JPS6347538A - Transfer device - Google Patents

Abstract

PURPOSE:To simplify a switchover mechanism by carrying out the switchover of the engagement of an input member with any element of a planetary gear through the formation of a sleeve and the relative position of each engaging element. CONSTITUTION:When engagement is switched over to positions shown by dashed lines, a driving force from a transmission part is inputted into a sun gear 5 via a sleeve 4 and transmitted to a pinion gear 8. In this case, a ring gear 10 is engaged with a transfer case 17 via a sleeve and unable to rotate. The driving force transmitted to the pinion gear 8 is transmitted to a carrier 6 and its torque is amplified. The driving force transmitted to the carrier 6 is transmitted to both of integrally engaged front output shaft 20 and rear output shaft 19 through a sleeve 14. Accordingly, since the switchover of engagement is carried out by sleeves, the switchover device can be simplified.

Description

DETAILED DESCRIPTION OF THE INVENTION (Industrial Application Field) The present invention relates to a transfer device, and more particularly to a transfer device that achieves direct coupling to differential power train by switching engagement.

(Prior Art) Conventionally, this type of transfer device has a transmission function that allows selection of either a low-speed high-side power stage or a high-speed low-side power stage, and a differential function that eliminates the tight corner braking phenomenon when cornering. In the case of a system having both, at least one set of transmissions and one set of central differentials are required.

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

The present invention aims to eliminate the above-mentioned drawbacks, and particularly aims to provide a transfer device that performs both direct coupling and differential functions using a series of gear IR configurations.

(Means for Solving the Problems) The transfer device of the present invention includes an input member, two output members, nine reaction force members, a set of planetary gear devices, and input side and output side engagement/disengagement switching means. A transfer device consisting of:

The input end engagement/disengagement switching means enables switching of engagement of the input member with any element of the planetary gear device.

The output-side engagement/disengagement switching means is configured to engage one or both of the other two elements, excluding the element that engages with the input member, with one output member. It includes a second switching state and a third switching state in which one element other than the element that engages the input member is engaged with the two output members, and the remaining one element is engaged with the reaction force member. It is characterized by this. Furthermore, the engagement/disengagement switching means includes a neutral state.

The engagement/disengagement switching means is 1, for example, a sleeve (of a dog clutch).
FIf) etc. can be considered.

The engagement can be switched by the configuration of the sleeve and the relative positional relationship of each engagement element. For example, the sleeve can be slid in the axial direction, and the sleeve can be engaged with each intended engagement element in accordance with a predetermined sliding movement of the sleeve.

The sleeve arrangement at the input end permanently engages the input shaft and allows selective engagement with either the sun gear or the carrier, for example.

The output side sleeve has a plurality of sleeves as its constituent elements, and can be configured as one body or separate pieces. When the ring gear is fixed and output engaged, the structure of the sleeve 1 is such that it always engages the ring gear and also engages the reaction member (for example, the case) and the output member (for example, the output shaft). Enable selectively. The sleeve 2 can be engaged with any one of the fM vehicle elements and can be engaged with one or two output members.

Now - as an example, when the input sleeve engages the carrier, the output sleeve configuration is such that sleeve 1, which is always engaged with the ring gear, is engaged with one output member while the other sleeve 2 is engaged with the carrier. The sun gear is engaged with another output member (first switching state).

Alternatively, by changing the configuration of the sleeve, it is possible to engage either the ring gear or the sun gear with the one output member (second switching state).

When the input end sleeve engages the sun gear.

The sleeve 1 engages one reaction force member, and the sleeve 2 directly connects and engages the carrier and two output members (third switching state).

The free length gear device 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 manpower member and the other two elements separately engaging the two output members, respectively.

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, if S is human power, the following two choices 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 human-powered, 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.

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

(P) 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 (Figures 4-6).

For example, when the two output engagements in the directly coupled four-wheel drive state of (A) are made into a single engagement of either output 1 or output 2, two-wheel drive is achieved. By switching the engagement, you can drive two wheels, direct four-wheel drive, or (E) to (G).
With differential four-wheel drive.

It is also possible to obtain two-wheel or differential four-wheel drive.

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

(Example) The present invention will be described below with reference to drawings showing examples. FIG. 2 is an overall view of the transfer device of Kimoto's embodiment. In this embodiment, the above (Δ) is a directly coupled power train, and (E
) as a differential power train, and is represented by the skeleton diagram shown in FIG. 31 is a human power shaft connected to an output shaft (not shown) of the transmission, and gears 32, 34 .
35 forms an input side gear train. 32 is an input gear, which is integrally connected to the input shaft 31. 34 is idler gear.

An idler gear 34a that meshes with the input gear 32 is integrally formed and rotatably supported by the idler shaft 33 via a bearing. Reference numeral 35 denotes an output gear of the input side gear train, which meshes with the idler gear 34a and is rotatably supported by the front output shaft 20.

FIG. 1 is a detailed diagram of the transfer device of this embodiment.

Note that 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 human-powered 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 P--P.

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 manual sleeve 4 are engaged and disengaged by sliding the sleeve 4 in the axial direction, and the two are removably engaged through 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 IO is engaged with an outer sleeve 13 that is freely slidable in the direction of the axis PP through a spline 13a. The outer sleeve 13 is integrally connected to the case engagement sleeve 1B by a spline tab. The sleeve 16 can be selectively engaged with and disengaged from the case 17 or the rear output shaft 19 by a spline lea. The position of the inner sleeve 14 in the axis P-P direction is determined by the outer sleeve 13.
It is rotatable. Inner sleeve 14 has splines 14
a, it can be freely engaged with and disengaged from the hub 12, and the spline 18a
It can be freely engaged with and disengaged from the hub 18, freely engaged with and disengaged from the rear output shaft 19 through the spline 19a, and freely slidably engaged with the front output shaft 20 through the spline 20a.

A hub 12 is connected to the output side member 6' of the planetary carrier 6 through a spline 12a, and a hub I8 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 Jffi gear shaft 7 It is distributed to ring gear lO and sun gear 5 via. The driving force distributed to the ring gear 10 is transmitted to the rear output shaft 19 that is engaged with the sleeve (13, 1 [i] integrated). sun gear 5
The driving force distributed to the sleeve 1 engaged with the sun gear
4 to the front output shaft 20. (To summarize, that is, 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 transmission The driving force input from the carrier 6 to the carrier 6 is distributed to the rear output shaft and the front output shaft. The planetary gear system then also functions as a central differential.

Next, when the engagement is switched to the position shown by the dashed line in FIG. 3, the driving force from the transmission section is input to the sun gear 5 via the sleeve 4 and transmitted to the pinion gear 8. At this time, the ring gear IO is connected to the sleeve (13, 18
) and is engaged with the transfer case 17 through the connector 17, making it impossible to perform d-transfer. 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 unit also functions as a reduction gear.
The front output shaft and rear output shaft are integrally connected, and no differential occurs between the two shafts.

(Example effect) The state shown in FIG. 1 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 human power 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 1B 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 rotational 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.

When the engagement switching operation is performed by the direct coupling/differential switching operation means (schematically shown as 21), each sleeve moves to the position shown by the two-dot chain line in the figure.

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. The human power is further distributed from the carrier to the ring gear IO and the sun gear 5 via the planetary gear shaft 7 and the planetary gear 8. The input distributed to the sun gear 5 passes through the hub 18 and the inner sleeve 14 to the front output shaft 2.
0. 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) Since the switching of engagement is performed by the sleeves configured on the input side and the output side, it can be performed on both sides at the same time, and the switching device can be miniaturized.

The transfer device of the present invention, which performs both the full-width direct connection function and the front and rear wheel differential function through a series of gear configurations, has a smaller and lighter overall device, and the direct connection/differential switching operation means is also simplified. is possible.

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.

[Brief explanation of the drawing]

FIG. 1 shows detailed wheel drive of a transfer device according to an embodiment of the present invention.
Block diagrams illustrating differential four-wheel drive are shown respectively. 4...Input sleeve 5...Sun gear 6...
Carrier T...Planetary gear shaft 8...Planetary gear 10...Ring gear 13...Outer sleeve 14...Inner sleeve 16...Case engagement sleeve 19...Rear output shaft 20...・Front output shaft 35...Output gear 38...Planetary gear device Applicant Aisin Seiki Co., Ltd. Agent Patent attorney Tomomichi Kato (and 1 other person) Tsukiji Nehosei νf (method) 1985 November // Ll

Claims (2)

[Claims] (1) Input member, two output members, reaction force member, 1
A transfer device comprising a set of planetary gears and input side and output side engagement/disengagement switching means, wherein the input side engagement/disengagement switching means is capable of switching engagement of an input member with any element of the planetary gear device. In addition, the output side engagement/disengagement switching means has a first and second switching state in which both or one of two elements other than the element that engages with the input member is engaged with one output member; A transfer device comprising a third switching state in which one element other than the element that engages the member is engaged with two output members, and the remaining one element is engaged with a reaction member. . (2) The device according to claim 1, wherein the engagement/disengagement switching means includes a neutral state.