 58 to the hub 59 is cut off, and the power of the engine 2 is not transmitted to the propeller shaft 11 . . In this state, power is not transmitted from the hub 59 to the propeller shaft 11 via the output member 64, so the vehicle 1 runs in two-wheel drive.

On the other hand, when the shift sleeve 60 is moved toward the transfer pinion gear 56A by the electric actuator 63, the inner spline 60a of the shift sleeve 60 is engaged with the outer spline 58a of the dog 58 and the outer spline 59a of the hub 59 (Fig. 5).

At this time, the power of the engine 2 is transmitted from the dog 58 to the rear wheels 9L, 9R via the hub 59, the output member 64, the propeller shaft 11, the rear differential 12, and the rear drive shafts 7L, 7R. As a result, the vehicle 1 runs in four-wheel drive.

The dog 58, hub 59 and shift sleeve 60 of this embodiment form a switching mechanism for switching between two-wheel drive and four-wheel drive.

In FIG. 6, a damper member 68 is installed between the hub 59 and the output member 64 to absorb rotational fluctuations and torque fluctuations of the engine 2. The damper member 68 is installed at the rear end of the hub 59 in the axial direction. It is

In the transfer device 5 of this embodiment, the dog 58 is in communication with the engine 2, and the hub 59 is in communication with the rear wheels 9L and 9R via the damper member 68. As shown in FIG. In other words, the damper member 68 is installed downstream of the dog 58 on the power transmission path of the engine 2 .

As shown in FIG. 7, the damper member 68 is provided between an outer ring 68A, an inner ring 68B, and between the outer ring 68A and the inner ring 68B. body 68C.

As shown in FIGS. 5 and 8, the inner ring 68B includes an annular portion 68R having an inner peripheral surface 68r overlapping the inner peripheral portion of the elastic body 68C and the transfer pinion shaft 56 in the axial direction, and an elastic portion 68R with respect to the annular portion 68R. and an annular projection 68T projecting forward from the front end of the body 68C.

The inner peripheral surface 68r of the annular portion 68R faces the outer peripheral surface of the output member 64 in a non-engaged state with the outer peripheral surface of the output member 64, and the inner peripheral surface 68r of the annular portion 68R and the outer peripheral surface of the output member 64 are aligned. A minute gap through which oil can flow is formed between them.

An inner peripheral spline 68s is formed on an inner peripheral surface 68t of the annular protrusion 68T, and the inner peripheral spline 68s is separated axially forward of the transfer pinion shaft 56 from the elastic body 68C.

The inner ring 68B of this embodiment constitutes the inner peripheral member of the present invention. The inner peripheral surface 68t of the annular protrusion 68T constitutes the first inner peripheral surface of the present invention, and the inner peripheral surface 68r of the annular portion 68R constitutes the second inner peripheral surface of the present invention.

The outer ring 68A is press-fitted into the inner peripheral surface of the large-diameter portion 59A of the hub 59, and the damper member 68 rotates together with the hub 59. As shown in FIG.

An inner spline 68 s of the damper member 68 is fitted to an outer spline 65 a of the output member 64 . A gap is formed between the inner spline 68s of the damper member 68 and the outer spline 65a of the output member 64 in the circumferential direction.

This gap is smaller than the circumferential gap between the outer spline 65 a of the output member 64 and the inner spline 59 b of the hub 59 .

Thereby, the relative rotation between the damper member 68 and the output member 64 is smaller than the first predetermined angle θ1 due to the circumferential gap between the outer spline 65a of the output member 64 and the inner spline 68s of the inner ring 68B of the damper member 68. It is restricted to the second predetermined angle θ2.

A minute gap is formed between the inner peripheral surface of the inner ring 68B of the damper member 68 and the cylindrical portion 65 of the output member 64 to allow oil to pass therethrough.

A cylindrical member 69 is installed between the hub 59 and the output member 64 and at the front ends of the hub 59 and the output member 64 .

The cylindrical member 69 is installed rotatably relative to the output member 64 and prevents the eccentricity of the hub 59 with respect to the output member 64 . The cylindrical member 69 overlaps the inner spline 59b of the hub 59 in the axial direction of the transfer pinion shaft 56. As shown in FIG.

The dog 58 of this embodiment constitutes the first power transmission member of the invention, and the hub 59 constitutes the second power transmission member of the invention. The outer spline 58a of the dog 58 constitutes the first outer spline of the invention, and the outer spline 59a of the hub 59 constitutes the second outer spline of the invention.

The outer spline 65a of the output member 64 constitutes the third outer spline of the present invention, and the inner spline 60a of the shift sleeve 60 constitutes the first inner spline of the present invention. The inner spline 59b of the hub 59 constitutes the second inner spline of the present invention, and the inner spline 68s of the damper member 68 constitutes the third inner spline of the present invention.

A nut 70 is fastened to the central portion of the transfer pinion shaft 56 in the axial direction. The nut 70 abuts the rear end of the dog 58 , and the transfer pinion gear 56 A abuts the front end of the inner race 57 A of the thrust ball bearing 57 .

The transfer pinion shaft 56 is axially positioned and attached to the transfer case 45 by the nut 70 and the transfer pinion gear 56 A sandwiching the thrust ball bearing 57 and the dog 58 , and rotates together with the dog 58 .

A stepped portion 56a extending in the circumferential direction of the transfer pinion shaft 56 is formed in the axial center portion of the transfer pinion shaft 56, and the front end portion of the inner race 67c of the ball bearing 67B contacts the stepped portion 56a.

A stepped portion 64 a extending in the circumferential direction of the output member 64 is formed at a connecting portion between the cylindrical portion 65 and the flange portion 66 of the output member 64 . provided at a position overlapping in the axial direction of the A rear end portion of a damper member 68 is in contact with the stepped portion 64a.

Further, an axial gap is formed between the damper member 68 and the connecting portion between the large diameter portion 59A and the small diameter portion 59B of the hub 59 so that the hub 59 and the damper member 68 can rotate relative to each other.

A stepped portion 65b extending in the circumferential direction of the output member 64 is formed in the cylindrical portion 65 of the output member 64, and the stepped portion 65b is in contact with the front end portion (one axial end portion of the bearing) of the outer race 67b of the ball bearing 67A. in contact with A circlip 74 is provided on the inner peripheral surface of the flange portion 66 of the output member 64, and the circlip 74 is in contact with the rear end portion of the outer race 67b of the ball bearing 67A (the other axial end portion of the bearing). there is

That is, the ball bearing 67A is positioned in the axial direction of the transfer pinion shaft 56 by holding the outer race 67b between the stepped portion 65b and the circlip 74 in the axial direction of the transfer pinion shaft 56. cannot be moved to

In the output member 64, a stepped portion 65b is formed at the rear end of the outer race 67b of the ball bearing 67A (the other end in the axial direction of the bearing), and the front end of the outer race 67b of the ball bearing 67A (one end in the axial direction of the bearing) is formed. ) may be provided with a circlip 74 .

A nut 71 is fastened to the rear end portion of the transfer pinion shaft 56 . A spacer 72 is interposed between the nut 71 and the inner race 67a of the ball bearing 67A, and a spacer 73 is interposed between the inner race 67a of the ball bearing 67A and the inner race 67c of the ball bearing 67B. .

The front end of the inner race 67c of the ball bearing 67B contacts the stepped portion 56a, and the rear end of the inner race 67c of the ball bearing 67B contacts the spacer 73. As shown in FIG.

Therefore, when the nut 71 is fastened to the rear end portion of the transfer pinion shaft 56, the ball bearings 67A and 67B are sandwiched between the step portion 56a and the nut 71 via the spacers 72 and 73 in the axial direction of the transfer pinion shaft 56. be.

As a result, the output member 64 is positioned in the axial direction of the transfer pinion shaft 56 and becomes immovable in the axial direction of the transfer pinion shaft 56 .

The rear end portion of the inner ring 68B of the damper member 68 abuts on the stepped portion 64a of the output member 64, and the front end portion of the inner ring 68B of the damper member 68 is located between the large diameter portion 59A and the small diameter portion 59B of the hub 59. It abuts on the contact.

A circlip 77 is provided on the outer peripheral surface of the front end portion of the output member 64 , and the front end portion of the cylindrical member 69 contacts the circlip 77 . A rear end portion of the cylindrical member 69 is in contact with the inner peripheral spline 59 b of the hub 59 . The circlip 77 of this embodiment constitutes the clip member of the present invention.

As a result, the cylindrical member 69 , the hub 59 and the damper member 68 are sandwiched between the circlip 77 and the stepped portion 64 a in the axial direction of the transfer pinion shaft 56 , so that the damper member 68 is transferred to the output member 64 . It is positioned in the axial direction of the pinion shaft 56 and cannot move in the axial direction of the transfer pinion shaft 56 .

As shown in FIG. 8, a stepped portion 64b extending in the circumferential direction of the output member 64 is formed on the outer peripheral surface of the output member 64, and the stepped portion 64b is positioned forward of the stepped portion 64a. The stepped portion 64b is positioned between the circlip 77 and the stepped portion 64a in the axial direction of the output member 64, and the circlip 77 and the stepped portion 64a are positioned apart from the stepped portion 64b in the axial direction of the output member 64. is installed in

A rear end portion of an inner peripheral spline 68s of an inner ring 68B of the damper member 68 is in contact with the stepped portion 64a.

Thus, the cylindrical member 69 , the inner spline 59 b of the hub 59 and the inner spline 68 s of the damper member 68 are positioned in the axial direction of the output member 64 by the stepped portion 64 b and the circlip 77 . The stepped portion 64b of this embodiment constitutes the stepped portion of the present invention.

A ring member 78 is provided on the outer peripheral portion of the hub 59 . The ring member 78 is press-fitted into the inner peripheral portion of the flange portion 66 of the output member 64 and rotates together with the output member 64 .

An oil seal 75 is provided on the outer periphery of the ring member 78 , and the oil seal 75 overlaps the damper member 68 in the axial direction of the transfer pinion shaft 56 , that is, in the axial direction of the output member 64 . In other words, the oil seal 75 is installed side by side with the damper member 68 in a direction perpendicular to the axial direction of the transfer pinion shaft 56 .

The ball bearing 67A of this embodiment is located on the flange portion 66 side of the output member 64, and the ball bearing 67B is located on the projecting direction tip (front end) side of the cylindrical portion 65. As shown in FIG. The oil seal 75 is installed between the rear end of the ball bearing 67A and the front end of the ball bearing 67B in the axial direction of the transfer pinion shaft 56, and overlaps the ball bearing 67A in the axial direction of the transfer pinion shaft 56. .

Specifically, as shown in FIG. 5, the oil seal 75 is installed within a range L connecting the rear end portion of the ball bearing 67A and the front end portion of the ball bearing 67B in the axial direction of the transfer pinion shaft 56. there is

67 A of ball bearings located in the rear side of the ball bearing 67B are formed in a diameter direction larger than the ball bearing 67B. That is, the radial dimension of the ball bearing 67A is configured to be larger than the radial dimension of the ball bearing 67B.

The inner peripheral surface of the oil seal 75 is in close contact with the ring member 78 , and the outer peripheral surface of the oil seal 75 is in close contact with the switching mechanism case 46 . Therefore, the opening between the switching mechanism case 46 and the flange portion 66 of the output member 64 is closed by the oil seal 75 , and the inside of the switching mechanism case 46 is sealed by the oil seal 75 . Therefore, oil can be prevented from leaking from the inside of the switching mechanism case 46 .

The inner diameter of the oil seal 75 is larger than the outer diameters of the hub 59 , the damper member 68 , the cylindrical member 69 and the ring member 78 . The damper member 68 overlaps the oil seal 75 , the ring member 78 and the large diameter portion 59 A of the hub 59 in the axial direction of the transfer pinion shaft 56 .

An oil seal 79 is provided on the outer peripheral portion of the spacer 72 . The inner peripheral surface of the oil seal 79 is in close contact with the spacer 72 , and the outer peripheral surface of the oil seal 79 is in close contact with the flange portion 66 of the output member 64 .

As a result, the inside of the switching mechanism case 46 is sealed by the oil seal 79 , and oil can be prevented from leaking from the inside of the switching mechanism case 46 from between the output member 64 and the spacer 72 .

Inside the transfer pinion shaft 56, an oil passage 56B is formed through which oil for lubrication flows. The front end of the oil passage 56B is open, and the rear end of the oil passage 56B extends from the open end to the ball bearing 67A.

A radial hole 56C is formed in the transfer pinion shaft 56. The radial hole 56C extends radially from the oil passage 56B and has an open end in the extending direction.

The open end of the oil passage 56B is introduced with oil that is raked up by the bevel gear 54, and the oil flowing through the oil passage 56B is discharged outward from the radial hole 56C by the centrifugal force caused by the rotation of the transfer pinion shaft 56.

Here, the oil level of the oil O1 stored in the transfer case 45 and the oil level of the oil O2 stored in the switching mechanism case 46 are shown in FIG.

A through hole 73a is formed in the spacer 73, and the oil discharged outward from the radial hole 56C is introduced into the space between the ball bearings 67A and 67B through the through hole 73a of the spacer 73. . As a result, the ball bearings 67A and 67B are lubricated with oil.

A through-hole 65c is formed in the cylindrical portion 65 of the output member 64, and oil introduced into the space between the ball bearings 67A and 67B is discharged from the through-hole 65c, and is discharged from the inner ring 68B of the damper member 68. and the outer spline 65a of the output member 64 are lubricated.

An oil reservoir 76 is formed in a space between the output member 64 , the flange portion 66 and the ring member 78 . Specifically, the ring member 78 is provided on the outer peripheral portion of the oil reservoir 76, and surrounds the space between the output member 64 and the flange portion 66 from the outside, so that the oil is temporarily stored in the oil reservoir 76. be done.

The oil that has lubricated the inner spline 68s and the outer spline 65a passes through the gap between the cylindrical portion 65 of the output member 64 and the inner ring 68B of the damper member 68, and flows between the damper member 68 and the flange portion 66 of the output member 64. It is temporarily stored in the oil reservoir 76 .

On the other hand, the oil discharged from the through hole 65c lubricates the inner spline 59b of the hub 59 and the outer spline 65a of the output member 64, passes through the gap between the output member 64 and the cylindrical member 69, and flows through the dog 58. It is discharged radially outward through the gap between hubs 59 .

Oil discharged radially outward from the gap between dog 58 and hub 59 lubricates outer spline 58 a of dog 58 , outer spline 59 a of hub 59 , and inner spline 60 a of shift sleeve 60 .

Further, since a large amount of oil can be stored in the oil reservoir 76, the fitting surface between the inner ring 68B of the damper member 68 and the output member 64, the inner peripheral spline 59b of the hub 59, the outer peripheral spline 65a of the output member 64, and the cylindrical member 69 The lubricating performance of the fitting surface of the output member 64 can be improved.

Next, the action will be explained.
When the vehicle 1 is in two-wheel drive mode, the inner spline 60a of the shift sleeve 60 meshes only with the outer spline 59a of the hub 59 (see FIG. 6).

To switch from two-wheel drive to four-wheel drive, the shift shaft 62 is driven axially forward by the electric actuator 63 to move the shift sleeve 60 forward.

When the dog 58 and the hub 59 are synchronized, the inner spline 60a of the shift sleeve 60 meshes with the outer spline 58a of the dog 58, and the dog 58 and the hub 59 are connected through the shift sleeve 60.

At this time, after the power of the engine 2 is transmitted to the reduction drive shaft 51 via the transmission 3 and the differential case 38 of the front differential 4, the reduction drive gear 51B, the reduction driven gear 53A, the reduction driven shaft 53, the bevel gear 54, the transfer pinion shaft 56 and through dog 58 to hub 59 .

The power of the engine 2 is transmitted from the hub 59 to the output member 64, the propeller shaft 11, and the rear differential 12, distributed to the rear drive shafts 7L and 7R by the rear differential 12, and then transmitted to the rear wheels 9L and 9R. be. In FIG. 8, power transmission paths 82 and 83 in the transfer device 5 during four-wheel drive are indicated by arrows.

On the other hand, the inner spline 59b of the hub 59 and the outer spline 65a of the output member 64 restrict the relative rotation of the hub 59 and the output member 64 to the first predetermined angle θ1, and the outer spline 65a of the output member 64 and the damper member 68 The inner spline 68s of the inner ring 68B restricts the relative rotation between the output member 64 and the damper member 68 to a second predetermined angle θ2 smaller than the first predetermined angle θ1.

As a result, when rotational fluctuations and torque fluctuations of the engine 2 are input to the hub 59 during four-wheel drive, and the hub 59 and the output member 64 rotate relative to each other, the elastic body 68C of the damper member 68 elastically deforms, thereby 2 can absorb rotational fluctuations and torque fluctuations.

At this time, power is transmitted from the hub 59 to the output member 64 via the damper member 68 . In FIG. 8, a power transmission path 83 through which power is transmitted through the damper member 68 is indicated by a dashed arrow.

Next, the effect of the transfer device 5 of this embodiment will be described.
According to the transfer device 5 of this embodiment, the damper member 68 that rotates integrally with the hub 59 is provided between the hub 59 and the output member 64, and the outer peripheral spline 65a is formed on the outer peripheral surface of the output member 64. It is

The damper member 68 includes an elastic body 68C and an inner peripheral surface 68t provided on the inner peripheral surface of the elastic body 68C, on which an inner peripheral spline 68s is formed, and an inner peripheral surface facing the outer peripheral surface of the output member 64 in a non-fitted state. A tubular inner ring 68B having a surface 68r, and an inner spline 68s is separated axially forward of the transfer pinion shaft 56 with respect to the elastic body 68C.

As a result, the inner spline 68s is prevented from being located radially inward of the elastic body 68C, and the radial dimension of the elastic body 68C can be increased by the inner spline 68s.

Therefore, it is possible to increase the radial thickness of the elastic body 68C while preventing an increase in the radial dimension of the switching mechanism case 46, thereby preventing deterioration in the durability of the damper member 68. FIG.

In addition, since the inner ring 68B has an inner peripheral surface 68r that faces the outer peripheral surface of the output member 64 in a non-fitted state, the damper member 68 can be centered by the inner ring 68B, and the hub 59 can move radially. eccentricity can be prevented.

As a result, whirling of the damper member 68 can be prevented, and torque fluctuation and rotation fluctuation of the engine 2 can be more effectively absorbed by the damper member 68 .

As a result, the impact when the outer spline 58a of the dog 58 and the inner spline 60a of the shift sleeve 60, and the outer spline 59a of the hub 59 and the inner spline 60a of the shift sleeve 60 contact can be effectively reduced. It is possible to prevent the occurrence of rattling noise between the teeth.

Further, according to the transfer device 5 of this embodiment, the cylindrical member 69 rotatable relative to the output member 64 is installed between the hub 59 and the output member 64 in the radial direction of the transfer pinion shaft 56 .

The damper member 68 is installed at the rear end of the hub 59 , and the cylindrical member 69 is installed at the front end of the hub 59 so as to be positioned forward of the damper member 68 .

As a result, the centering of the hub 59 with respect to the output member 64 can be performed by the damper member 68 and the cylindrical member 69 .

Therefore, in addition to being able to more effectively prevent the damper member 68 from being radially eccentric, it is possible to prevent the hub 59 from being radially eccentric. As a result, whirling of the damper member 68 can be more effectively prevented, and torque fluctuations and rotation fluctuations of the engine 2 can be more effectively absorbed by the damper member 68 .

Further, according to the transfer device 5 of the present embodiment, the output member 64 includes a stepped portion 64b extending in the circumferential direction on the outer peripheral surface of the output member 64, and the output member 64 separated from the stepped portion 64b in the axial direction of the output member 64. and a circlip 77 provided on the outer periphery of the.

In addition, the cylindrical member 69 , the inner spline 59 b of the hub 59 and the inner spline 68 s of the damper member 68 are positioned in the axial direction of the output member 64 by the stepped portion 64 b and the circlip 77 .

As a result, the inner spline 59b of the hub 59 can be fitted to the outer spline 65a of the output member 64 without the damper member 68 interposed therebetween. Therefore, even if the damper member 68 deteriorates, the power of the engine 2 can be stably transmitted from the hub 59 to the output member 64 during four-wheel drive.

Here, the thrust ball bearing 57 that supports the transfer pinion shaft 56 is located in the front portion of the transfer pinion shaft 56 , and the thrust ball bearing 57 is separated forward from the rear portion of the transfer pinion shaft 56 . Also, the output member 64 is installed at the rear portion of the transfer pinion shaft 56 .

Therefore, the radial load generated on the transfer pinion shaft 56 increases toward the rear portion of the transfer pinion shaft 56 .

In the transfer device 5 of this embodiment, the inner spline 68s is separated from the elastic body 68C in the axial direction forward of the transfer pinion shaft 56, and the radial dimension of the elastic body 68C is increased by the inner spline 68s. can.

As a result, the radial dimension of the ball bearing 67A, which is behind the ball bearing 67B and overlaps the damper member 68 in the axial direction, can be made larger than the radial dimension of the ball bearing 67B. Therefore, the support rigidity of the transfer pinion shaft 56 and the output member 64 against the radial load acting on the rear portion of the transfer pinion shaft 56 can be ensured.

As a result, the transfer pinion 56 and the output member 64 can be prevented from being eccentric in the radial direction, and power can be smoothly transmitted from the transfer device 5 to the rear wheels 9L and 9R during four-wheel drive.

Although embodiments of the present invention have been disclosed, it will be apparent that modifications may be made by those skilled in the art without departing from the scope of the invention. All such modifications and equivalents are intended to be included in the following claims.

1... vehicle, 2... engine (driving source), 5... transfer device (vehicle transfer device), 8L, 8R... front wheels (main driving wheels), 9L, 9R... rear wheels (auxiliary drive wheel), 56...Transfer pinion shaft (input shaft), 58...Dog (first power transmission mechanism), 58a...Peripheral spline (first peripheral spline), 59... hub (second power transmission mechanism), 59a... outer spline (second outer spline), 59b... inner spline (second inner spline), 60... shift sleeve, 60a... Inner spline (first inner spline), 64: output member, 64b: stepped portion (stepped portion), 65a: outer spline (third outer spline), 68: damper Members, 68B... inner ring (inner peripheral member), 68r... inner peripheral surface (second inner peripheral surface), 68t... inner peripheral surface (first inner peripheral surface), 68s... Inner spline (third inner spline), 69... Cylindrical member, 77... Circlip (clip member),

Claims (3)

A vehicular transfer device capable of switching between two-wheel drive that transmits power from a drive source to main drive wheels and four-wheel drive that transmits power from the drive source to the main drive wheels and the auxiliary drive wheels,
an input shaft extending in the longitudinal direction of the vehicle and to which power is transmitted from the drive source;
a first power transmission member having a first outer spline formed on its outer periphery and rotating integrally with the input shaft;
a second power transmission member provided coaxially with the first power transmission member, the second power transmission member having a second outer peripheral spline formed on an outer peripheral portion thereof;
It has a first inner peripheral spline and is provided movably in the axial direction of the first power transmission member and the second power transmission member. By fitting only to the spline, transmission of power from the first power transmission member to the second power transmission member is interrupted, and the first inner peripheral spline is connected to the first outer peripheral spline during four-wheel drive. a shift sleeve that transmits power from the first power transmission member to the second power transmission member by fitting the spline and the second outer peripheral spline;
an output member that is provided rotatably relative to the input shaft and that transmits power to the sub-driving wheels;
a damper member provided between the second power transmission member and the output member and rotating integrally with the second power transmission member;
A third outer spline is formed on the outer peripheral surface of the output member,
A second power transmission member fitted to the third outer spline on the inner peripheral surface of the second power transmission member for restricting relative rotation between the second power transmission member and the output member to a first predetermined angle. An inner spline is formed,
A third spline is fitted on the inner peripheral surface of the damper member to the third outer spline to restrict relative rotation between the damper member and the output member to a second predetermined angle smaller than the first predetermined angle. The inner circumference spline of is formed,
The damper member includes an elastic body, and is provided on the inner peripheral surface of the elastic body and is not fitted to the first inner peripheral surface on which the third inner peripheral spline is formed and the outer peripheral surface of the output member. and a cylindrical inner peripheral member having opposing second inner peripheral surfaces,
A transfer device for a vehicle, wherein the third inner peripheral spline is separated from the elastic body in the axial direction of the input shaft. a cylindrical member rotatable relative to the output member is installed between the second power transmission member and the output member in the radial direction of the input shaft;
The damper member is installed at the rear end of the second power transmission member,
2. The transfer device for a vehicle according to claim 1, wherein the cylindrical member is installed at the front end portion of the second power transmission member so as to be located on the front side of the damper member. The output member includes a stepped portion extending in the circumferential direction on the outer peripheral surface of the output member, and a clip member installed on the outer peripheral surface separated from the stepped portion in the axial direction of the output member,
3. The apparatus according to claim 2, wherein the cylindrical member, the second inner spline, and the third inner spline are positioned in the axial direction of the output member by the stepped portion and the clip member. vehicle transfer device.

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