JPH03208732A - Transfer - Google Patents

Abstract

PURPOSE:To reduce the size of a differential mechanism by housing a planetary gear type differential mechanism in a space for high-low switching part having an auxiliary shaft provided on the output side of a transmission, causing the auxiliary shaft to support it, and interlocking the output side of the differential mechanism with respective transmission shafts of front and rear wheels. CONSTITUTION:In a transfer 5 which distributes driving force of an engine to a front wheel side and a rear wheel side, a planetary spur gear type center differential 33 is placed on one side of the output shaft 25 of a transmission 3 in parallel with the output shaft and its internal gear 35 is formed on a rotary member 39 rotatably supported by a shaft on a case 23. A spur gear 41 is formed on the rotary member 39 to be engaged with a spur gear 31 on the output shaft 25. The internal gear 35 is engaged with a planetary gear 43 rotatably supported by a shaft on a hollow planetary carriers 47, 49, while the planetary gear 43 is also engaged with a sun gear 51 on an auxiliary shaft 35. A spur ger 63 formed on the carrier 49 and a spur gear 65 formed on the auxiliary shaft 35 are engaged with spur gears 67, 69 on transmission shafts 71, 73 on the rear wheel side and the front wheel side which are coaxial on inner and outer sides.

Description

[Detailed description of the invention] [Purpose of the invention] (Industrial application field) The present invention relates to vehicle transfer.

(Prior art) JP-A-62-181922, JP-A-62181923
The transfer is described in the publication. As shown in FIG. 3, in these transfers, a planetary spur gear type center differential 201 (center differential device) is used and is arranged coaxially with an output shaft 205 of a transmission 203. The driving force of the engine is input from the output shaft 205 to the internal gear 207, and the divided output driving force is sent from the planetary carrier 209 to the rear wheel side via the shaft 211, and from the sun gear 213 to the hollow shaft 215 and the gear assembly. 217, and is sent to the front wheels via the counter shaft 219. The shaft 211 is inserted into the hollow shaft 215.

(Problem to be Solved by the Invention) Incidentally, in a sports type or off-road type four-wheel drive (4WD) vehicle, it is desirable that the driving force on the rear wheel side is large. In such a case, as in this embodiment, the shaft 21 on the rear wheel side
1 is connected to the planetary carrier 209 which has a larger output torque than the sun gear 213. However, the larger the transmitted torque, the larger the diameter of the shaft 211 is.
The whole thing becomes large. Therefore, even if the high-low switching gear of a part-time 4WD vehicle is removed, the center differential 201 cannot be housed, and this case cannot be shared.

Therefore, an object of the present invention is to provide a transfer that can increase the driving force on the rear wheel side without increasing the size, and that allows the transfer case to be shared with a part-time 4WD vehicle.

[Structure of the Invention] (Means for Solving the Problems) The transfer of the present invention includes a space for a high-low switching section having a subshaft on the output side of the transmission of a four-wheel drive vehicle, and on the output side of this space, It has a front wheel side transmission shaft and a rear wheel side transmission shaft arranged coaxially on the inside and outside, and a differential mechanism of a planetary spur gear is housed in the space for the high-low switching part and supported on the countershaft, and the differential mechanism is The present invention is characterized in that the transmission output side is interlocked with the input side, and both the transmission shafts are interlocked with the output side.

(Function) Even if the distribution of driving force to the rear wheels is increased and the rear wheel transmission shaft is made thicker, the differential mechanism does not become larger, and an increase in size can be prevented.

If you remove the differential mechanism, you can use the countershaft to store the high-low switching gear.

(Example) One embodiment will be explained with reference to FIG. 1 and FIG. 2.

FIG. 2 is a schematic diagram showing the power system of a vehicle using this embodiment. Hereinafter, the left and right directions are the directions in these drawings, and the upper part of FIG. 1 corresponds to the front of this vehicle (the upper part of FIG. 2). Note that members without numbers are not shown.

The power system of the vehicle shown in Fig. 2 includes an engine 1, a transmission 3, a transfer 5 in this embodiment, a propeller shaft 7 on the front wheel side, a front differential 9 (differential device on the front wheel side), a propeller shaft 11 on the rear wheel side, and a rear differential. 13 (differential device on the rear wheel side), left and right front wheels 1
5.17, left and right rear wheels 19.21, etc.

The transfer 5 is housed in a transfer case 23, and the output shaft 25 of the transmission 3 passes through the front end of the case 23 and is supported by a bearing 27. Two seals are arranged between the shaft 25 and the case 23. A spur gear 31 is attached to the rear end of the output shaft 25 passing through.
are integrally formed.

A planetary spur gear type center differential 33 (differential mechanism) is arranged on the left side of the output shaft 25 and parallel thereto. The internal gear 35 is formed of three rotating members supported by the case 23 by bearings 37. A spur gear 41 is formed in front of the internal gear 35 in the rotating member 39 and meshes with the spur gear 31 .

In this way, the center differential 33 rotates in conjunction with the output shaft 25, and is rotationally driven by the driving force from the engine l.

A planetary gear 43 meshing with the internal gear 35 is rotatably supported on a shaft 45, and both ends of the shaft 45 are supported by hollow planetary carriers 47 and 49 arranged on both the front and rear sides. A sun gear 51 that meshes with the planetary gear 43 is integrally formed on the subshaft 53. The front end of this subshaft 553 is supported by the three rotating members by a bearing 55, and the rear end is supported by the case 23 by a bearing 57. The front carrier 47 is supported by the three rotating members by bearings 59, and the four rear carriers are supported by the shaft 53 by bearings 61.

Therefore, the rotation of the internal gear 35 is dividedly outputted to the carriers 47, 49 and the shaft 53, and differentially distributed to each side due to the rotation and revolution of the planetary gear 43.

Spur gears 63 are formed on the four carriers, spur gears 65 are integrally formed on the shaft 53, and spur gears 67.
69 and mesh with each other. The spur gear 67 is attached to the front end of the rear wheel transmission shaft 71, and the spur gear 69 is attached to the front end of the hollow front wheel transmission shaft 7.
3 are integrally formed at the front end of each. Each axis 71, 7
3 is disposed coaxially with the output shaft 25, and the holder 7 is inserted into the hollow shaft 73. The shaft 73 is a bearing 75
The shaft 71 is supported by a bearing 77, and is supported by a shaft 71 by a bearing 77. The shaft 71 is supported on the shaft 73 by a bearing 79 and in the case 23 by a bearing 81.

Therefore, the four carriers rotate in conjunction with the shaft 71, and the shaft 53 rotates in conjunction with the shaft 73. Moreover, due to such a transmission structure, the arrangement of inside and outside is reversed, and the rotation of the inside shaft 53 is caused by the rotation of the outside shaft 7.
3, and the rotation of the outer carrier 4 is transmitted to the inner shaft 7.
1.

The shaft 71 passes through the rear end of the case 23 and is connected to the propeller shaft 11 on the rear wheel side. A seal 83 is arranged between the case 23 and the shaft 71 side. Further, a timing gear 85 is spline connected to the shaft 73 and positioned by a stepped portion 87 and a retaining ring 89. This timing gear 85 is connected by a timing belt 91 to a timing gear on the front wheel side output shaft disposed on the left side, and this output shaft passes through the left front end of the case 23 and is connected to the front wheel side propeller shaft 7 side. ing.

In this way, the transfer 5 is constructed.

The rotational driving force of the engine 1 is shifted by a transmission 3 and transmitted to a front differential 9 and a rear differential 13 via a transfer 5. The transmitted driving force is divided and outputted by the front differential 9 to the left and right front wheels 15, 17, and by the rear differential 13 to the left and right rear wheels 21, respectively.

Differential movement between the front and rear wheels is allowed by the center differential 33, and differential movement between the left and right of the front and rear wheels is allowed by the front differential 9 and the rear differential 13, respectively. Therefore, the vehicle can turn smoothly, maintain good straight-line stability on uneven roads, and prevent tight corner braking when making sharp turns at low speeds.

In the center differential 33, the rear wheel side is connected to the four planetary carriers and the front wheel side is connected to the sun gear 51, so the proportion of driving force distributed to the rear wheel side is large, and large driving force is effectively transmitted to the road surface during acceleration. This makes it possible to obtain a vehicle with a driving force distribution ratio suitable for sports types, off-road types, etc. Further, unlike the conventional example, it is not necessary to insert the shaft on the planetary carrier side, which has a large transmission torque, into the shaft on the sun gear side, so that the center differential 33 does not become large. Furthermore, if the center differential 33 is removed, a space is created for the high-low switching section, and the high-low switching section can be stored in this section. Therefore, it is possible to share the transfer case with a part-time 4WD vehicle, and the compatibility of this case is maintained.

In the present invention, the carrier 47 of the center differential 33 may be rotated in conjunction with the output shaft 25, and the rear wheel side may be connected to the internal gear 35. In this way, the proportion of driving force distributed to the rear wheels can be further increased than in the above embodiment.

Furthermore, by disposing a viscous coupling between the shafts 71 and 73, the center differential 33 can be provided with a differential limiting function.

[Effects of the Invention] The transfer of this invention can increase the ratio of driving force distribution to the rear wheel transmission shaft without increasing the size of the differential mechanism, and it is also possible to increase the ratio of driving force distribution to the rear wheel side transmission shaft without increasing the size of the differential mechanism. Can be shared.

[Brief explanation of drawings]

FIG. 1 is a sectional view of one embodiment, FIG. 2 is a schematic diagram showing the power system of a vehicle using this embodiment, and FIG. 3 is a skeleton mechanism diagram showing a conventional example. 25...Output shaft (transmission output side) 33
... Center differential (differential mechanism) 35 ... 4 internal gears ... Planetary carrier 51 ... Sun gear 71 ... Rear wheel side transmission shaft 73 ... Front wheel side transmission shaft

Claims (1)

[Claims] A space for a high-low switching section equipped with a subshaft is provided on the output side of the transmission of a four-wheel drive vehicle, and a front wheel side transmission shaft and a rear wheel side transmission shaft are arranged coaxially inside and outside on the output side of this space. A planetary spur gear differential mechanism is accommodated in the space for the high-low switching section and supported on the subshaft, and the transmission output side is interlocked with the input side of the differential mechanism, and both transmission shafts of the transfer are connected to the output side. Transfer configured in conjunction with.