JPS6338037A - Engagement and disengagement switchover means for transfer device - Google Patents

Abstract

PURPOSE:To miniaturize and lighten a device as a whole by providing an engagement/disengagement switchover means with a specific structure for carrying out the engagement and disengagement of each of two output members, etc. with and from each of the elements of one set of planetary gear device which is commonly provided for said two output members, and the engagement and disengagement between two elements. CONSTITUTION:An output gear 35 to which the rotation of an input shaft is transmitted via an idler gear 34, etc., is rotatably and removably supported by a front output shaft 20, and an input sleeve 4 is engaged by spline with a hub 3 which is joined by spline to the output gear 35. Also, the sun gear 5 of a planetary gear device 38 is rotatably and removably supported by he front output shaft 20 while an outer sleeve 13 is engaged by spline with a ring gear 10, and an inner sleeve 14 which is rotatably provided on this outer sleeve 13 is engaged by spline with a rear output shaft 19. And, forks 21, 22 which are fixed to form shafts 23, 24 are engaged with the sleeves 4, 13 respectively, and the shaft 23, 24 are operated with a common operating lever, to effect direct connecting and differentially moving performance.

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to an engagement/disengagement switching operation means for a transfer device.

(Prior Art) Conventional transfer devices have a speed change function that allows selection of either a low-speed, high-flexion power stage or a high-speed, low-drive power stage, and a differential function that eliminates the tight corner braking phenomenon when cornering. For devices with both, at least one
It requires one set of transmissions and one set of central differentials.

(Problems to be Solved by the Invention) A transfer device having the above-mentioned two sets of devices is larger and heavier than a transfer device having only a transmission device or only a central differential device. Furthermore, there is also the disadvantage that the number of gears increases and the switching mechanism becomes complicated.

SUMMARY OF THE INVENTION The present invention aims to eliminate the above-mentioned drawbacks, and particularly to provide an engagement/disengagement switching operation means for a transfer device that provides both direct coupling and differential functions using a series of gear configurations.

(Means for Solving the Problems) The present invention includes one manual member, two output members, two reaction force members, one set of planetary gears, and the relationship of each member to each element of the planetary gear. An engagement/disengagement switching operation means for a transfer device equipped with a speed change function, which includes an engagement/disengagement switching means for disengaging and engaging/disengaging between two of the respective elements, the fork shaft having a fork, and the fork shaft being connected to the fork shaft. It consists of an operating lever, and converts the movement of the operating lever into axial movement of the fork shaft to enable movement of the engagement/disengagement switching means in the output axial direction.

On the input side, the engagement of the input member with any element of the planetary gear train can be switched.

On the output side, the other two elements excluding the element that engages with the input member
a first switching state in which each of the two elements is engaged with one output member, and another state other than said element in which each of the two elements is engaged with an input member;
The present invention is characterized in that it includes a second switching state in which one element is engaged with two output members and the remaining one element is engaged with a reaction force member.

A planetary gear system consists of three gear sets: a sun gear, a planetary pinion, and a ring gear, and the planetary pinion is supported by a carrier. Either one of the three elements (sun gear, carrier, ring gear) is engaged with the input member, the other one is engaged with one output member, and the other one is fixed or engaged with one of the remaining two elements or otherwise. A predetermined power train can be achieved by engaging the output member of.

Now, if one element is fixed, input can be made to either of the other two elements, and the remaining element becomes the output element. In this case, a direct (all-wheel) drive power train is achieved by engaging this output element with two output members. A differential power train may also be achieved by engaging one of these elements (eg, the carrier) with the input member and separately engaging the other two elements with each of the two output members.

In FIG. 4, S represents a sun gear, C represents a carrier, and R represents a ring gear.

In the case of direct four-wheel drive, when S is input, the following two selections are possible.

(A) R is a reaction force engagement, and C is engaged with output 1 and output 2 (Figure 4-A).

(B) C is a reaction force engagement, and R is engaged with output 1 and output 2 (Figure 4-B).

Moreover, when C is input, the following two selections are possible.

(C) S is a reaction force engagement, and R is engaged with output 1 and output 2 (Figure 4-0).

(D) R is a reaction force engagement, and S is engaged with output 1 and output 2 (Figure 4-D).

When R is input, two choices are similarly possible (explanation path).

In the case of differential four-wheel drive, it is obtained by separately engaging two elements S, C, and R to two outputs.

(E) When C is input, R is engaged with output 1 and S is engaged with output 2 (Figure 4-E).

(F) When S is input, R is engaged with output 1 and C is engaged with output 2 (Figure 4-F).

(G) When R is input, C is engaged with output 1 and S is engaged with output 2 (Figure 4-G).

As described above, various engagement combinations are possible, but when used in a vehicle, it is preferable from the viewpoint of deceleration and efficiency.

(Example) The present invention will be described below with reference to drawings showing examples.

FIG. 1 shows a plan view of the engagement/disengagement switching operation means of this embodiment,
FIG. 2 is a longitudinal sectional view thereof.

In FIG. 1, 26 is an outer lever (operation lever), 25
indicates the inner lever, respectively. Both levers are concentrically coupled together and rotate about an axis 27.

The fork shaft 23.24 is supported in the case 17 in a fork shaft bearing 11.15. A groove 28 perpendicular to the axial direction is provided at one end of the fork shaft 23, 24.
．． 29 are provided, and both circular ends 30 of the inner lever 25,
31 is the groove portion 21! , 29, respectively. A fork 21.22 is fixed to each of the fork shafts 23.24. In FIG. 5, annular grooves 1 and 2 are provided on the outer peripheries of the input sleeve 4 and the outer sleeve 13, respectively. Fork 21 is in groove 1
The fork 22 is fitted into the groove 2 and fixed to the fork shaft 23, and the fork 22 is fitted into the groove 2 and fixed to the fork shaft 24.

FIG. 6 is an overall view of the transfer device of this embodiment. This embodiment consists of a combination in which (A) is used as a direct power train and (E) is used as a differential power train, as shown in FIG. This is represented by a skeleton diagram. 31 is a human power shaft connected to an output shaft (not shown) of the transmission, and gears 32, 34, 35
This forms an input side gear train. 32 is an input gear, which is integrally connected to the input shaft 31. 34 is an idler gear, and the idler gear 34 meshes with the input gear 32.
a is integrally formed and rotatably supported by the idler shaft 33 via a bearing. 35 is the output gear of the input side gear train, and the idler gear 34
a and is rotatably supported by the front output shaft 20.

FIG. 5 is a detailed diagram of the transfer device of this embodiment.

In this embodiment, a sleeve (a type of dog clutch) is used as the engagement/disengagement switching means, but the present invention is not limited to this; for example, it is also possible to use other types of clutches or rotary engagement/disengagement means. . The hub 3 is connected to an output gear 35 by a spline 2a. The input sleeve 4 is always engaged with the hub 3 via the spline 3a so as to be freely slidable in the direction of the axis PP.

38 is a planetary gear device. Sun gear 5 is rotatably supported by front output shaft 20. A planetary gear 8 that meshes with the sun gear 5 is rotatably attached to a planetary gear shaft 7, and the planetary gear shaft 7 is fixedly supported by a planetary carrier 6. The planetary gear 8 meshes with the ring gear 10.

The input sleeve 4 is selectively engageable with the carrier 6 or the sun gear 5. The sun gear 5 and the input sleeve 4 are engaged and disengaged by sliding the sleeve 4 in the axial direction, and the two are removably engaged via a spline 4a. Similarly, the input side member 6' of the planetary carrier 6 is also freely engaged with the sleeve 4 via the spline 6a.

The engagement and disengagement on the output side is performed via the outer sleeve 13 and the inner sleeve 14, which is fixed in the axial direction but is arranged to be free to rotate relative to the outer sleeve 13.

The ring gear 10 is engaged by a spline 13a with an outer sleeve 13 that can freely slide in the direction of the axis PP. The outer sleeve 13 is integrally connected to the case engagement sleeve I6 by a splint 13b. The sleeve 16 can be selectively engaged with and disengaged from the case 17 or the rear output shaft 19 via a spline 16a. The position of the inner sleeve 14 in the axis P-P direction is determined by the outer sleeve 13.
3 is rotatable. Inner sleeve 14 has spline 1
4a, it can be freely engaged with and disengaged from the hub 12, and the spline 18
It can be freely engaged and disengaged with the hub 18 by a, the rear output shaft 19 can be freely engaged and disengaged by the spline 19a, and the front output shaft 20 can be freely slidably engaged by the spline 2Qa.

A hub 12 is connected to the output side member 6'' of the planetary carrier 6 through a spline 12a, and a hub 18 is connected to the sun gear 5 through a spline 18b.

In FIG. 3, when the driving force input from the transmission section (not shown) is input to the carrier 6 via the sleeve 4, a pinion gear 8 rotatably supported on the carrier 6 via a planetary gear shaft 7 Through ring gear 10
and distributed to Sangia 5. The driving force distributed to the ring gear 10 is transmitted to the rear output shaft 19 engaged by a sleeve (integrated structure of 13 and 16). The driving force distributed to the sun gear 5 is transmitted to the front output shaft 20 via the sleeve 14 engaged with the sun gear. (According to the WL theory, the transmission of the distributed driving force to each output shaft is performed by the engagement/disengagement switching means (sleeve) that can be selectively engaged with the ring gear 10, sun gear 5, or carrier 9.) In this way, The driving force input from the transmission section to the carrier 6 is distributed to the rear output shaft and the front output shaft. At this time, the planetary gear unit also functions as a central differential.

Next, when the engagement is switched to the position shown by the dashed line in FIG. At this time, the ring gear 10 has sleeves (13, 16)
It is engaged with the transfer case 17 via , and cannot rotate. The driving force transmitted to the pinion gear 8 is transmitted to the carrier 6 (its output side member 6'), and the torque is amplified (the rotational speed is reduced). The driving force transmitted to the carrier 6 is transmitted to both the front output shaft 20 and the rear output shaft 19, which are integrally engaged by the sleeve 14. At this time, the planetary gear device also functions as a speed reduction device, and the front output shaft and rear output shaft are integrally connected, and no differential movement occurs between the two shafts.

(Example effect) The state shown in FIG. 5 shows a low speed, high driving force running state.

Input from the transmission (not shown) is transmitted to the output gear 35 via the idler gear 34, and the spline 2a
is transmitted to the hub 3 connected to the output gear 35. The input transmitted to the hub 3 is transmitted from the sun gear 5 to the planetary gear 8 via the sleeve 4. Since the case engagement sleeve 16 is engaged with the case 17, it cannot rotate, and the outer sleeve 13. Ring gear 10 is also non-rotatable. Therefore, the input transmitted to the planetary gear 8 is amplified and transmitted as rotation of the planetary carrier 6 around the axis PP (the rotational speed is reduced). The amplification input is transmitted via hub 12 to inner sleeve 14 . Furthermore, inner sleeve 1
4 to the rear output shaft 19 and front output shaft 20. At this time, the input is amplified within the planetary gear device 38, the rotation speed of the output gear 35 is reduced, and the vehicle runs at a low speed.

Next, a case where the planetary gear device functions as a central differential device will be described.

In FIG. 1, when the outer lever 2B is rotated in the X direction, the inner lever 25 is rotated counterclockwise in the same direction as the outer lever. At this time, the fork shaft 24 moves to the left, and the fork shaft 23 moves to the right. The fork 21 fixed to the fork shaft moves to the right and the fifth
In the figure, the input sleeve 4 is slid into position C. Similarly, the fork 22 moves to the left and the outer sleeve 13
is slid into position.

The input from the transmission is the idler gear 34.
It is transmitted to the hub 3 via the output gear 35. The input transmitted to the hub 3 is in turn transmitted to the planet carrier 6 via the input sleeve 4. Human power is further passed from the carrier to the planetary gear shaft 7 if! Ring gear l from LJ gear 8
It is distributed to O and Sun Gear 5. The input distributed to the sun gear 5 is transmitted to the front output shaft 2o via the hub I8 and the inner sleeve 14. The input distributed to the ring gear 10 is transmitted to the case engagement sleeve 16 via the outer sleeve 13.

This is because the sleeve 16 is engaged with the rear output shaft 19.

The distributed input is transmitted to the rear output shaft 19. At this time, the planetary gear set 38 also functions as a central differential. Further, simultaneously achieving a speed stage higher than the low speed stage,
In this sense, it also has a speed change function.

(Effects of the Invention) The engagement/disengagement switching operation means of the present invention performs switching between the two functions of a transfer device that performs both the direct connection and differential functions by a series of gear configurations. Therefore.

The overall size and weight of the transfer device will be reduced.

In addition, the number of gears is reduced and the complexity of the mechanism is also suppressed. Furthermore,
Since there are fewer gears, gear noise is suppressed.

The engagement/disengagement switching operation means 6 of the present invention is easy to operate and can reliably switch engagement with a simple configuration.

[Brief explanation of drawings]

FIG. 1 is a plan view of the engagement/disengagement switching operation means according to the embodiment of the present invention, FIG. 2 is a longitudinal sectional view thereof, and FIG. 3 is a schematic diagram showing power transmission.
FIG. 4 is a block diagram illustrating direct four-wheel drive and differential four-wheel drive, FIG. 5 is a detailed view of a transfer device according to an embodiment of the present invention, and FIG. 6 is an overall view of the same transfer device. 4...Input sleeve 5...Sun gear 6...
Carrier 7... Planet gear shaft 8... Planet gear 10... Ring gear 13... Outer sleeve 14... Inner sleeve 1G... Case engaging sleeve 19... Rear output shaft 20...・Front output shaft 21, 22...Fork 23, 24...Fork shaft 35...Output gear 38...Planetary gear device applicant Aisin Seiki Co., Ltd. agent Patent attorney Asami Kato (and 1 others) (name) Cleaning of drawings '8 (Figure 4 (A) (C) (B) (D) Procedural amendment form with changes in content) October 15, 1986

Claims (1)

[Claims] An input member, two output members, a reaction member, a set of planetary gears, engagement and disengagement of each of the members with respect to each element of the planetary gear, and two components of each of the elements. The engagement/disengagement switching operation means for a transfer device equipped with a speed change function consists of an engagement/disengagement switching means for engaging/disengaging between converting the motion into axial movement of the fork shaft to enable movement of the engagement/disengagement switching means in the output axial direction, and on the input side, enable switching of engagement of the input member with any element of the planetary gear device; On the output side, the other two elements excluding the element that engages with the input member
a first switching state in which each of the two elements is engaged with one output member, and another state other than said element in which each of the two elements is engaged with an input member;
A second switching state in which one element is engaged with two output members and the remaining one element is engaged with a reaction member.