JPS6136559A - Speed change gear case of automatic speed change gear - Google Patents

Abstract

PURPOSE:To improve drainage of lubricating oil supplied to the outer periphery of a multiple disc brake by forming a spline forming portion of a speed change case having a spline in the inner periphery thereof corresponding to the form of a floor of a car, and deeply forming the spline. CONSTITUTION:A spline forming portion 1B of a speed change gear case 1 which is mounted below a floor A of a car, and has a spline 1A in the inner periphery is formed corresponding to the form of the floor A. The spline 1A is deeply formed. In this arrangement, as the capacity of the inner peripheral spline 1A for draining lubricating oil is increased, lubricating oil supplied to the outer periphery of a multiple disc brake can be quickly drained.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a transmission case having splines formed on its inner periphery.

[Prior Art] A transmission case of a conventional automatic transmission is attached to the lower part of a floor A of a vehicle as shown in FIG. Machine case 1
a rotating member 2 having an outer peripheral spline 2A on its outer periphery that rotates upon receiving power transmission on the inner periphery; a plate 3 spline-fitted to the internal spline 1A of the transmission case 1; and a spline 2A of the rotating member 2. It consists of a multi-disc brake 5 combined with a spline-fitting disc 4, and an actuator (not shown) that engages and releases the multi-disc brake 5, and the spline forming portion 1B of the spline 1A of the transmission case 1 rotates. The spline 1A of the transmission case 1 is provided so as to draw a circle in the circumferential direction from the center of the member 2.
The depth was determined by the minimum clearance between the floor A and the variable speed case 1 having the spline 1A.

[Problems to be Solved by the Invention] In the conventional technology having the above configuration, the multi-disc brake 5 disposed inside the transmission case 1 receives lubricating oil from the inner periphery to prevent seizure and wear. Yes, but the transmission case 1
Conventionally, the depth of the inner spline 1A on the outer periphery of the multi-disc brake 5 has not been formed shallow due to the constraints of the floor A, so it is possible to increase the amount of lubricating oil drained by the inner spline 1A on the outer periphery of the multi-plate brake 5. For this reason, transmission case 1
IIWII which is not drained from the inner peripheral spline 1A of
The oil drains from the inner periphery of the multi-disc brake 5 and flows out to the inner periphery of the multi-disc brake 5, and the lubricating oil is agitated by various rotating members provided on the inner periphery of the multi-disc brake 5, causing an increase in oil temperature. This causes deterioration of the lubricating oil due to
There were concerns that it would temporarily block the oil discharge port and obstruct the lubricating oil supply path.

The purpose of the invention is to utilize the amount of clearance between the vehicle floor and the transmission case to form deep grooves in the inner spline of the transmission case, thereby improving the drainage of lubricating oil supplied to the outer periphery of the multi-disc brake. Our goal is to provide a transmission case for automatic transmissions that

[Means for Solving the Problems] In order to solve the above problems, the transmission case of the automatic transmission of the present invention is attached to the lower part of the vehicle 707A and has a spline 1A on the inner periphery, as shown in FIG. Spline forming part 1B@ of machine case 1: It is formed in a shape corresponding to the shape of the floor A, and the spline 1A is deeply provided.

[Operations and Effects of the Invention] The transmission case of the automatic transmission of the present invention having the above-mentioned configuration is achieved by deepening the stomach of the inner circumferential spline 1A by utilizing the gap m between the floor A of the vehicle and the transmission case 1. Since each pair of inner peripheral splines 1A that drains lubricating oil becomes larger, for example, the lubricating oil supplied to the outer periphery of a multi-disc brake disposed inside can be quickly drained, and the lubricating oil can be supplied to the inner circumferential side of the multi-disc brake. In order to prevent rA lubricating oil from flowing out, it is prevented from being agitated by each rotating member arranged on the inner circumferential side of the multi-disc brake, preventing an increase in oil temperature and deterioration of lubricating oil viscosity, and rIUWJ oil being multi-disc. By preventing the lubricating oil from flowing back to the inner circumferential side of the brake, there is no fear that the lubricating oil flowing back will obstruct the lubricating oil supply path provided on the inner circumferential side of the multi-disc brake 5. Furthermore, since the transmission case 1 is formed to correspond to the shape of the floor A of the shaft, it can be mounted on a vehicle without changing the shape of parts on the vehicle side.

[Embodiment] Next, a transmission case of an automatic transmission according to the present invention will be described based on an embodiment shown in the drawings.

FIG. 1 is a sectional view showing a transmission case of an automatic transmission according to the present invention, and FIG.

Automatic transmission 100 includes a hydraulic torque converter 200, a transmission 300, and a hydraulic control device 400.

The transmission 300 includes a 1'M star gear device UO.
1 multi-disc clutch C0 operated by hydraulic servo
an overdrive transmission 300A that cooperates with 11 multi-disc brakes BO, # and one one-way latch FO;
2nd planetary gear set U1, 3rd T1 star gear set W1 ζ, two multi-disc clutches C1 and C operated by hydraulic pumps
2. One belt brake B1. Two multi-disc brakes B
2, B3, and two one-way latches F1, F2 after three forward gears! 1-speed underdrive transmission 1
It consists of 3ooB.

The transmission case 1 of the automatic transmission 100 includes a torque converter housing 120 that accommodates a torque converter 200.
, a transmission case 130 to which the present invention is applied, which is integrally formed with a winter box housing an overdrive transmission III 300A and an underdrive transmission [3003], and an extension housing 140 that covers the rear side of the automatic transmission 100. These torque converter housing 120, transmission case 130, and extension hinge 140 are each fastened with a large number of bolts.

The torque converter 200 is housed in a torque converter housing 120 that is open at the front (engine side), and includes a front cover 201 that rotates under the drive of an engine (not shown), and an annular plate welded to the inner circumference of the front cover 201. A rear cover 202 having a shape, a pump impeller 203 disposed around the inner peripheral wall of the rear cover 202, a turbine runner 204 disposed opposite to the pump impeller 203, and a turbine shell 205 holding the turbine launch 204. , a stator 208 that is supported by a fixed shaft 207 connected to the transmission case 1 via a one-way clutch 206 and increases the torque capacity when the input rotation speed is low;
A direct coupling clutch (lock-up clutch) 2 is provided between the front cover 201 and the turbine shell 205 to rotate the front cover 201 and the turbine shell 205 at the same time.
It is equipped with 09. The torque converter housing 1
Between the cylindrical transmission case 130 and the torque converter housing 120, which are continuous to the rear of the transmission case 20,
Inscribed l! with an external gear 150a and an internal gear 150b inside! An oil pump body 15 that accommodates the vehicle oil pump 0 and has a cylindrical portion 151 that protrudes forward on the inner periphery.
2 is fastened to the fiJ portion of the transmission case 130, and the extension member 210 connected to the inner circumferential end of the rear cover 202 extends outward through the inner circumference of the cylindrical portion 151. l gear 1
It is spline fitted to the inner periphery of 50a. Further, the cylindrical portion 151 is provided on the rear side of the oil pump body 152.
A cylindrical front support 1 that is coaxial with and protrudes rearward.
An oil bomb cover 154 having a diameter of 53 is fastened so that the oil pump housing 152 and the oil pump cover 154 form a partition between the torque converter housing 120 and the transmission case 130. In addition, an overdrive transmission 300A is formed in the middle of the transmission case 130, and an overdrive 1i1i! Underdrive mechanism chamber 13 where 11 to 130A and underdrive transmission 300B are formed
0B and Fa! An intermediate support wall 132 having a cylindrical center support 131 projecting rearward is provided.

A rear support ql 134 having a cylindrical rear support 133 protruding forward is provided at the rear (right side in the figure) of the transmission case 130.

Inside the front support 153 is a one-sided clutch 2 that supports the stator 208 of the torque converter 200.
A fixed shaft 201 of No. 06 is fitted, and the input shaft 10 of the transmission 300, which is the output shaft of the torque converter 200, is rotatably supported inside the fixed shaft 207. The input shaft 10 has a 7-lung portion 101 at the rear end,
A rearward facing hole 102 is formed in the center of the rear end.

An intermediate power transmission shaft 11 arranged in series with the input shaft 10 is rotatably mounted behind the input shaft 10, and the tip of the intermediate power transmission shaft 11 slides into a hole 102 of the input shaft 10. The intermediate transmission shaft 11 has a seven flange portion 111 at its rear end, and a rearward hole 112 is formed in the center of which the tip of an output shaft 12 that transmits power to the driving wheels slides. Output shaft 1
2 fixes the sensor rotor 121 for rotation speed detection and the speedometer drive gear 122 in the extension housing 140, and the rear end has a spline groove 1 on the outer periphery to attach the sleeve yoke that transmits power to the drive wheels.
23 is formed, and is rotatably supported by the extension housing 140 via a sleeve yoke, and the front end is rotatably supported within the hole 112 of the intermediate transmission shaft 11.

The overdrive transmission f 300A is provided with a first planetary gear @luo behind the input shaft 10, whose ring gear RO is connected to the intermediate transmission shaft 11 via a 7-lunge plate 113, and a planetary carrier PO is connected to the input shaft 10. Coupled with the seven flange portions 101 of the shaft 10, the sun gear SO is formed by the inner race shaft 13 of the one-way latch FO. 11th tooth Ig equipment ff1U.

On the front side, there is a first hydraulic servo drum 14 that opens rearward.
is fixed to the inner race shaft 13, and an annular piston 15 is fitted between the outer peripheral wall 14A and the inner peripheral wall 114B of the first hydraulic servo drum 14 to engage and disengage the carrier PO and the first hydraulic servo drum 14. A return spring 16 forms the hydraulic servo C-0 of the latch CO and presses the annular piston 15 toward the hydraulic servo C-0 on the inner race shaft 13 side, and a clutch CO is installed inside the outer peripheral wall 14A. The first hydraulic servo drum 14 and the inner race shaft 13 are connected to the carrier P via
O is connected. A one-way latch FO with the inner race shaft 13 as an inner race is provided on the inner periphery of the first hydraulic servo drum 14, and an outer race 1 is provided on the outer periphery of the one-way latch FO.
Clutch C between 7 and transmission case 130
O and a brake BO are provided, and a piston 1i that presses the brake BO is fitted in front of an intermediate support wall 132 behind the brake BO.
A hydraulic servo B-o of the brake BO is formed between the piston 1 and the piston 1 on the inner circumference 135 of the front end of the intermediate support 1i 132.
A return spring 19 is fitted in which presses the hydraulic seam 8 toward the hydraulic seabo B- and 0 side.

In the underdrive transmission [300[3], the second hydraulic servo drum 20, which opens toward the rear, is the intermediate support at the front!
It is freely rotatable to the outside of the center report 131 of 1132, and its outer wall 208 and inner circumference! l! An annular piston 21 that presses the clutch C2 is fitted between the annular piston 21 and the second hydraulic servo drum 20, and the oil of the clutch C2 is formed between the annular piston 21 and the second hydraulic servo drum 20 to form a cylinder C-12 and an inner peripheral wall 20B side. The annular piston 21 is connected to the hydraulic servo C-
Return spring 22 that presses to the 2 side, outer circumference 120A
A clutch C2 is attached to the inner side of the clutch C2. Behind the second hydraulic servo drum 20 is a third hydraulic servo drum 24 that is open at the rear and has an annular projection 23 at the front.
is fixed to the outer periphery of the flange portion 111 at the rear portion of the intermediate transmission shaft 11, and a clutch is connected between the rear end of the intermediate transmission shaft 11, the outer peripheral wall 24^ of the third hydraulic pump drum 24, and the outer periphery of the flange gll 111. Annular piston 25 pressing C1
is fitted to form the hydraulic servo C-1 of the clutch C1 between the annular piston 25 and the third hydraulic servo drum 24, and a return that presses the annular piston 25 toward the hydraulic servo C-1 on the inner peripheral side of the clutch C1. spring 26,
Furthermore, a clutch C2 is connected to the outer periphery of the annular projection 23, and the second and third hydraulic servo drums 20 are connected via the clutch C2.
．． 24 are connected. The third hydraulic servo drum 24
A second planetary float mount [Ul is provided behind the second planetary float unit [Ul], and its ring gear R1 is provided to protrude in front of a rotation support member 27 that rotatably supports the ring gear R1 on the outer periphery of the output shaft 12. The carrier P1 is spline-fitted to the front outer periphery of the output shaft 12, and the sun gear S1 is rotatably provided on the outer periphery of the output shaft 12. It is integrally formed at the tip of the thin gear shaft 29. Also, the second.
3 hydraulic servo drums 20, 24 and the 21st helical gear device 1[Jl] A connecting drum 30, which is shaped to cover the 2nd hydraulic servo drum 20, 24 and the 21st helical gear device 1 [Jl, with a minimum space, connects the second hydraulic servo drum 20 at its front end.
The rear end is connected to the sun gear shaft 29 behind the second planetary gear unit U1, and the connecting drum 3 is attached to the outer peripheral side.
A belt brake B1 is provided for fixing and releasing 0.

As shown in FIG. 1, the spline 1A formed on the inner periphery of the rear part of the transmission case 130 is deeply formed by forming the spline forming portion 1B corresponding to the shape of the spline 707A. The brake plate b2 of the brake B2 and the brake plate b3 of the brake B3 are spline-fitted to the rear, and between the brakes B2 and B3 there is a fourth hydraulic rib having a frontage and an annular protrusion 31 on the front side. The drum 32 is spline fitted. An annular piston 33 that presses the brake B2 is fitted between the outer peripheral wall 32^ of the fourth hydraulic servo drum 32 and the annular projection 31, and the annular piston 33 presses the brake B2.
A return spring 34 forms the hydraulic servo 3-2 of the brake B2 between the hydraulic servo drum 3 and the fourth hydraulic servo drum 32, and presses the annular piston 33 on the inner mold 32B side toward the oil J3-+1-bot B-2 side. is provided.

Also brake 8.2. A one-way latch F1 with the thin gear shaft 29 as an inner race is provided on the inner circumference of the brake, and a brake B2 is attached to the outer circumference of the outer race 35. A plurality of pistons 371, 373 and a reaction plate 37 press the brake B3 into an annular hole 36 formed between the outer circumferential side of the rear support 133 of the rear support wall 134 on the rear side of the brake B2 and the transmission case 130.
2 is fitted to form the hydraulic servo B-3 of the brake B3, and also connects the piston 371.373 to the hydraulic servo [3-
A return spring mount 38 is attached to the tip of the rear support 133, and a return spring 38 that presses toward the 3 side is attached to the tip of the rear support 133.
Supported by A. The inner race 39 of the one-way clutch F2 arranged on the inner periphery of the brake B3 is connected to the fourth hydraulic servo drum 32 on the outer periphery of the sun gear shaft 29.
A brake B3 is attached to the outer periphery of the outer race 40 of the one-way clutch F2. Third planetary gear unit 1ffU
2, the sun gear S2 is formed integrally with the ring gear shaft 29, the carrier P2 is connected to the outer race 40 of the one-way clutch F2 on the front side, and is connected to the brake B3,
A ring gear R2 having a parking gear 41 around its outer periphery is connected to the output shaft 12 via a connecting member 42 whose inner periphery is spline-fitted.

The parking gear 41 engages the parking pawl 4 when the shift lever of the automatic transmission is selected in the parking (P) position.
3 is provided so as to mesh with the parking gear 41 and fix the output shaft 12.

The transmission 300 controls vehicle speed and throttle! ? i
The hydraulic uJill device 400 in the valve body 403 built in the oil pan 402 fastened to the lower part of the transmission case 130 by a bolt 401 selectively controls the hydraulic servo of each friction engagement device depending on the driving conditions of the vehicle, such as once. Each clutch and brake is engaged or released by the hydraulic pressure output from the engine, so that four forward gears or rear gears can be shifted to four gears. Table 1 shows an example of the operation of each clutch, brake, and one-way clutch and the achieved gear position (RANGE).

! ! 1! ! 1, E indicates that the corresponding clutch and brake are engaged, and x indicates that the corresponding clutch and brake are disengaged.

On the other hand, L corresponds to the Yoi Clap, which is engaged in the engine drive state, but its engagement is not necessarily required since power transmission is guaranteed by a clutch or brake built in parallel with it ( lock). (L) indicates that the corresponding one-way clutch is engaged only in the engine drive state and is not engaged in the engine brake state. Furthermore, f indicates that the corresponding one-way clutch is free.

In the above embodiment, the transmission case of the automatic transmission of the present invention is attached to a multi-disc brake (82, B) provided on the rear side of the automatic transmission.
3), but the present invention is not limited thereto, and can be applied to multi-disc brakes such as the fiJ section side of an automatic transmission (for example, the multi-disc brake BO of this embodiment), the intermediate section, etc. Alternatively, a transmission case portion that does not use a multi-disc brake inside the transmission case may be made to correspond to the shape of a transmission case portion that includes a multi-disc brake.

[Brief explanation of drawings]

FIG. 1 is a front cross-sectional view showing a transmission case of an automatic transmission of the present invention, FIG. 2 is a cross-sectional view of an automatic transmission for a vehicle to which the transmission case of an automatic transmission of the present invention is applied, and FIG. 1 is a front sectional view of a spline forming portion of a conventional transmission case.

Claims (1)

[Claims] 1) A spline forming part of a transmission case that is attached to the lower part of the floor of a vehicle and has a spline on the inner periphery is formed in a shape corresponding to the shape of the floor, and the spline is provided deeply. Characteristic transmission case for automatic transmissions. 2) The transmission case for an automatic transmission according to claim 1, wherein the depth of the spline is shallow at the upper part to avoid interference with the floor above.