JPH04136545A - Variable speed gear for automatic transmission - Google Patents

Abstract

PURPOSE:To shorten the length of a shaft to make the overall size compact by providing a second fixed member and a one way clutch arranged between a rotating member and the cylindrical part of the second fixed member. CONSTITUTION:The inner race 218A of a second one way clutch 218 is spline- coupled with the other end of a braking shaft 212 on one end of which a sun gear 214, with a sub-input gear 202 placed between both the ends. The outer race 218B of the second one way clutch 218 is pressed and fixed into a cylindrical part 318A provided adjacent to a confining wall 318 in its axial direction as a second fixed member. The outer peripheral part of the confining wall 318 is fixed to a cover body 310 as a first fixed member confining a circular space. Further, a dish plate 220 is fixed to the end of the inner race 218A, and plural clutch plates are provided between the dish plate 220 and the cover body 310 as multi-disc frictional engaging elements.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application 1] The present invention relates to a transmission device for an automatic transmission, and particularly to a transmission device for an automatic transmission equipped with a sub-transmission.

[Prior Art J] Conventionally, in order to increase the number of gears of an automatic transmission, it has been widely practiced to add a sub-shift mode to a main transmission.

For example, in the ``TOYOTA New Model Manual'' (published by Toyota Motor Corporation in August 1985), AI40
As a type, it has an input shaft on the same predetermined axis and an output shaft connected to an output gear at the terminal end, and is directly connected to a three-speed forward main transmission on an extension of the output shaft of this main transmission. An automatic transmission is shown that includes an auxiliary transmission capable of switching between gears and increasing gears. This one has an input gear that meshes with the output gear,
and an output gear connected to a final drive device on a counter shaft having an axis parallel to the axis of the main transmission. Furthermore, a brake device, a one-way clutch, and the like are provided in order to apply force to predetermined elements of the planetary gear set to perform a speed change operation.

By setting the auxiliary transmission as a direct gear, the main transmission can obtain the first, second, and third gears as usual, and the main transmission can obtain the third gear (the highest gear). In this state, the auxiliary transmission is set to an increasing speed to obtain the fourth speed of the overdrive gear ratio.

[Problem to be Solved by the Invention J] However, in such conventional devices, as a brake device that applies a reaction force to a predetermined element of a planetary gear set,
Since a multi-disc brake device with multi-disc frictional engagement elements is used and this and a one-way clutch are arranged side by side in the axial direction, the axial length becomes long, which causes an increase in the overall dimensions.

For this reason, there are restrictions on the layout on the vehicle.

An object of the present invention is to provide a transmission device for an automatic transmission that can eliminate such conventional problems and can shorten the shaft length (and make the overall size compact) even when a brake device and a one-way clutch are used. It is in.

[Means for Solving the Problems 1] In order to achieve the above object, the present invention includes a first fixing member defining an annular space, and a first fixing member disposed inside the annular space defined by the first fixing member. a multi-disc brake disposed between the first fixed member and the front rotating member and including a multi-disc frictional engagement element, a piston, and a return spring; a second fixing member having a cylinder part fixed to the piston and movably supporting the piston in the axial direction; and a cylindrical part to which the return spring is fixed; A one-way clutch disposed between the fixed member and the cylindrical portion.

[Function] According to the present invention, the multi-plate frictional engagement element is fastened by the piston supported movably in the axial direction by the cylinder provided on the second fixed member, and a braking force is exerted on the rotating member. As a result, a reaction force can be applied to one element of the planetary gear set, for example. In addition, a one-way clutch disposed between the rotating member and the cylindrical portion provided on the second fixed member prevents reverse rotation in a predetermined direction, and similarly prevents reverse rotation of one element of the planetary gear set. It is possible to apply a reaction force that

Since the one-way clutch is provided in the cylindrical portion, the multi-disc brake and the one-way clutch overlap in the axial direction, making it possible to shorten the axial length.

[Examples] Examples of the present invention will be described below with reference to the accompanying drawings.

FIG. 1 and FIG. 2 show an automatic transmission with four forward speeds and one reverse speed for a front wheel drive vehicle to which the present invention is applied.

The automatic transmission in this embodiment includes a main transmission 1 with three forward speeds.
00 and an auxiliary transmission 200 capable of switching between a high speed gear and a low speed gear are arranged so that their rotation axes are parallel to each other.

Here, since the power transmission mechanism in main transmission 100 is well known, only its outline will be explained.

That is, this power transmission mechanism, as shown in the skeleton diagram in FIG. They are on the same rotation axis, and on both shafts 12.0□ are a first planetary gear set Gl, a second planetary gear set Gl, a first clutch CI, a second clutch C2, a first brake Bl, and a second brake. B, and a first one-way clutch 0wC1 are arranged.

The first planetary gear set G is composed of a sun gear S, an internal gear R, and a pinion carrier PC1 that supports a pinion P1 that meshes with both gears S1 and R1 at the same time. G2 similarly includes a sun gear S2, an internal gear R1, and a binion carrier PC2 that supports a binion P that meshes with both gears S and R1 at the same time.

The above-mentioned components are connected as shown in the figure, and the first clutch CI, second clutch C3, first brake B, and second brake Bt (first one-way clutch OWC+) are connected as shown in FIG. This figure can be viewed by operating each element of the first and second planetary gear sets G1 and G2 (S+ , Ss, R1,
Rg, PC+ and PC,), thereby changing the rotational state of the main input shaft 11. The rotational speed of the main output shaft ON and the main output gear 0° which is integrally attached to the main output shaft 0 can be varied.

Next, the power transmission mechanism in the auxiliary transmission 200 is similarly configured with the main output gear OOM, as shown as a skeleton diagram in FIG.
The auxiliary input shaft 1g connected to the auxiliary input gear Ias to which the rotational force is transmitted, and the auxiliary output shaft 05 that transmits the driving force to the auxiliary output gear 008 meshing with the ring gear of the final drive device are on the same rotational axis. have. Furthermore, a third planetary gear set Gs is provided between the sub-input work and the sub-output shaft 08,
A third clutch Cm, a third brake B3 and a second one-way clutch 0WCI are arranged.

The third planetary gear set G is composed of a sun gear S, an internal gear R8, and a binion carrier PC1 that supports a binion P that meshes with both gears S and R8 at the same time. Binion carrier PC8 has sub output shaft 0. is always connected. Further, the sub-input shaft I is connected to the sub-output shaft 0 through the third clutch C8. and Binion carrier PC
3, the sun gear S3 can be connected to the third brake B,
Alternatively, it can be fixed to a stationary part by a second one-way clutch 0wC2.

Therefore, as is clear from FIG. 3, the main transmission 100
When is in the first to third speed state, in the sub-transmission 200, the third clutch C8 is released and the third brake B1 is engaged, so that the sun gear S is moved relative to the stationary part. A low gear state is established in which the sub output shaft 01 is driven via the pinion carrier P, and in this state, the gear ratios of the first to third gears are obtained as the main transmission 100 changes gears.

Furthermore, to obtain the fourth speed state from the third speed state, the third brake B is released and the third clutch C is engaged to upshift the auxiliary transmission 200 to the direct connection state, and at the same time, the main transmission 100 may be set to the third speed state.

At this time, the third brake B3 is released by the third clutch C3.
This is done before the engine is engaged to prevent gear shift shock from occurring. In this case, reverse rotation of the sun gear S is prevented by the second one-way clutch 0WCx.

Conversely, when switching from the fourth speed state to the third speed state, the third brake B,
The engagement of the second one-way clutch 0WC was delayed slightly.
It is configured to be fastened after x is activated.

Next, an example in which the power transmission mechanism shown in the above-mentioned skeleton diagram is actually constructed as an actual machine will be described based on FIG. 2.

In the figure, 300 is a main body case in which the main transmission 100 connected to the torque converter T/C and the sub-transmission 200 are housed, and a pump housing 302 is fixed to the main body case 300 with bolts. A pump gear 304 is housed inside the pump housing 302 and a pump cover 306 fastened thereto, and is driven by the engine via a pump impeller of a torque converter T/C. 306 is a pump housing 302.

In the main transmission 100, 102 is a torque converter T
104 is the above-mentioned main input shaft (A) connected to the output side of /C (hereinafter, in order to facilitate understanding, the reference numerals shown in the above-mentioned framework diagram are added in parentheses); Output gear (0,,1106 and main output shaft (
OM), and are rotatably supported on the same rotational axis.

108 and 110 are a first planetary gear set (G1) and a second planetary gear set (G1) arranged on the main input shaft 102, respectively.
G2), and both sun gears 10g5(S, )i5 and 110S(Ss) are integrally connected and connected to the main input shaft 102 via the first clutch 112(C+). . Further, the internal gear ID8R (R+) of the first planetary gear set 108 is connected to the second clutch 11
4 (C*), it is also connected to the main input shaft 102. Furthermore, the binion carrier L supporting the binion l08P (P, ) of the first planetary gear set 108
O8PC (pc + ) is connected to the main output shaft 104 by a spline connection. Also, both sun gear 108
A band-type first brake 113 (B,) is provided between the clutch casing 112A that connects the first clutch 112 and the first clutch 112, and a band-type first brake 113 (B,) that connects the sun gears 108s and 112 via the brake drum.
The 0S can be stationary.

On the other hand, the internal gear 110 of the second planetary gear set 110
R (Rz) is connected to the main output shaft 104 by spline connection and supports the binion ll0P (P2), and the main body case 300.
A second brake 116 (B,) and a first one-way clutch 118 (OWC+) are provided between the two.

By the way, the main output shaft 104 mentioned above is attached to the main body case 300.
It is rotatably supported by a bearing 308 fixed to the terminal end of the main body case 300 and a bearing 312 fixed to the main body cover 310 covered at the terminal end of the main body case 300. The above-mentioned main output key 7106 is arranged between them.

Next, in the sub-transmission 200, 202 is the main output key 71.
06, and is spline-coupled to a hollow sub-input shaft 204 (Is). The sub input gear 202 is located at the terminal end of the main body case 300,
A bearing 316 is fixed to a support wall 314 fixed to the main body case 300 with bolts so as to be disposed substantially on the same plane as the aforementioned bearing 308.
and a third
It is supported by a bearing 320 fixedly attached to a defining wall 318 that defines the brake cylinder.

206 is an auxiliary output shaft (03), and the auxiliary output gear 208 (Ls) spline-coupled to one end of this and the ring gear 402 meshing with this constitute the final reduction gear of the final drive device 400 and transmit driving force. I try to do that.

Therefore, in this embodiment, the sub output gear 20B is
In order to liquid-tightly separate the final drive device 400 and the transmission mechanism section of the sub-transmission 200, the main body case 300
First and second opposing walls 322 and 324 integrally formed with each other are supported on both sides by bearings 326 and 328, respectively, fixed thereto. Therefore, the above-mentioned pump housing 302 is fixedly installed in a part of the first opposing wall 322, with the minus side facing the housing space for the torque converter T/C, and the outer race of the bearing 326 on the other side. A recessed portion 322A is formed with a diameter in which the portion 326A is press-fitted.

Further, the second opposing wall 324 is disposed substantially parallel to the first opposing wall 322 and faces inward of the main body case 300, and has a diameter D2 in which the outer race 328A of the bearing 328 is press-fitted. A hole 324A is bored. A partition wall 330 that is continuous with the first opposing wall 322 is formed at the peripheral edge of the second opposing wall 324, and the accommodating space for the sub-output key 7208 is communicated with the accommodating space for the transmission mechanism except for communication through the fitting hole 324A. , liquid-tightly separated.

Therefore, the bearing 3 is press-fitted into the fitting hole 324A.
28 uses a so-called oil-sealed bearing that can prevent the movement of oil in the axial direction.

Furthermore, the recessed portion 322A of the diameter, the sub-output key 7208
The relationship between the outer diameter Do and the diameter of the fitting hole 324A is DI<D, <D! This facilitates the machining of the recessed portion 322A and the fitting hole 324A, and facilitates the assembly of parts related to the sub-output gear 208.

Furthermore, 2]0 is a bearing pressing member, and after the bearing 328 is press-fitted into the fitting hole 324A, it is fastened to the second opposing wall 324 with a bolt.

Further, a bearing hole 206A is formed at the other end of the auxiliary output shaft 206 to which the auxiliary output gear 208 is spline-coupled;
A distal end portion 212A of a brake shaft 212 rotatably supported is fitted into the hollow sub-input shaft 204 described above. A sun gear 214S (Ss), which is one of the components of the third planetary gear set 214 (G,), is integrally formed on the brake shaft 212. Furthermore, the internal gear 214R (Rs) of the third planetary gear set 214 is connected to the aforementioned sub-input shaft 204.
A binion carrier 214PC (Pct) supporting a binion 214P (P,) connected to the flange portion 204A formed therein and meshing with the internal gear 214R and the sun gear 214S is connected to the aforementioned sub output shaft 20.
6 with a spline connection. The internal gear 214R and the sub-output shaft 206 can be connected via a third clutch 216 (C,).

Further, the brake shaft 212, which has the sun gear 214S formed at one end thereof, has a second
An inner race 218A of a one-way clutch 218 (OWC, ) is splined. In addition, the outer race 218B of the second one-way clutch 218 is
It is press-fitted and fixed to a cylindrical portion 318A extending in the axial direction of the aforementioned defining wall 318 as a second fixing member.

The outer periphery of the defining wall 31g is a first wall defining an annular space.
It is fixed to the cover main body 310 as a fixed member.

A dish plate 220 is fixed to the end of the inner race 218A, and a plurality of clutch plates as multi-plate friction engagement elements are provided between the dish plate 220 and the above-mentioned main body cover 310. wall 318
A piston 222A is supported movably in the axial direction by a cylinder portion 318B formed in
The piston 222 has one end supported by a retainer fixed to the piston 222.
A third brake 222 (B*) is constituted by a return spring that biases A.

Note that the final drive device 400 has a main body case 3.
It is surrounded in a fluid-tight manner by a final drive case 404 that is fastened in half in the upper and lower halves in the figure along the axis of the axle indicated by the two-dot chain line in the figure.

In this embodiment having the above configuration, the gear shifting operation of each stage is performed by operating each component in the combination shown in FIG. 3, as already explained using the skeleton diagram of FIG. Needless to say, the operation of the sub-transmission 200 will be further explained, although a redundant explanation will be avoided.

The auxiliary transmission 200 includes a third clutch capable of connecting the auxiliary output shaft 206 and the internal gear 214R of the third planetary gear set 214 when the main transmission 100 is in the first to third speeds and in the reverse state. 216 is in the released state. and,
The third brake 222 has its piston 222A moved by hydraulic pressure and is in an operating state.
20. Inner race 21 of one-way clutch 218
8A, a brake shaft 212 supported by the hollow sub-input shaft 204, and a sun gear 214S formed on the brake shaft 212 are fixed to the main body cover 310. Therefore, in the sub-transmission 200, the sub-input gear 202
The rotational force input to the sub-input shaft 204 is transmitted to the sub-output shaft 206 in an underdrive state via the internal gear 214R and the binion carrier 214PC integrally connected to the sub-input shaft 204.

Furthermore, when in the fourth speed state, the above-mentioned third brake 2
22 is released, and the third clutch 216 is fastened. Then, the internal gear 214R, which is integrally connected to the sub-input shaft 204, and the sub-output shaft 206 are directly connected via the third clutch 216, and are in a directly connected state.

[Effects of the Invention] As is clear from the above description, according to the present invention, the multi-disc brake and one-way clutch that apply reaction force to the components of the planetary gear set are arranged in an overlapping manner in the axial direction. , the axial length can be shortened, and the overall dimensions can be made compact.

[Brief explanation of the drawing]

Fig. 1 is a skeleton diagram showing an embodiment of the power transmission mechanism according to the present invention, Fig. 2 is a sectional view showing an embodiment of the present invention, and Fig. 3 is a diagram showing the operating state of each element of the embodiment of the present invention. It is a diagram. In addition, in FIG. 3, ◯ indicates the time of operation. However, Knee:・ only operates when 1st gear is selected in manual operation.1, 4. , :N' means that it operates only before B operates, and 00 means that it operates with a delay when it is engaged and operates in advance when it is released. 100... Main transmission, 10102 (I... Input shaft, 104 (ON>... Output shaft, 106 (Oay)... Output gear, 200... Sub-transmission, 202 (I.S. )... Input gear, 204 (1,)... Input shaft, 206 (Os)... Output shaft, 208 (Oct)... Output gear, 212... Braking shaft, 214 (G, l ...Third planetary gear set, 216 (C,)
...Third clutch (g friction engagement device), 218 (OWC
, )...Second one-way clutch, 222 (Bri...
- Third brake, 300... Main body case, 310... Main body cover 400... Final drive device.

Claims (1)

[Claims] 1) a first fixing member defining an annular space; a rotating member disposed inside the annular space defined by the first fixing member; and the first fixing member and the rotating member. a multi-disc brake disposed between the members and the multi-disc brake including a multi-disc frictional engagement element, a piston, and a return spring; a second fixing member provided with a cylinder part that supports the return spring, and a cylindrical part to which the return spring is fixed; and a one-way disposed between the rotating member and the cylindrical part of the second fixing member. A transmission device for an automatic transmission, comprising: a clutch;