JP7306155B2 - vehicle power transmission - Google Patents

Description

The present invention relates to a vehicle power transmission 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 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. Equipped with a hub.

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.

A shift sleeve for switching between 2WD and 4WD is always in mesh with the power transmission teeth of the output gear. By meshing with both of the power transmission teeth, power can be transmitted from the power transmission shaft to the power output shaft.

A cushioning 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. When rotational fluctuations due to engine torque fluctuations or the like occur between the inner hub and the outer hub, the cushioning member elastically deforms to absorb the rotational fluctuations of the power transmission shaft.

Japanese Utility Model Laid-Open No. 60-23321

In such a conventional transfer, since the buffer member is installed on the power transmission shaft, the power transmission shaft is lengthened in the axial direction by the length of the buffer member. Furthermore, if a component such as an oil seal, which constitutes the transfer device, is installed in the axial direction of the power transmission shaft, the power transmission shaft will be further elongated in the axial direction by the oil seal or the like. Therefore, the size of the transfer may increase.

The present invention has been made in view of the circumstances described above, and by optimizing the installation positions of the oil seal and the damper member, it is possible to prevent the axial lengths of the power transmission member and the output member from increasing. It is an object of the present invention to provide a power transmission device for a vehicle that can be downsized.

The present invention comprises a case member, a power transmission member that is rotatably accommodated in the case member and that transmits power from a drive source, and a power transmission member that is provided coaxially with the power transmission member and transmits power from the power transmission member. a ring member, an oil seal, and a damper member, wherein the output member includes a flange portion and a diameter smaller than that of the flange portion; and a cylindrical portion extending along the axial direction of the power transmission member, the ring member being positioned on the outer peripheral portion of the cylindrical portion and press-fitted into the flange portion, and the oil seal The damper member is installed between the case member and the ring member so as to block an opening between the case member and the flange portion, and the damper member absorbs fluctuations of the drive source. and the cylindrical portion, and the damper member overlaps the oil seal in the axial direction of the output member.

As described above, according to the present invention, by optimizing the installation positions of the oil seal and the damper member, it is possible to prevent the shaft lengths of the power transmission member and the output member from becoming long, thereby reducing the size of the vehicle power transmission device. can be improved.

FIG. 1 is a plan view of a vehicle equipped with a vehicle power transmission device according to an embodiment of the present invention. FIG. 2 is an exploded perspective view of a vehicle power transmission device according to one embodiment of the present invention. FIG. 3 is a plan view of a vehicle power transmission device according to one embodiment of the present invention. FIG. 4 is a right side view of the vehicle power transmission 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 power transmission 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 power transmission device according to the embodiment of the present invention. FIG. 9 is a diagram showing a vehicle power transmission device according to an embodiment of the present invention, showing a state in which the switching mechanism is removed from the transfer device. FIG. 10 is a diagram showing a vehicular power transmission system according to an embodiment of the present invention, showing the flow of lubricating oil.

A vehicle power transmission device according to an embodiment of the present invention includes a case member, a power transmission member rotatably accommodated in the case member and to which power is transmitted from a drive source, and a power transmission member coaxially with the power transmission member. A power transmission device for a vehicle comprising: an output member provided to transmit power from the power transmission member; a ring member; an oil seal; and a cylindrical portion extending from the flange portion along the axial direction of the power transmission member. The ring member is positioned on the outer peripheral portion of the cylindrical portion and press-fitted into the flange portion. , is installed between the case member and the ring member so as to block the opening between the case member and the flange portion, and the damper member is provided between the power transmission member and the cylindrical portion so as to absorb fluctuations of the drive source. A damper member is positioned between and overlaps the oil seal axially of the output member.

As a result, the vehicle power transmission device according to the embodiment of the present invention can prevent the axial length of the vehicle power transmission device from increasing by optimizing the installation positions of the oil seal and the damper member. miniaturization can be achieved.

DETAILED DESCRIPTION OF THE INVENTION A vehicle power transmission system according to an embodiment of the present invention will be described below with reference to the drawings.

1 to 10 are diagrams showing a vehicle power transmission system according to one embodiment of the present invention. In FIGS. 1 to 10, 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 power transmission device advances is the front, and the direction in which the vehicle moves backward is the rear. The horizontal direction is the vertical direction.

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 transfer device 5 of this embodiment constitutes the vehicle power transmission device of the present invention.

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 . The transfer case 45 and switching mechanism case 46 of this embodiment constitute the case member of the present invention.

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 cylindrical large diameter portion 59A and a cylindrical small diameter portion 59B smaller in 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 . The ball bearings 67A and 67B of this embodiment constitute the bearing of the present invention.

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 fluctuations in rotation and torque of the engine 2 . 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.

The inner ring 68B has an annular protrusion 68a projecting forward from the front end of the elastic body 68C, and an inner peripheral spline 68s is formed on the inner peripheral surface of the annular protrusion 68a.

As shown in FIG. 5, 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.

Between the hub 59 and the output member 64 and at the front ends of the hub 59 and the output member 64, a cylindrical member 69 is installed so as to be relatively rotatable with the output member 64. eccentricity of the hub 59 is prevented. 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 power transmission member and 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 inner spline 60a of the shift sleeve 60 constitutes the first 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 nut 70 of this embodiment constitutes the fastening member of the present invention.

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 is formed on the outer peripheral surface of the transfer pinion shaft 56 at 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 abuts against the stepped portion 56a. there is

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 cylindrical portion 65 of the output member 64 is formed with a stepped portion 65b extending in the circumferential direction on the inner peripheral surface of the output member 64. The stepped portion 65b is formed at the front end portion of the outer race 67b of the ball bearing 67A (one axial end of the bearing). part) are in contact with each other. 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 The stepped portion 64a of this embodiment constitutes the stepped portion of the present invention.

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 .

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 oil seal 75 of this embodiment constitutes the oil seal of the present invention.

The ball bearing 67A of this embodiment is located on the flange portion 66 side of the output member 64 in the axial direction of the transfer pinion shaft 56, and the ball bearing 67B is located on the tip (front end) side of the cylindrical portion 65 in the projecting direction. positioned. The ball bearing 67A of this embodiment constitutes the first bearing of the invention, and the ball bearing 67B constitutes the second bearing of the invention.

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

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 flow of lubricating oil will be shown below with reference to FIG.
FIG. 10 shows 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. As shown in FIG.

As shown by oil O3 in FIG. 10, the oil that is raked up by the bevel gear 54 is introduced into the open end of the oil passage 56B, and the oil that flows through the oil passage 56B is forced into a radial hole by centrifugal force due to the rotation of the transfer pinion shaft 56. It is discharged outward from 56C.

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. (See Oil O4). 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 (see oil O5).

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 (see oil O6).

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 the hubs 59 (see oil O7).

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 .

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 for 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.
The transfer device 5 of this embodiment includes a switching mechanism case 46, a hub 59 rotatably housed in the switching mechanism case 46 and to which power is transmitted from the engine 2, and an output member 64 provided coaxially with the hub 59. , a ring member 78 , an oil seal 75 and a damper member 68 .

The output member 64 has a flange portion 66 and a cylindrical portion 65 having a smaller diameter than the flange portion 66 and extending from the flange portion 66 along the axial direction of the transfer pinion shaft 56 .

The ring member 78 is positioned on the outer peripheral portion of the cylindrical portion 65 and is press-fitted into the flange portion 66 . 46 and the ring member 78 .

A damper member 68 is installed between the hub 59 and the cylindrical portion 65 so as to absorb fluctuations of the engine 2 , and the damper member 68 overlaps the oil seal 75 in the axial direction of the output member 64 .

The ring member 78 press-fitted into the flange portion 66 of the output member 64 allows the damper member 68 and the oil seal 75 to overlap in the axial direction of the transfer pinion shaft 56.
The installation positions of the oil seal 75 and the damper member 68 can be optimized.

As a result, the damper member 68 can be installed in the installation range of the oil seal 75 in the axial direction of the transfer pinion shaft 56, and the shaft lengths of the transfer pinion shaft 56, the hub 59, the output member 64, etc. can be prevented from becoming long. . As a result, the size of the transfer device 5 can be reduced, and the mountability of the transfer device 5 on the vehicle 1 can be improved.

Further, according to the transfer device 5 of this embodiment, the switching mechanism case 46 accommodates the transfer pinion shaft 56 that transmits power from the engine 2 to the hub 59 .

The flange portion 66 and the cylindrical portion 65 of the output member 64 are formed in a hollow shape, and the transfer pinion shaft 56 is installed on the inner peripheral portion of the output member 64 and communicates with the output member 64 via ball bearings 67A and 67B. Relatively rotatable.

As a result, the output member 64, the damper member 68, and the oil seal 75 can be overlapped in the axial direction of the transfer pinion shaft 56, the shaft length of the output member 64 is shortened, and the output member 64 is supported on the transfer pinion shaft 56. can.

Therefore, it is possible to further reduce the size of the transfer device 5, and to improve the mountability of the transfer device 5 on the vehicle 1 more effectively.

Further, according to the transfer device 5 of the present embodiment, the ball bearing 67A located on the flange portion 66 side in the axial direction of the transfer pinion shaft 56 and the ball bearing 67A on the tip portion side of the projection direction of the cylindrical portion 65 with respect to the ball bearing 67A. The oil seal 75 overlaps the ball bearing 67A in the axial direction of the transfer pinion shaft 56 .

The output member 64 is supported by ball bearings 67A and 67B. Least eccentricity. Therefore, the oil seal 75 can be prevented from tilting by overlapping the ball bearing 67A and the transfer pinion shaft 56 in the axial direction of the output member 64 where the eccentricity of the output member 64 is minimized.

Therefore, the sealing performance of the oil seal 75 can be improved, and the inner peripheral surface of the oil seal 75 with which the ring member 78 contacts can be prevented from being unevenly worn, thereby improving the durability of the oil seal 75 .

In addition, the transfer device 5 of this embodiment has a dog 58 formed with an outer peripheral spline 58a on its outer peripheral portion and rotating integrally with the transfer pinion shaft 56. The hub 59 has an outer peripheral spline 59a formed on its outer peripheral portion. It is provided coaxially with the dog 58 .

The transfer device 5 has a shift sleeve 60 which has an inner spline 60a and is movably provided in the axial direction of the dog 58 and the hub 59 (the axial direction of the transfer pinion shaft 56).

The shift sleeve 60 blocks transmission of power from the dog 58 to the output member 64 by engaging only the outer spline 59a with the inner spline 60a during two-wheel drive, and the inner spline 60a is fitted with the outer spline 59a during four-wheel drive. Power is transmitted from dog 58 to hub 59 by engaging 58a with peripheral spline 59a.

Further, according to the transfer device 5 , a 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 . A cylindrical member 69 for preventing radial eccentricity of the hub 59 is installed at a position overlapping the outer spline 59 a in the axial direction of the transfer pinion shaft 56 .

In addition to this, the transfer device 5 is fastened to the transfer pinion shaft 56 between the transfer pinion shaft 56 and the cylindrical portion 65 of the output member 64 in the radial direction of the transfer pinion shaft 56 so that the transfer pinion shaft 56 is connected to the switching mechanism case. A nut 70 is provided which secures to 46 .

Since the output member 64 and the relatively rotatable cylindrical member 69 are installed between the hub 59 and the output member 64, the output member 64, which is relatively rotatably provided on the transfer pinion shaft 56 which is the rotation center, The radial eccentricity of the hub 59 can be prevented. As a result, the outer spline 58a of the dog 58 and the outer spline 59a of the hub 59 can be prevented from radially shifting.

Therefore, the inner spline 60a of the shift sleeve 60 can be smoothly meshed with the outer spline 58a of the dog 58 when switching from two-wheel drive to four-wheel drive. For this reason, it is possible to prevent deterioration in the switching performance from two-wheel drive to four-wheel drive.

Furthermore, since the cylindrical member 69 overlaps the outer spline 59a of the hub 59 in the axial direction of the transfer pinion shaft 56, the radial deviation of the outer spline 58a of the dog 58 and the outer spline 59a of the hub 59 can be prevented more effectively. can be prevented.

In addition, since the nut 70, the cylindrical member 69, and the outer spline 59a are overlapped in the axial direction of the transfer pinion shaft 56, the shaft lengths of the transfer pinion shaft 56, the hub 59, the output member 64, and the like are increased. This can be prevented more effectively, and the size of the transfer device 5 can be further reduced.

Further, according to the transfer device 5 of the present embodiment, the output member 64 is positioned at the connecting portion between the cylindrical portion 65 and the flange portion 66, and the stepped portion 64a extending in the circumferential direction of the output member 64 and the projecting portion of the cylindrical portion 65 and a circlip 77 provided at the tip of the direction.

The cylindrical member 69, the hub 59, and the damper member 68 are sandwiched between the stepped portion 64a and the circlip 77 in the axial direction of the transfer pinion shaft 56, so that they are installed on the outer peripheral portion of the cylindrical portion 65 to provide an oil seal. The inner diameter of 75 is larger than the outer diameters of cylindrical member 69 , hub 59 and damper member 68 .

As a result, as shown in FIG. 9, the output member 64, hub 59 and damper member 68 are attached to the oil seal 75 while the output member 64, hub 59 and damper member 68 are assembled to the switching mechanism case 46 to form a unit. By assembling the transfer pinion shaft 56 and the dog 58 through the inner peripheral surface, the transfer device 5 can be assembled.

Therefore, the number of man-hours for assembling the transfer device 5 can be reduced, the work time for assembling the transfer device 5 can be shortened, and the workability of the work for assembling the transfer device 5 can be improved.

Further, according to the transfer device 5 of this embodiment, the transfer pinion shaft 56 extends in the axial direction of the transfer pinion shaft 56, and extends in the radial direction of the transfer pinion shaft 56 from the oil passage 56B through which the oil flows. , and a radial hole 56C through which the oil flowing through the oil passage 56B is discharged.

The cylindrical portion 65 of the output member 64 is formed with a through hole 65c through which the oil that has passed through the through hole 73a of the spacer 73 flows from the radial hole 56C. An oil reservoir 76 is formed in which the oil that has flowed through is stored.

As a result, the oil stored in the oil reservoir 76 lubricates the fitting surfaces of the inner ring 68B of the damper member 68 and the output member 64, lubricates the inner spline 59b of the hub 59 and the outer spline 65a of the output member 64, The lubricating performance of the fitting surfaces of the cylindrical member 69 and the output member 64 can be improved.

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 (drive source), 5... transfer device (vehicle power transmission device), 8L, 8R... front wheels (main driving wheels), 9L, 9R... rear Wheel (sub-drive wheel), 45...Transfer case (case member), 46...Switching mechanism case (case member), 56...Transfer pinion shaft (input shaft), 56B...Oil passage, 56C ... radial hole, 58 ... dog (first power transmission member), 58a ... outer peripheral spline (first outer peripheral spline), 59 ... hub (power transmission member, second power transmission member) ), 59a... Peripheral spline (second outer spline), 60... Shift sleeve, 60a... Inner spline (first inner spline), 64... Output member, 64a... Step portion, 65... Cylindrical portion, 65c... Through hole, 66... Flange portion, 67A... Ball bearing (first bearing), 67B... Ball bearing (second bearing), 68... Damper member, 69... Cylindrical member, 70... Nut (fastening member), 75... Oil seal, 77... Circlip (clip member), 78... Ring member

Claims (6)

a case member;
a power transmission member that is rotatably accommodated in the case member and that transmits power from a drive source; an output member that is provided coaxially with the power transmission member and transmits power from the power transmission member; and a ring member. , an oil seal, and a damper member, a power transmission device for a vehicle,
The output member has a flange portion and a cylindrical portion having a smaller diameter than the flange portion and extending from the flange portion along the axial direction of the power transmission member,
The ring member is positioned on the outer peripheral portion of the cylindrical portion and is press-fitted into the flange portion,
The oil seal is installed between the case member and the ring member so as to close an opening between the case member and the flange,
The damper member is installed between the power transmission member and the cylindrical portion so as to absorb fluctuations of the drive source,
A power transmission device for a vehicle, wherein the damper member overlaps the oil seal in the axial direction of the output member. The case member houses an input shaft that transmits power from the drive source to the power transmission member,
The flange portion and the cylindrical portion of the output member are formed in a hollow shape,
2. The power transmission device for a vehicle according to claim 1, wherein the input shaft is installed on the inner peripheral portion of the output member and is rotatable relative to the output member via a plurality of bearings. The plurality of bearings include a first bearing located on the flange portion side in the axial direction of the input shaft, and a second bearing located on the distal end side of the cylindrical portion in the projecting direction of the first bearing. a bearing;
3. The vehicle power transmission device according to claim 2, wherein the oil seal overlaps the first bearing in the axial direction of the input shaft. A vehicular power transmission device capable of switching between two-wheel drive for transmitting power from the drive source to the main drive wheels and four-wheel drive for transmitting power from the drive source to the main drive wheels and the auxiliary drive wheels,
When the power transmission member is a second power transmission member, the first power transmission member has a first outer spline formed on an outer peripheral portion and rotates integrally with the input shaft,
The second power transmission member has a second outer spline formed on an outer peripheral portion thereof, and is provided coaxially with the first power transmission member,
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, and the first inner peripheral spline is aligned with the second power transmission member during two-wheel drive. By engaging only the outer spline, transmission of power from the first power transmission member to the output member is interrupted, and in four-wheel drive, the first inner spline and the first outer spline are connected to each other. a shift sleeve that transmits power from the first power transmission member to the second power transmission member by being fitted to a second peripheral spline;
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 cylindrical member is installed at a position overlapping the second outer spline in the axial direction of the input shaft,
A fastening member that is fastened to the input shaft and fixes the input shaft to the case member is provided between the input shaft and the cylindrical portion of the output member in a radial direction of the input shaft. The vehicle power transmission device according to claim 2 or 3. The output member has a step portion extending in the circumferential direction of the output member positioned at a connecting portion between the cylindrical portion and the flange portion, and a clip member provided at a distal end portion of the cylindrical portion in a projecting direction. ,
The cylindrical member, the second power transmission member, and the damper member are sandwiched between the stepped portion and the clip member in the axial direction of the input shaft so as to be installed on the outer peripheral portion of the cylindrical portion,
5. The vehicle power transmission device according to claim 4, wherein the inner diameter of the oil seal is larger than the outer diameters of the cylindrical member, the second power transmission member and the damper member. . The input shaft has an oil passage extending in the axial direction of the input shaft through which oil flows, and a radial hole extending from the oil passage in the radial direction of the input shaft and through which the oil flowing through the oil passage is discharged. ,
A through hole through which oil flows is formed in the cylindrical portion of the output member,
6. The vehicle power transmission according to claim 4, wherein the damper member, the output member, and the ring member form an oil reservoir in which oil that has flowed through the through hole is stored. Device.

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