JPS62258815A - Part time four-wheel drive vehicle with sub-transmission - Google Patents

Abstract

PURPOSE:To make a transfer device lightweight and small-sized by constituting a planetary type sub-transmission mechanism arranged in parallel with a sleeve gear type sub-transmission mechanism and constituting a planetary type center differential mechanism arranged in parallel with a sleeve gear type 2-4 transfer mechanism. CONSTITUTION:A transfer device 4 is constituted of a planetary type sub- transmission mechanism 9 with its output shaft 14 connected to the output shaft 13 of a main transmission 3 and arranged in parallel with a sleeve gear type sub-transmission mechanism 11 arranged on the said shaft and a planetary type center differential mechanism 10 with its input member 24 connected to the output member 23 of the planetary type sub-transmission mechanism 9, with the first output member 33 directly connected to a rear wheel drive shaft 6, with the second output member 34 connected to a front wheel drive shaft 5 via a transfer gear 36, and arranged in parallel with a sleeve gear type 2-4 transfer mechanism 12 arranged on the said shaft. According to this constitution, this device can be made lightweight and small-sized.

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a part-time four-wheel drive vehicle with an auxiliary transmission;
More specifically, this paper relates to a transfer structure in a part-time four-wheel drive vehicle with an auxiliary transmission.

(Prior Art) In recent years, there has been a demand for improvements in the driving performance of automobiles, particularly in response to road surface conditions. In response to these demands, when driving on concrete roads, the power transmission to the front wheels is disconnected and only the rear wheels are driven, and when driving on soft roads, power is transmitted to the front and rear wheels to drive all wheels. A part-time four-wheel drive vehicle configured to
A proposal has already been made as described in Japanese Utility Model Publication No. 13155/1983. In this known example, a sleeve gear type 2-
A transfer device is constructed by combining a four-switching mechanism and an operating gear device, and is configured to selectively switch between two-wheel drive, four-wheel drive in a differential-free state, and four-wheel drive in a differential-locked state.

(Problems to be Solved by the Invention) When configuring a transfer structure of a part-time four-wheel drive vehicle with an auxiliary transmission by combining the transfer device disclosed in the above-mentioned prior art with an auxiliary transmission, the auxiliary transmission and the transfer Due to the structure of the device, it is difficult to make the device more compact and lightweight, and the development of a lightweight and compact transfer structure that can be used in part-time, one-wheel drive vehicles with an auxiliary transmission has been awaited. Ta.

The present invention has been made in view of the above points, and employs a planetary gear system for both the auxiliary transmission and the center differential in a part-time four-wheel drive vehicle with an auxiliary transmission, thereby making the device more compact and lightweight. 1] The purpose is to achieve the following.

(Means for solving the problems) In the present invention, as means for solving the above problems,
In a part-time, one-wheel drive vehicle with an auxiliary transmission configured to transmit the driving force transmitted through the main transmission to the front and rear wheels via a transfer, the input shaft is connected to the output shaft of the main transmission. a planetary auxiliary transmission gear mechanism in which a sleeve gear type stiffness switching mechanism arranged coaxially is arranged in parallel;
an input member is connected to an output member of the planetary auxiliary transmission gear mechanism, a first output member is directly connected to the rear wheel drive shaft, and a second output member is connected to the front wheel drive shaft via a transfer gear and is coaxially arranged. A planetary center differential mechanism is provided with a sleeve gear type 2-4 switching mechanism arranged in parallel.

As described in Embodiment Section 2.3, in the part-time four-wheel drive vehicle with an auxiliary transmission, gears with the same specifications are employed as the planetary gears in the planetary auxiliary transmission gear mechanism and the planetary 2-4 switching mechanism. However, it is more preferable that the planetary auxiliary transmission gear mechanism, the sleeve gear stiffness switching mechanism, the sleeve gear 2-4 switching mechanism, and the planetary center differential mechanism are sequentially arranged on the same axis from the upstream side of the transfer device. .

(Function) In the present invention, the following effects can be obtained by the above means.

In other words, the driving force manually applied to the planetary auxiliary transmission gear mechanism via the input shaft connected to the output shaft of the main transmission is changed to high or low speed by the switching operation by the sleeve gear type rigidity switching mechanism arranged on the same axis. The power is then transmitted to the human-powered member of the planetary center differential mechanism, where the power is distributed to two-wheel drive (rear wheel drive only) or four-wheel drive (main wheel drive) by switching operation by the sleeve gear type 2-4 switching mechanism. However, by making both the auxiliary transmission gear mechanism and the center differential mechanism planetary type, and the rigidity switching mechanism and 2-4 switching mechanism both using sleeve gear types, it is possible to arrange them coaxially, making the device more compact and Weight reduction can be achieved.

If the configuration is as described in Embodiment Section 2.3, it will be advantageous in terms of parts management, ease of assembly, and cost, and it will also be advantageous in terms of making the switching operation section more compact.

(Embodiments) Hereinafter, preferred embodiments of the present invention will be described with reference to the accompanying drawings.

The part-time four-wheel drive vehicle of this embodiment has a structure as shown in FIG.
, from the main transmission 3 to a transfer device 4 with an auxiliary transmission function, from which transmission is transmitted to the front wheels 7.7 via the front drive shaft 5 and to the rear wheels 8.8 via the rear drive shaft 6. The transfer device 4 is configured to perform two-speed switching between high and low speeds and 2-4 switching between two-wheel drive and four-wheel drive.

As shown in FIG. 1, the transfer device 4 is a planetary type in which an input shaft 14 is connected to an output shaft 13 of the main transmission 3, and a sleeve gear type rigidity switching mechanism 11 arranged on the same axis is arranged in parallel. Sub-transmission gear mechanism and input member 2
4 is an output member 23 of the planetary sub-transmission gear mechanism 9;
The first output member 33 is directly connected to the rear wheel drive shaft 6, the second output part 34 is connected to the front wheel drive shaft 5 via a transfer gear 36, and the sleeve gear type 2-4 is coaxially arranged. It includes a planetary center differential mechanism 10 in which a switching mechanism 12 is arranged in parallel. In addition, each of the above mechanisms is
It is disposed within the transfer casing 37.

The planetary sub-transmission gear mechanism 9 is connected to the input shaft 14
A sun gear 15 provided at the end of the sun gear 15, a ring gear 16 on the outer peripheral side of the sun gear 15, and a plurality of pinion gears 17, 17, which are located between the ring gear 16 and the sun gear 15 and perform rotation and revolution actions. It is configured. And the pinion gear l7, 17...
is rotatably supported by a carrier 18,
The carrier 18 is connected to the planetary auxiliary transmission gear mechanism 9.
The output part 11 is rotatably supported relative to the material 23. Also, the ring gear I6 is pivotally supported by the rotary mill (1:) relative to the output part (23rd). Note that the output member 23 is on the same axis as the human power shaft I4, and is rotatable relative to the input shaft 14.

On the outer layer of the pivot portion of the ring gear 16, a club hub 2 is provided.
0, a sleeve 19 is supported so as to be slidable in the axial direction. On both sides of the sleeve 19 in the axial direction, there are clutch teeth 21 provided on a locking member 38 that is locked on the transfer ring 37 and clutch teeth that are rotatably supported on the output member 23. 22, and the sleeve 19 slid axially with respect to these clutch teeth 21, 22 is selectively engaged. In other words, these sleeves I
A sleeve gear stiffness switching machine +'11911 is constituted by the gear 9 and the clutch teeth 21 and '22, and the sleeve gear stiffness switching machine lateral 11 is located on the output side of the planetary sub-transmission gear mechanism 9. -ing This sleeve gear stiffness switching mechanism 11 is operated by an appropriate operating member (not shown).

By switching the sleeve gear stiffness switching mechanism 11, the following speed change action is performed in the planetary sub-transmission gear mechanism 9.

(1) When the N range sleeve 19 is positioned at the solid line position in Fig. 1 and is not engaged with any of the clutch teeth 21, 22, and the ring gear 16 is in a free state, the input shaft 14 is connected to the sun gear! The power input to pinion gear 17,1?・
... is only rotated, but is not transmitted to the output member 23, resulting in a neutral state.

([1) Position the LOW range sleeve 19 at the position indicated by the symbol [9' (shown in FIG. 1! 1a), engage it with the clutch teeth 21 of the locking member 38, and move the ring gear 16 to the transfer song 3.
Fix it on the front side. Then, from the input shaft 14 to the sun gear 15
The power input to the pinion gear l7.17...
This results in rotation and revolution, and the deceleration is transmitted to the output member 23 via the carrier 18.

(III) The +4+ range sleeve 19 is shown with reference numeral 19 (1'1. position (shown with chain lines in Figure 1)) and is engaged with the clutch (122) on the output member 23 side, and the ring gear 16 is connected to the output member. 23. The power manually applied from the input shaft 14 to the sun gear 15 only causes the pinion gears 17, 17, . . . to revolve, and is directly transmitted to the output member 23 via the carrier 18.

On the other hand, the planetary type center differential mechanism 10 includes a sun gear that is rotatably supported in phases χ and r on the outer periphery of the manpower section attachment 2. 25, a ring gear 26 on the outer peripheral side of the sun gear 25, and a plurality of pinion gears 27, 27, . The pinion gears 27, 27, . Further, the ring gear 26 is rotatably supported by the first output member 33 (that is, the output member 91 directly connected to the rear wheel drive shaft 6) of the planetary center differential mechanism IO. Note that the first output member 33
is on the same axis as the input member 24 and is rotatable relative to the input member 24.

A gear 34 serving as a second output member of the planetary center differential mechanism IO is relatively rotatably supported on the outer layer of the pivot portion of the sun gear 25, and the gear 34 is connected to the chain 3
5 to a transfer gear 36 on the front wheel drive shaft 5 side.

A sleeve 29 is axially slidably supported on the outer periphery of the input side end of the planetary center differential mechanism 10 at the pivot portion of the sun gear 25 via a clutch hub 30. On both sides of the sleeve 29 in the axial direction, the clutch teeth 31 rotatably supported and the gears 3 and 1 (if changed, the second
Clutch teeth 32 are integrally formed with the output member (output member), and the sleeve 29 slid onto these clutch teeth 431, 32 is selectively engaged. In other words, the sleeve gear type 2-
4 switching mechanism 12 is constructed, and the sleeve gear type 2-4 switching mechanism 12 is connected to the planetary type center differential mechanism 10.
It is located on the input side of the This sleeve gear type 2-4 switching mechanism 12 is operated by an appropriate operating member (not shown).

By switching the sleeve gear type 2-1 switching device 12, the following power distribution effect is achieved in the planetary type center differential mechanism 10.

(1) Position the two-wheel drive sleeve 29 to the solid line position in FIG. to connect the sun gear 26 to the manpower member 24. Then, the power input from the output member 23 of the planetary sub-transmission gear mechanism 9 to the human power member 24 is input to the sun gear 25 and the carrier 28, and is transmitted to the first gear via the ring gear 26 due to the revolution of the pinion gears 27, 27... It is transmitted directly to the rear wheel drive shaft 6 via the output member 33, or via the gear 34 which is the second output member.
Since it is in a free state, there is no power transmission to the front wheel drive shaft 5, resulting in two-wheel drive with only the rear wheels 8.8 (see Fig. 2).

(■) Four-wheel drive (differential lock state) The sleeve 29 is positioned at the position indicated by the symbol 29' (shown by the chain line in FIG. 1), and both the clutch teeth 31 on the input member 24 side and the clutch teeth 32 on the gear 34 side are connected. The sun gear 25 is connected to the manpower member 24 and the gear 34 which is the second output member.

Then, the output member 23 of the planetary sub-transmission gear mechanism 9
The power inputted to the input member 24 from the sun gear 25,
The input is input to the carrier 28 and the gear 34, and is directly transmitted to the rear wheel drive shaft 6 via the ring gear 26, the first output member 33, and the rotation of the pinion gears 27, 27, etc., while the input is transmitted from the gear 34 to the chain 35. It is also transmitted to the front wheel drive shaft 5 via the transfer gear 36, resulting in four-wheel drive with the front wheels 7.7 and the rear wheels 8.8 (see FIG. 2). At this time, the power from the human power member 24 is simultaneously input to the sun gear 25 and the carrier 28, so the pinion gears 27, 27, etc. do not rotate and enter a differential lock state.

(1■) Four-wheel drive (differential free state) The sleeve 29 is positioned at the position indicated by the symbol 29'' (shown by the chain line in FIG. 1) and engaged with the clutch teeth 32 on the gear 34 side, which is the second output member, The sun gear 25 is connected to the gear 34. The power manually applied to the human power member 24 from the output part 1.t23 of the planetary sub-transmission gear mechanism 9 is transmitted to the carrier 28, and then transferred to the pinion gear 27.27.
The output from the ring gear 26 is transmitted to the rear wheel drive shaft 6 via the first output + 1
The output from the chain 35 and transfer gear 3
It is also transmitted to the front wheel drive shaft 5 via 6. Therefore, four-wheel drive is provided by the front wheels 7, 7 and the rear wheels 8, 8 (see FIG. 2). At this time, since the power from the input member 2.1 is input only to the carrier 28, the pinion gear 27.27
... rotates and revolves, and is in a differential-free state.

As described above, in the transfer device of this embodiment, the planetary type sub-transmission gear mechanism 9, the sleeve gear type rigidity switching mechanism 11, and the sleeve gear type 2-4 switching mechanism 12
The planetary center differential mechanism 10 is sequentially arranged on the same axis from the upstream side to the downstream side of the transfer device. With this configuration, it is extremely convenient to make the entire device compact and lightweight, and the system switching mechanism 11 and 2-4 switching mechanism 12 are arranged adjacent to each other, making it possible to make the operating section more compact. Contribute.

Furthermore, in this embodiment, the planetary gears (i.e., sun gears 15, 25, ring gear 16° 26, pinion gear 17, 28) in the planetary sub-transmission gear mechanisms 9 to 1 and the planetary 2-1 switching mechanism 10 are the same. The original gear is used. When the two mechanisms have gear configurations having the same specifications as described above, it is extremely convenient in terms of parts management, ease of assembly, and cost.

Note that the sub-transmission gear mechanism 9 and the center differential mechanism 10 each having a planetary gear configuration having the same specifications provide the following functions. Here, the number of teeth Ta of sun gear 15.25 is 58, and the number of teeth Tr of ring gear I 6.26 is 8.
6. Gear ratio of both gears λ= Ta/ 1' r= 58
/86=0.674.

In the planetary auxiliary transmission gear mechanism 9, in the case of H lunge, the gear ratio is -1,0 because it is directly connected, but in the case of LOW range, the gear ratio is (l+λ)/λ#25, 4 degrees.
]j On the other hand, in the planetary center differential mechanism IO, the torque distribution I r and I a between the front wheels and the rear wheels are as follows.

That is, Ir=λ/(1+λ); 0.403Ia=1/(
1+λ) #0.597, resulting in 1 r: I a44:6.

As mentioned above, the rear wheel torque is slightly larger than the front wheel torque, but a larger rear wheel torque distribution provides desirable results in terms of driving performance and the like.

It goes without saying that the present invention is not limited to the embodiments described above, and that the design can be modified as appropriate without departing from the gist of the invention.

(Effects of the Invention) As described above, according to the present invention, there is provided a part-time four-wheel vehicle with an auxiliary transmission configured to transmit the driving force transmitted through the main transmission to the front and rear wheels through the transfer device. In the drive vehicle, the auxiliary transmission gear mechanism is a planetary auxiliary transmission gear mechanism in which coaxially arranged sleeve gear type rigidity switching mechanisms are arranged in parallel, while the center differential mechanism is a coaxially arranged sleeve gear type 2-4. Since it is a planetary center differential mechanism in which the switching mechanisms are arranged in parallel, it is possible to arrange each mechanism on the same axis, which has the excellent effect of making the device more compact and lightweight.

In addition, sleeve gear type stiffness switching mechanism and sleeve gear type 2
-4 switching mechanism can be arranged adjacent to each other, which also has the effect of making the switching mechanism operating section more compact.

Furthermore, as described in Embodiment 2, if gears with the same specifications are adopted as the planetary gears in the planetary sub-transmission gear mechanism and the planetary 2-4 switching mechanism,
In terms of parts management, it greatly contributes to improving assembly ease and reducing costs.

Furthermore, as described in Embodiment 3, the planetary auxiliary transmission gear mechanism, the sleeve gear stiffness switching mechanism, the sleeve gear 2-1 switching mechanism, and the planetary center differential mechanism are arranged on the same axis from the upstream side of the transfer device. If arranged sequentially on the line, the device 1'l.

can be made even more compact.

[Brief explanation of drawings]

FIG. 1 is a vertical sectional view, not showing a transfer device, of a heart-time four-wheel drive vehicle with an auxiliary transmission according to an embodiment of the present invention, and FIG. FIG. 2 is a plan view schematically showing a power transmission section of a four-wheel drive vehicle. 3...Main transmission 4...Transfer device 5...Front wheel drive shaft 6...Rear wheel drive shaft 9...Planetary sub-transmission gear mechanism 10. ...
Planetary center differential mechanism 11... Sleeve gear type stiffness switching mechanism 12... Sleeve gear type 2-4 switching mechanism 13... Output shaft 14... Input shaft 23... Output member 24...Input member 33...First output member 3.1...Second output member 36...Transfer gear 37...Transfer casing Fig. 2

Claims (1)

[Claims] 1. In a part-time four-wheel drive vehicle with an auxiliary transmission configured to transmit the driving force transmitted through the main transmission to the front and rear wheels through a transfer device, the input shaft is connected to the a planetary auxiliary transmission gear mechanism connected to the output shaft of the main transmission and having a coaxial sleeve gear type auxiliary conversion switching mechanism arranged in parallel; and an input member connected to the output member of the planetary auxiliary transmission gear mechanism. , a planetary type in which the first output member is directly connected to the rear wheel drive shaft, the second output member is connected to the front wheel drive shaft via a transfer gear, and a sleeve gear type 2-4 switching mechanism arranged on the same axis is arranged in parallel. A part-time four-wheel drive vehicle with an auxiliary transmission characterized by being equipped with a center differential mechanism. 2. The part-time four-wheel drive vehicle with an auxiliary transmission according to claim 1, wherein gears having the same specifications are used as the planetary gear in the planetary auxiliary transmission gear mechanism and the planetary 2-4 switching mechanism. . 3. The planetary auxiliary transmission gear mechanism, the sleeve gear auxiliary conversion switching mechanism, the sleeve gear 2-4 switching mechanism, and the planetary center differential mechanism are sequentially arranged on the same axis from the upstream side of the transfer device. A part-time four-wheel drive vehicle with an auxiliary transmission according to claim 1 or 2.