JPH0249426B2 - - Google Patents

Description

[Detailed description of the invention]

[Industrial Application Field] The present invention relates to a multi-stage automatic transmission for an automobile. [Conventional technology] In recent years, four-speed automatic transmissions have been commercialized to reduce fuel consumption, and front-engine, front-drive (hereinafter referred to as FF)
There is also a remarkable trend toward the automobileization of automobiles. In particular, it has been difficult to install a conventional four-speed forward automatic transmission for front-engine, rear-drive vehicles in small vehicles with horizontally mounted front-wheel drive engines due to overall width constraints. FIGS. 1 and 3 show a schematic diagram and an overall sectional view of a conventional automatic transmission transmission related to the present invention. The automatic transmission 100 is comprised of a hydraulic torque converter 200, a transmission 300, and a hydraulic control device (not shown in FIG. 3). The transmission 300 includes a first planetary gear set 30, a second planetary gear set 40, two multi-disc clutches C1 and C2 operated by hydraulic servos, and one band brake B.
1. A transmission with three forward speeds and one reverse speed, which is equipped with two multi-disc brakes B2 and B3, one one-way clutch F1, and one one-way brake F2, a first planetary gear set 30, and a hydraulic servo. It is comprised of an overdrive device including one operated multi-disc clutch C0, one multi-disc brake B0, and one one-way clutch F0, and further includes a relay transmission shaft 70 and a differential gear 80. The automatic transmission housing 110 includes a torque converter 200, a transmission, and a relay transmission shaft 70.
, a main housing 120 integrally formed with each chamber for accommodating the differential device 80, a sub-housing 130 for accommodating the overdrive device 50 and covering the rear side of the automatic transmission, and a rear housing for the differential device chamber. It consists of a rear cover 140 that covers the sides. Torque converter 200 is housed in a torque converter chamber 121 that is open at the front (engine side). An oil pump 15 is installed inside between the cylindrical transmission chamber 122 and the torque converter chamber 121 which are connected to the rear of the torque converter chamber 121.
An oil pump front cover 151 that is shaped like a return plate and has a cylindrical part 152 inside is firmly fastened to the main housing 120. An oil pump cover 154 having a front center support 153 projecting rearward is fastened to the front center support 153.
and oil pump cover 154 are partition walls 155 between both chambers.
is formed. Further, at the rear of the transmission chamber 122, a center support 156 that protrudes forward is provided.
An intermediate support wall 157 is provided. The transmission device 12 is located between the partition wall 155 and the intermediate support wall 157.
2, an intermediate support wall 157 and a subhousing 13
The space between the rear walls 141 of 0 is the overdrive device chamber 1.
23 and the rear side wall 14 of the subhousing.
1 has a cylindrical rear center support 142 that is coaxial with the front center support 153 and projects forward. A fixed shaft 203 of a one-way clutch 202 that supports a stator 201 of a torque converter 200 is fitted inside the front center support 153, and an input shaft of the transmission, which is an output shaft of the torque converter, is fitted inside the fixed shaft 203. 1 is rotatably supported. The input shaft 1 has a large diameter rear end 2 that projects rearward from the front center support 153, and a rearward hole 3 is formed in the center of the rear end 2. An intermediate shaft 4 arranged in series with the input shaft 1 is rotatably attached to the rear of the input shaft 1, and the tip of the intermediate shaft 4 has a hole 3.
The rear end is supported inside the rear center support 142 via a bearing, and the middle part is in sliding contact with the rear center support 142.
Carrier P1 of third planetary gear set 60
A cylindrical carrier shaft 5 connected to the shaft is externally fitted with a spline, and the carrier shaft 5 is supported by a center support 156 of the intermediate support wall via a ball bearing. Further, a sun gear shaft 6 is rotatably fitted on the outer side of the distal end of the intermediate shaft 4. Inside the transmission chamber 122, in the front, first,
A first hydraulic servo drum 7 that opens rearward is rotatably fitted onto the front center support 153, and an annular piston 8 is fitted between its inner and outer circumferential walls to form a hydraulic servo 9 of the clutch C2, while also returning to the inner circumferential wall side. A clutch C2 is fitted inside the outer peripheral wall of the spring 10. The first
On the rear side of the hydraulic servo drum 7, a second hydraulic servo drum 12 which is open to the rear and has an annular projection 11 at the front is fitted with an annular piston 13 fitted between the rear end portion 2 of the input shaft 1 to engage the clutch C1. A hydraulic servo 14 is formed, and a return spring 15 is attached to the inner circumferential side, a clutch C1 is attached to the inner side of the outer circumferential wall, and a clutch C2 is attached to the outer circumference of the annular projection 11. Two hydraulic servo drums 7 and 14 are connected. On the rear side of the second hydraulic servo drum 14,
A first planetary gear set 30 is provided, a ring gear R3 of which is connected to a second hydraulic servo drum via a clutch C1, a carrier P3 splined to the tip of the intermediate shaft 4, and a sun gear S3 connected to the sun gear shaft 6. They are united. Also,
A connecting drum 16 shaped to cover the first and second hydraulic servo drums 7, 14 and the first planetary gear set 30 in a minimum space is fixed to the outside of the first hydraulic servo drum 7 at its leading end, and its rear end is fixed to the outside of the first hydraulic servo drum 7. , is connected to the sun gear shaft 6 on the rear side of the first planetary gear set 30, and a band brake B1 is provided on the outer peripheral side. An annular third hydraulic servo drum 17 that opens rearward is fixed to the surplus space 16A outside the connecting drum outside the first planetary gear set 30.
The piston 18 is fitted to form a hydraulic servo 19 of the brake B2. A spline groove 20 formed inside the main housing 120 on the rear side of the hydraulic servo 19 has a brake B2, an outer race 21 of a one-way brake F2, and a brake B
3, and the outer peripheral side of the center support 156 of the intermediate support wall 157 on the rear side and the housing 12
The piston 22 is fitted into the annular hole between the two ends to form a hydraulic servo 23 of the brake B3, and the return spring 24 of the hydraulic servo 23 is supported by a flange plate attached to the tip of the center support 156. A one-way clutch F1 is provided inside the brake B2, and the outer race 25 is connected to the brake B2, and a second planetary gear set 40 is attached to the rear side of the one-way clutch F1. ing. The second planetary gear set 40 is
Sun gear S2 is integrally formed with sun gear shaft 6,
The carrier P2 is connected to the inner race of the outer one-way brake F2 and also to the brake B3, and the ring gear R2 is connected to the intermediate shaft 4. In the overdrive device chamber 123, an output gear 61 of the overdrive device is rotatably fitted outside the carrier shaft 5 on the rear side of the intermediate support wall 157 via a tapered roller bearing. Further, on the rear side, a sun gear shaft 62 is rotatably fitted to the rear of the intermediate shaft 4, a third planetary gear set 60 is placed on the inside, a brake B0 and its hydraulic servo 63 and a turn spring 64 are placed on the outside, and a single gear is placed on the rear side. Behind the direction clutch F0, a fourth hydraulic servo drum 65 that opens forward is rotatably fitted onto the rear center support. An annular piston 66 is fitted between the inner and outer peripheral walls of the fourth hydraulic servo drum 65 to form a hydraulic servo 67 for the clutch C0, and a return spring 68 is installed on the inner peripheral side, and a clutch C0 is installed inside the outer peripheral wall.
is fitted, and the fourth hydraulic servo drum 65 is integrally connected to the sun gear S1, and connected to the carrier P1 via the clutch C0, and also to the brake B.
0 to the housing 130.
Carrier P1 and sun gear S1 are one-way clutch F.
0, and the ring gear R1 is coupled to the output gear 61 of the overdrive device. A cylindrical relay transmission shaft chamber 124 is provided on the side of the transmission chamber 122 and the overdrive device chamber 123, and a relay transmission shaft 70 arranged parallel to the intermediate shaft 4 is connected to a pair of tapered roller bearings 71, 7.
2, the relay transmission shaft 7
An input gear 73 that meshes with the output gear 61 of the overdrive device is provided at the rear of the 0, and an output gear 74 is provided at the tip. A differential gear chamber 125 is provided on the side of the torque converter chamber 121, and a tapered roller bearing 8 is provided in the differential gear chamber 125.
1 and 82, an input large gear 83 provided at the rear end of the differential device 80 is connected to the output gear 7.
It meshes with 4. The transmission 300 engages each clutch and brake using hydraulic pressure selectively output from a hydraulic control device (not shown) to the hydraulic servo of each friction engagement device according to vehicle running conditions such as vehicle speed and throttle opening. Alternatively, the release is performed, and the gear is shifted to four forward speeds or one reverse speed. Table 1 shows an example of the RANGE achieved by the operation of each clutch, brake, one-way clutch, and one-way brake.

[Problem to be solved by the invention]

In the conventional automatic transmission described above, as is clear from the operation table shown in Table 1, in the first forward gear, clutch C1 is engaged and one-way clutches F1 and F2 are in a locked state. . The rotation applied to the input shaft 1 is reduced by both the first planetary gear set 30 and the second planetary gear set 40. The one-way clutch F0 of the overdrive device is in a locked state, and the third
The planetary gear set 60 rotates together.
This state is maintained up to the third gear. In the second gear, the clutch C1 and the brake B2 are engaged, and the one-way clutch F1 is in a locked state. As a result, the speed is reduced only by the first planetary gear set 30. In the third gear, clutches C1 and C2 and brake B2 are engaged, and one-way clutches F1 and F2 are engaged.
will be free. Therefore, the first planetary gear set 3
Both the zero and second planetary gear sets 40 rotate at a constant speed and are in a directly connected state. When the overdrive stage is reached, the brake B0 is engaged, and the input to the carrier P1 increases the speed and drives the output gear 61 via the ring gear R1. Focusing on the second gear, a brake B2 and a one-way clutch F1 are used as means for stopping the sun gear S2 of the second planetary gear set 40. However, as is clear from Figure 1,
Even when brake B1 is engaged, sun gear S2 can be brought to a standstill. Therefore, the present invention provides a compact automatic transmission whose axial dimension is shortened by omitting the brake B2 and the one-way clutch F1. Furthermore, by improving the mounting structure of the return spring 24 of the brake B3, a more compact automatic transmission can be provided. The output gear 61 supported by the carrier shaft 5
By changing the bearing from a tapered roller bearing to a needle bearing, the nut for applying preload, which is essential to tapered roller bearings, is eliminated, and the axial direction can be further shortened. [Means for Solving the Problems] The transmission installed in the automatic transmission of the present invention is arranged concentrically with the input shaft of the transmission connected to the output shaft of the torque converter. an intermediate shaft, a sun gear shaft rotatably supported by the intermediate shaft, a first planetary gear set disposed on one of the sun gear shafts, and a second planetary gear set disposed on the other sun gear shaft. , an overdrive device disposed on the other of the intermediate shafts, the input shaft being coupled to the ring gear of the first planetary gear set via a first clutch and connecting the second clutch and the first brake. The sun gears of the first and second planetary gear sets are directly connected to the sun gear shaft through the intermediate shaft, and the pinion carrier of the first planetary gear set and the ring gear of the second planetary gear set are connected to the intermediate shaft. Second
The pinion carrier of the planetary gear set is connected to a stationary member via a second brake, and is provided with means for achieving four forward speeds and one reverse speed. The second brake is disposed on the radially outer side of the second planetary gear set, and the second
The hydraulic servo of the brake is arranged such that its piston and cylinder are disposed in one of the second brakes, and its return spring is disposed in a space outside the first planetary gear set in the radial direction. Means for connecting the second brake by an overhanging member is also provided. [Operation] By providing the above means, a compact automatic transmission with 4 forward speeds and 1 reverse speed can be created using 3 clutches, 3 brakes, and 2 one-way clutches as frictional engagement elements. Can be configured. The return spring of the servo that operates the second brake is separated from the piston and cylinder and placed in the space outside the first planetary gear set, and is connected to the piston with an overhang member, so the space is saved. Achieve a reduction in axial dimension through effective utilization. [Example] Hereinafter, an example of the present invention will be described with reference to FIGS. 2 and 4. FIG. 2 is an explanatory diagram similar to FIG. 1 showing an overview of the gear train of the automatic transmission of the present invention, and FIG. 4 is a sectional view similar to FIG. 3 showing the structure of the main parts of the automatic transmission. Therefore, similar components are given the same reference numerals and their explanations will be omitted. In FIG. 2, the transmission of the present invention has a first planetary gear set 30 disposed on the torque converter side (front side) which is a starting device, and a second planetary gear set 40 following the first planetary gear set 30. Sun gear S3 of set 30 and sun gear S2 of second planetary gear set 40 are connected via sun gear shaft 6. Input shaft 1 is connected to ring gear R3 of first planetary gear set 30 via clutch C1, and
2 to the sun gear shaft 6. Clutch C
A brake B1 is disposed on the outer periphery of the second drum. The pinion carrier P3 of the first planetary gear set 30 is connected via the intermediate shaft 4 to the carrier P1 of the third planetary gear set 60 and to the ring gear R2 of the second planetary gear set 40. Second planetary gear set 4
0 pinion carrier P2 is one-way clutch F2
or selectively engages a stationary member via brake B3. Carrier P of third planetary gear set 60
1 is connected to a sun gear shaft 62 integral with the sun gear S1 via a one-way clutch F0 or clutch C0, and the sun gear shaft 62 is connected to a stationary member by a brake B0. Ring gear R1 is connected to output gear 61. FIG. 4 shows a transmission 300 of the present invention.
This shows the specific structure of main transmission 10.
A and an overdrive device 50A.
Transmission chamber 122A of main housing 110A
A first hydraulic servo drum 7 is disposed on the inner side (on the torque converter side), and a piston 8 is fitted into the drum 7 to form a hydraulic servo 9 for the clutch C2.A return spring 10 is disposed on the inner peripheral wall side. Clutch C2 is installed on the outer peripheral wall side. A second hydraulic servo drum 14, which is open at the rear side of the first hydraulic servo drum 7 and has an annular projection at the front, has an annular piston 13 fitted between the rear end portion 2 of the input shaft 1, and controls the hydraulic servo of the clutch C1. 14, a return spring 15 is attached to the inner circumference, a clutch C1 is attached to the inner side of the outer circumference, and a clutch C2 is attached to the outer side of the annular projection.
is attached, and the first and second
Hydraulic servo drums 7 and 14 are connected. A first planetary gear set 30 is provided on the rear side of the second hydraulic servo drum 14, the ring gear R3 of which is connected to the second hydraulic servo drum 14 via a clutch C1, and the carrier P2 is connected to the intermediate shaft 4. The sun gear S2 is integrally connected to the sun gear shaft 6 by spline connection at its tip. Also, the first
A connecting drum 16 shaped so as to cover the second hydraulic servo drums 7, 14 and the first planetary gear set 30 in a minimum space is fixed at its leading end to the outside of the first hydraulic servo drum 7, and its rear end is connected to the first planetary gear set 30. The rear side of the first planetary gear set 30 is connected to the sun gear shaft 6, and a band brake B1 is provided on the outer peripheral wall. Conventionally, a hydraulic servo for the brake B2 was provided in the surplus space 16A outside the connecting drum 16 outside the first planetary gear set 30, but since the brake B2 and the one-way clutch F1 are omitted, , this hydraulic servo can also be removed, reducing the axial dimension of transmission 300A. Main housing 11 at the rear of the connecting drum 16
There is an annular protrusion or snap spring 1 inside 0A.
12A is provided to support the front end of the return spring 24A. A spline 20 is formed on the inner periphery of the main housing 110A behind the projection 112A, and the outer race 21 of the one-way clutch F2 and the brake B3 are fitted from the front. The piston 22A is fitted into the annular hole between the outer periphery of the center support 156A of the intermediate support wall 157 and the housing 110A, and the servo 23 of the brake B3 is installed.
form. A cylindrical overhang member 24B and a return spring 24A are provided for the return of the piston 22A.
Equipped with. The overhang member 24B consists of a disk member 24E and a cylindrical member 24F, and is made of sheet metal. The cylindrical member 24F has a groove that engages with the spline 20, and fits into the brake disc of the brake B3 and the outer race 21 of the one-way clutch F2 at the bottom side of the spline groove rather than the spline engagement portion, thereby engaging the brake B3 and the outer race 21 of the one-way clutch F2. It is arranged to overhang the one-way clutch F2. By using the overhang member 24B, the return spring 24A is connected to the connecting drum 16.
It can be arranged in the surplus space 16A behind the
By effectively utilizing the surplus space, the axial dimension of the transmission 300A can be further reduced. The inner race of the one-way clutch F2 is connected to the pinion carrier P2 of the second planetary gear set 40.
The ring gear R2 is spline-fitted to the intermediate shaft 4 via the side wall portion 42 and a boss portion 42A formed on the inner peripheral side of the side wall portion. Since there is no need to provide a return spring in the center support 156A, the axial dimension of the center support 156A can also be shortened. A carrier shaft 5 of a third planetary gear set is fitted into the splines of the intermediate shaft 4. By radially overlapping the front end portion 5A of the carrier shaft 5 with the outside of the boss portion 42A integral with the side wall portion 42 of the ring gear R2, the axial dimension can be further shortened. The carrier shaft 5 is supported on the inner periphery of the center support 156A by a ball bearing 52, and rotatably supports the output gear 61, which is integrated with the ring gear R1 of the third planetary gear set, on the outer periphery of the carrier shaft 5. . The bearing 54 between the carrier shaft 5 and the output gear 61 uses a needle bearing instead of a conventional tapered roller bearing. Therefore, it is possible to eliminate a nut for applying preload, which is essential to taper-to-roller bearings, and further shorten the axial dimension. Thrust bearings 52B and 56B are arranged on both sides of the output gear 61, respectively, and receive thrust from a mating member via thrust plates 52A and 56A. The rest of the configuration of the overdrive device 50A is the same as that of the conventional device explained in FIG. 3, so the explanation will be omitted. The transmission 300A of this embodiment controls each clutch and brake by selectively outputting hydraulic pressure from a hydraulic control device (not shown) to the hydraulic servo of each friction engagement device according to vehicle running conditions such as vehicle speed and throttle opening. is engaged or released, resulting in four forward speeds or one reverse speed change. Table 2 shows an example of the RANGE achieved by the operation of each clutch, brake, one-way clutch, and one-way brake.

〔Effect of the invention〕

As described above, the automatic transmission of the present invention includes a hydraulic torque converter, a transmission, and a hydraulic control device, in which the transmission is the output shaft of the torque converter and the input shaft of the transmission. A sun gear S3, a planetary carrier P3, a planetary carrier P3, and a cylindrical first sun gear shaft, which are rotatably fitted outside the intermediate shaft and which are arranged in series behind the intermediate shaft, are arranged at the front.
Forward gear consisting of a first planetary gear set with a ring gear R3, a sun gear S2 arranged at the rear, a planetary carrier P2, a second planetary gear set with a ring gear R2, clutches C1, C2, brakes B1, B3, and one-way clutch F2. A three-speed reverse and one-speed transmission is provided. A third planetary gear set including a sun gear S1, a planetary carrier P1, a ring gear R1, a clutch C0, and a brake B are mounted on the outside of the sun gear shaft rotatably fitted to the rear of the intermediate shaft.
0, an overdrive device consisting of a one-way clutch F0 is provided, and an output gear of the overdrive device is disposed between the transmission device and the overdrive device to form a transmission with four forward speeds and one reverse speed. . The output from the torque converter is input to ring gear R3 via clutch C1, or to a sun gear shaft directly connected to sun gears S2 and S3 via clutch C2 and brake B1, and to a carrier P3 directly connected to the intermediate shaft. Output from ring gear R2 and also from carrier P
2 is connected to the case via a one-way clutch F2 and/or a brake B3, and each clutch and brake C1, C2, B1, B3 are selectively engaged or released by the operation of these hydraulic servos to provide three forward speeds. The power output to the intermediate shaft after being shifted to one of the first reverse gears is input to the carrier P1 of the overdrive device, and the carrier P1 has the following:
One end of the clutch C0 is connected, and the clutch C0
The other end is connected to sun gear S1 via brake B0, and power is output from the output gear directly connected to ring gear R1. With this configuration, four forward speeds and one reverse speed are mounted on a set of rotating shafts arranged in series with the torque converter output shaft.
A gear train of stages is provided, the structure is simple, and the axial dimension can be shortened. Furthermore, a one-way clutch F2 that locks the carrier P2 in one direction is arranged on the front side of the outer part of the second planetary gear set, and a brake B3 that engages or releases the carrier P2 with the case is arranged on the rear side.
The hydraulic servo of brake B3 has its piston and cylinder installed on the rear side of brake B3, and its return spring is installed in the surplus space outside the first planetary gear set on the front side of the one-way clutch, and connects brake B3 and the one-way clutch. The configuration in which F2 is engaged with the piston by an overhanging member has the effect of further reducing the axial dimension, and can be suitably used in a FF vehicle with a horizontal engine. Furthermore, since there is no need to provide a return spring in the center support that accommodates the hydraulic servo of the second brake, the axial dimension of the center support can be shortened. The center support supports the carrier shaft at its inner circumference via a radial bearing, and the outer circumference of the carrier shaft rotatably supports the output gear integrated with the ring gear of the third planetary gear set via a needle bearing. Therefore,
By joining the ring gear of the second planetary gear set to the radial bearing that supports the carrier shaft and arranging the thrust bearing between the radial bearing and the output gear, it is possible to construct an automatic transmission that is even more compact in the axial direction. can.

[Brief explanation of drawings]

Fig. 1 is a skeletal diagram of a transmission of a conventional automatic transmission according to the present invention, Fig. 2 is a skeletal diagram of a transmission of an automatic transmission according to the present invention, and Fig. 3 is a skeletal diagram of a transmission of a conventional automatic transmission. Cross-sectional view of the machine, No. 4
The figure is a sectional view of a main part of a transmission of an automatic transmission according to the present invention. In the figure, 1... input shaft, 4... intermediate shaft, 5... carrier shaft, 6... sun gear shaft, 10A... transmission, 16...
Connection drum, 16A...excess space, 23...hydraulic servo of brake B3, 24A...return spring, 24B...overhang member, 30...first planetary gear set, 40...second planetary gear set, 50A...overdrive device, 60
...Third planetary gear set, C1, C2, C
3...Clutch, B0, B1, B3...Brake, F
0...One-way clutch, F2...One-way brake.

Claims (1)

[Scope of Claims] 1. An automatic transmission having a hydraulic torque converter, a transmission, and a hydraulic control device, wherein the transmission has an input shaft of the transmission connected to an output shaft of the torque converter. an intermediate shaft disposed concentrically with the input shaft; a sun gear shaft rotatably supported on the intermediate shaft; a first planetary gear set disposed on one of the sun gear shafts; a second planetary gear set disposed on the other of the intermediate shafts; and an overdrive device disposed on the other of the intermediate shafts, the input shaft being coupled to the ring gear of the first planetary gear set via a first clutch. At the same time, the sun gears of the first and second planetary gear sets are connected to the sun gear shaft through a second clutch and a first brake, and the pinion carrier of the first planetary gear set and the sun gear of the second planetary gear set are connected to each other. The ring gear of the planetary gear set is connected to the intermediate shaft, and the pinion carrier of the second planetary gear set is connected to a stationary member via a second brake, so that the automatic transmission achieves four forward speeds and one reverse speed. and the second
The second planetary gear set is arranged radially outwardly of the planetary gear set.
a brake, and a hydraulic servo of the second brake moves the piston and cylinder to the second brake.
a return spring of one of the brakes is arranged in a space radially outside of the first planetary gear set, and the piston of the hydraulic servo and the return spring are connected by an overhang member that overhangs the second brake. An automatic transmission characterized by: 2. The ring gear of the second planetary gear set and the carrier shaft of the overdrive device are fitted to the intermediate shaft via a spline, and the carrier shaft and the boss portion of the ring gear are overlapped in the radial direction to support the carrier shaft. Claim 1, characterized in that a thrust bearing is disposed between a radial bearing and an output gear integrated with a ring gear of a third planetary gear set rotatably supported by the carrier shaft. Automatic transmission.