JPS6078834A - Driving equipment of all-wheel-drive vehicle - Google Patents

Abstract

PURPOSE:To reduce the axial length of an equipment for smaller size thereof by shaping a transmission gear so as to have a recess like a pot which is opened to a shaft-to-shaft differential gear and housing a planetary carrier in the recess as the carrier is able to make relative revolution with respect to the transmission gear. CONSTITUTION:A transmission gear 13 is disposed adjacently to a shaft-to-shaft differential gear 7 and turnably mounted on a transmission shaft 18. The transmission gear 13 is shaped to have a recess 13b like a pot which is opened to the differential gear 7. The planetary carrier 8 of the differential gear 7 is housed in the recess 13b as the carrier 8 is able to make relative turn. Both the carrier 8 and a supporting plate 9 have relatively opposed faces at the external peripheral ends and a reduction gear 6 is held between those opposed faces. Since the carrier 8 is housed in the gear 13, the axial area occupied by the gear 13 and the differential gear 17 may be reduced, and since the supporting plate 9 is disposed close to the carrier, the axial length of the differential gear 7 may be shortened.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a drive system for an all-wheel drive vehicle, particularly a reduction gear meshed with an output gear of a transmission; a planetary gear substitute inter-axle differential device arranged concentrically with the reduction gear to split the output; an inter-axle differential device to transmit the output of one of the axle differential devices to one of the two wheels a transmission shaft disposed concentrically with the device; and a transmission gear rotatably mounted on the transmission shaft to transmit the output of the other inter-axle differential device to the other two-wheel differential device; The present invention relates to a drive device for an all-wheel drive vehicle.

A drive of this kind is already known from GB 1228752. In this known drive device, two planetary gear type differential devices are arranged closely in parallel as the inter-axle differential device, and the reduction gear that meshes with the output gear of the transmission is the tenth differential device. is screwed onto the planet carrier of the second differential, and the support plate cradles the planet carrier of the second differential in a screw-like manner. These two differentials have a single common ring gear that meshes with parallel pinions of both differentials.

The drive power for the rear axle is derived from the sun gear of the first differential, and the carrier and sun gear of the second differential are each connected in a manner prevented from relative rotation to the two parts of the front axle. The two parts are mounted one within the other to allow relative rotation between them.

Such a known drive device is characterized by the fact that the drive from the tenth differential requires a relatively large space along the axial direction of the differential, and that the drive from the tenth differential requires a relatively large amount of space along the axis of the differential, and the second differential is connected to the pinion by a reverse rotation. Unless a gear is also provided, it is inconvenient in that the two parts of the front axle cannot be given rotation in the same sense, and as a result, assembly and manufacturing costs are extremely increased. Furthermore, the mounting of the ring gear and the support along the axial direction were also not satisfactory.

A first object of the present invention is to provide an all-wheel drive device for a drive vehicle that has a simplified structure and is reduced in size by reducing its axial length, in order to eliminate the above-mentioned drawbacks. .

In a first invention to achieve the first object, an inter-axle differential device includes a planetary gear rear and a support in which a ring gear, a pinion, and a sun gear are arranged close to each other along the axis of a transmission shaft and are rotatably supported. It is arranged between boards,
The transmission gear is formed in a pot shape with a recess facing the inter-axle differential, the planet carrier is accommodated in the recess so as to be relatively relatable, the reduction gear is carried by the planet carrier, and the sun gear or ring gear is connected to the transmission gear. Alternatively, it is connected to a transmission shaft.

A second object of the present invention is to provide a drive device for an all-wheel drive vehicle that, in addition to the effects of the first invention, prevents the reduction gear from collapsing.

In the second invention to achieve this second purpose, the first invention
In addition to the configuration of the invention, the reduction gear is sandwiched between the outer peripheral edges of the planetary carrier and the support plate and is screwed.

Hereinafter, embodiments of the present invention will be explained with reference to the drawings.
First, in FIG. 1, the driving force of the engine (not shown) is
The driving force that is transmitted to the input shaft 2 of the transmission 3 via the clutch 1 and also output from the output shaft 5 of the transmission 3 is transmitted from the output gear 4 integrated with the output shaft 5 via the reduction gear 6. It is input to the inter-axle differential device 7, and one output of the inter-axle differential device 7 is inputted from the transmission shaft 18 to the front wheel inter-wheel differential device 17.
The signal is transmitted to the pair of front wheel drive shafts 16 via the.

The other output of the inter-axle differential device 7 is transmitted from the transmission gear 13 to the rear wheel differential device (not shown) via the gear 14 and the bevel gear train 15, and is further transmitted to the rear wheel differential device (not shown). (not shown).

Referring also to FIG. 2, the inter-axle differential device 7 consists of a planetary carrier 8 and a support plate 9 that are disposed close to each other along the axial direction of a transmission shaft 18 parallel to the output shaft 5 of the transmission 3. A pinion 10, a sun gear 11, and a ring gear 12 are disposed between them to form a planetary type, and the ring gear 12 is held in its axial position by the planetary carrier 8 and the support plate 9.

Further, the pinion 10 is rotatably held by the planetary carrier 8. The support plate 9 is rotatably mounted on the transmission shaft 18 in the vicinity of the planetary carrier 8, and a connecting member 19 is arranged between the second support plate 9 and the pinion 10. The outer peripheral edge of this connecting member 19 is meshed with the ring gear 12,
The inner circumferential edge is coupled to a spline 18α cut on the transmission shaft 18. Therefore, the ring gear 12 and the transmission shaft 18
are substantially integrated via a connecting member 19.

The transmission gear 13 is connected to the transmission shaft 1 adjacent to the inter-axle differential device 7.
8 is rotatably mounted. Moreover, the transmission gear 13 has a hub 13α extending along the transmission shaft 18 toward the inter-axle differential device 7.
Moreover, it is formed in a pot shape with the recess 13b facing the inter-axle differential device 7 side. Recess 13 of this transmission gear 13
The planetary carrier 8 of the inter-axle differential 7 is housed in h so that it can rotate relative to it. Further, a sun gear 11 is carved on the outer surface of the end portion of the hub 13α.

The planetary carrier 8 and the support plate 9 have opposing surfaces that face each other formed on their outer peripheral edges, and the reduction gear 6 is held between these opposing surfaces. Furthermore, the planet carrier 8, the support plate 9, and the reduction gear 6 are integrally screwed together.

Further, a block means 20 is spline-coupled to the transmission shaft 18 and is movable in the axial direction between a position in which the transmission gear 13 is engaged and a position in which the transmission gear 13 is disengaged. This blocking means 20 substantially integrates the transmission gear 13 and the transmission shaft 18 by meshing with the transmission gear 13, and the inter-axle differential device 7
Cancels the differential mode function.

Next, to explain the operation of this embodiment, one driving force output from the output gear 4 of the transmission 3 is transmitted to the planetary carrier 8 and the support plate 9 (through the rotating gear 6, and is further supported by the planetary carrier 8). The driving force transmitted to the ring gear 12 is distributed to the sun gear 11 and the ring gear 12 by the pinion 10.The driving force transmitted to the ring gear 12 is transmitted from the connecting member 19 via the transmission shaft 18 to the front wheel differential 17, and the driving force is transmitted between the front wheels. One drive force is transmitted to the pair of left and right front wheels by the differential device 17. On the other hand, the drive force transmitted to the sun gear 11 is transmitted from the transmission gear 13 to the rear wheels (not shown) via the gear 14 and the bevel gear train 15. The signal is transmitted to the differential gear, and then to the pair of left and right rear wheels.

In such a drive device, since the planetary carrier 8 of the inter-axle differential device 7 is housed within the transmission gear 13, the area occupied by the transmission gear 13 and the inter-axle differential device 7 along the axial direction can be reduced. can. Further, since the support plate 9 is arranged close to the planetary carrier 8, the ring gear 12
can be efficiently mounted between the support plate 9 and the planetary carrier 8, and thereby also the axial length of the inter-axle differential device 7 can be reduced. In particular, when the axis of the engine, transmission 3, or inter-axle differential 7 extends transversely to the vehicle traveling direction, the axial length of the transmission including the inter-axle differential I as described above The decrease in
It would be beneficial. As a result, the drive shaft 16 equipped with a universal joint shaft (not shown) can be made relatively long. Thereby, the spring excursion can be made relatively thick, the wheel alignment force can be made smaller, and the inclination of the plurality of equal length universal joint axes can be reduced.

Further, the reduction gear 6 is sandwiched between a planetary carrier 8 and a support plate 9 from both sides, the planetary carrier 8 is rotatably supported in a recess 13b of the transmission gear 13, and the support plate 9 is rotatably supported on the transmission shaft 18. Since it is supported, the reduction gear 6 is supported on both sides, and its fall is reliably prevented.

FIG. 3 shows another embodiment of the invention, which is similar to the embodiment of FIG. An independent sun gear IIZ is splined to the transmission shaft 18 at positions corresponding to the knobs 13 . At point z, a connecting member 19a whose outer peripheral edge meshes with the ring gear 12 is spline-coupled. According to this embodiment, one driving force is transmitted from the ring gear 12 of the inter-axle differential 7 to the transmission gear 13 via the connecting member 19a, and the other driving force is transmitted from the sun gear 11α to the transmission shaft 18. .

As described above, according to the first invention, the inter-axle differential device includes:
A ring gear, a pinion, and a sun gear are arranged between a planet carrier and a support plate adjacent thereto, the transmission gear being pot-shaped with a recess facing the interaxle differential, and the planet carrier facing the recess. The reduction gear is supported by the planetary carrier, and the sun gear or ring gear is connected to the transmission gear or transmission shaft, making the transmission gear and inter-axle differential compact in the axial direction. It can be summarized as follows, and the structure is simple.

According to the second invention, in addition to the configuration of the first invention,
Since the reduction gear is sandwiched between the outer peripheral edges of the planetary carrier and the support plate and screwed together, the same effect as the first invention can be achieved, and the reduction gear can be supported from both sides. It can be securely and firmly fixed to the planet carrier and support plate. Moreover, since the planetary carrier and the support plate are each rotatably supported by other members, the reduction gear is supported on both sides.
The fall of the reduction gear is reliably prevented.

[Brief explanation of drawings]

Figures 1 and 2 show one embodiment of the present invention. Figure 1 is a schematic diagram of the device of the present invention, Figure 2 is an enlarged sectional view of the main part of Figure 1, and Figure 3 is an enlarged sectional view of the main part of Figure 1. FIG. 3 is an enlarged sectional view corresponding to FIG. 2 of another embodiment. 3...Transmission, 4...Output gear, 6...Reduction gear,
7... Inter-axle differential device, 8... Planet carrier, 9...
... Support plate, 10... Pinion, 11.11d... Sun gear, 12... Ring gear, 13... Transmission gear,
13 (L use place, 17... differential equipment between both wheels, 18
Transmission shaft patent applicant Honda Motor Co., Ltd.

Claims (2)

[Claims] (1) A reduction gear that meshes with the output gear of the transmission; a planetary gear gear that is arranged concentrically with the reduction gear in order to divide the M power from the nuclear reduction gear to a pair of front and rear wheel differentials and output it. an inter-axle differential; a transmission shaft disposed concentrically with the inter-axle differential to transmit one output of the inter-axle differential to the other inter-axle differential; and a transmission gear relatively rotatably mounted on the transmission shaft to transmit the output of the other side of the inter-axle differential to the device, the inter-axle differential comprising: A ring gear, a pinion, and a sun gear are disposed close to the transmission shaft along the axis and between a rotatably supported planetary carrier and a support plate, and the transmission gear is recessed in the inter-axle differential. The planet carrier is housed in the recess so as to be rotatable relative to the transmission gear, the reduction gear is carried by the idler carrier, and the sun gear or ring gear is connected to the transmission gear or the transmission shaft. A drive device for an all-wheel drive vehicle, characterized in that it is connected to. (2) A reduction gear that meshes with the output gear of the transmission; arranged concentrically with the reduction gear so that one driving force from the reduction gear is divided and outputted to a pair of front and rear IP differentials. a planetary gear substitute inter-axle differential; a transmission shaft disposed concentrically with the inter-axle differential for transmitting one output of the vehicle+ll+ differential to one of the wheels; a transmission gear that is relatively rotatably mounted on the transmission shaft to transmit the output of the other of the inter-axle differential devices to the two-wheel differential device; The differential device includes a ring gear, a pinion, and a sun gear, which are disposed between a support plate and a planetary carrier that is disposed close to each other along the axis of a transmission shaft and rotatably supported, and the transmission gear is a differential between axles. It is formed in a pot shape with a recess facing the device, the planetary key carrier is housed in the recess so as to be rotatable relative to the transmission gear, and the reduction gear is sandwiched between the outer peripheral edges of the planetary carrier and the support plate. 1. A drive device for an all-wheel drive vehicle, wherein the sun gear or ring gear is connected to the transmission gear or the transmission shaft.