JPS6141048A - Lubricating mechanism of frictional engagement device of automatic speed change gear - Google Patents

Abstract

PURPOSE:To stabilize the direction of lubricating oil flow and to prevent a rise in oil temperature by providing oil grooves for connecting the inner periphery and outer periphery to each other on the pressing surface of a piston for pressing a frictional engagement portion of a frictional engagement device. CONSTITUTION:In a transmission, there is provided a frictional engagement device 3, which is a multiple disc brake, in the rear of a rotary member 30 rotated when power is transmitted thereto. The frictional engagement device 3 has inner peripheral frictional engagement members 2 disposed alternately with outer peripheral frictional engagement members 1 on the outer periphery of an outer race 35 of a one-way clutch fixed thereto by spline-fitting. In this case, a plurality of oil grooves 8 for connecting the inner periphery side and the outer periphery side to each other are radially formed on a pressing surface 7 of a piston fitted in a cylinder 5, which is adapted to press the frictional engagement device 3. In this arrangement, even if the frictional engagement device 3 is engaged, lubricating oil can be smoothly discharged to the outer periphery side to prevent a rise in oil temperature.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application 1] The present invention relates to lubrication of a multi-plate type, conical type, etc. friction engagement device disposed in an automatic transmission.

[Prior Art] Conventionally, a brake of a frictional engagement device disposed in an automatic transmission consists of an outer circumferential engagement member attached to a fixed member disposed on the outer circumference and a power transmission mechanism disposed on the inner circumference of the outer circumferential engagement member. an inner peripheral engagement member attached to a rotatable inner peripheral member, a frictional engagement part in which a rotating member is disposed adjacent to one side in the axial direction, and a chain on the other side of the frictional engagement part. The hydraulic actuator is comprised of a piston attached to the piston and a cylinder fitted into the piston, and engages and disengages the frictional engagement part by pressing and releasing the frictional engagement part. The pressing surface of the piston that presses the frictional engagement portion was formed into an annular plane.

[Problems to be Solved by the Invention] In the above conventional technology, when the frictional engagement portion engages, the lubricating oil supplied from the shaft center side is blocked at the inner periphery of the pressing surface of the piston, so that the pressing force of the piston is reduced. The lubricating oil supplied to the inner periphery of the surface flows out from between the frictional engagement portion and the inner peripheral member toward the rotating member disposed at the corner, and is agitated by the rotating member.

An object of the present invention is to provide an oil groove in the pressing surface of the piston that presses the frictional engagement part, in which the inner periphery and the outer periphery communicate, so that oil can be supplied from the shaft center side of the automatic transmission to the inner periphery of the pressing surface of the piston. An automatic transmission that can prevent oil from being agitated by rotating members by supplying lubricating oil to the outer periphery of the pressing surface of the piston through an oil groove formed on the pressing surface of the piston, regardless of whether the frictional engagement part is engaged or disengaged. The present invention provides a lubrication mechanism for a frictional engagement device.

[Means for Solving the Problems] The lubrication mechanism of the frictional engagement device of the automatic transmission of the present invention has the following features:
As shown in the figure, a rotating member that rotates in response to power transmission, consisting of an outer circumferential engaging member 1 attached to an outer circumferential fixed member and an inner circumferential engaging member 2 attached to an inner circumferential member arranged on the inner circumference. A fluid actuator comprising a frictional engagement part 3 disposed adjacent to one side, a piston 4 attached to a chain part on the other side of the frictional engagement part 3, and a cylinder 5 fitted inside the piston 4. 6, an oil groove 8 is formed in the pressing surface 7 of the piston 4 that presses the friction engagement portion 3, the inner circumferential side and the outer circumferential side communicating with each other. The composition is as follows. , [Function] The lubrication mechanism of the frictional engagement device of the automatic transmission of the present invention having the above-mentioned configuration includes an oil groove 8 whose inner circumference and outer circumference communicate with each other on the pressing surface 7 of the piston 4 that presses the frictional engagement portion. By providing lubricating oil supplied to the inner periphery of the pressing surface 7 of the piston 4 from the shaft center side of the automatic transmission, the lubricating oil is formed on the pressing surface 7 of the piston 4 regardless of whether the frictional engagement part 3 is engaged or disengaged. The oil is supplied to the outer periphery of the pressing surface 7 of the piston 4 via the oil groove 8 .

[Effects of the Invention] The lubrication mechanism of the frictional engagement device for an automatic transmission of the present invention having the above-mentioned configuration has the following effects.

b) By providing an oil groove in the pressing surface of the piston that presses the frictional engagement part, in which the inner and outer peripheries communicate, the lubricating oil supplied to the inner periphery of the pressing surface of the piston from the shaft center side of the automatic transmission is provided. Regardless of whether the frictional engagement part is engaged or disengaged, the lubricating oil is supplied to the outer periphery of the piston's pressing surface through the oil groove on the piston's pressing surface, so the flow direction of the lubricating oil is always stable and rotation of the inner periphery of the piston's pressing surface is prevented. Prevents lubricating oil from flowing unexpectedly into the body, prevents oil from being agitated by rotating bodies, and prevents oil from becoming too hot.

(2) By providing an oil groove in the pressing surface of the piston that suppresses the frictional engagement part, in which the inner and outer peripheries communicate, lubricating oil can be supplied to the oil groove on the pressing surface of the piston, regardless of the engagement state of the frictional engagement part. The lubricating oil can be supplied to the outer periphery of the pressing surface of the piston through the lubricating oil, and the lubricating oil can be stably supplied to the members on the outer periphery of the pressing surface of the piston.

c) O1 lubricant is supplied from the shaft center side of the automatic transmission to the inner periphery of the piston's pressing surface by providing an oil groove in which the inner and outer peripheries communicate with each other on the pressing surface of the piston that presses the frictional engagement part. can be supplied to the outer periphery of the pressing surface of screws 1 to 1 through the oil groove on the pressing surface of the piston, regardless of whether the frictional engagement part is engaged or disengaged. The drainage performance of lubricating oil can be improved.

[Embodiment] Next, a lubrication mechanism of a frictional engagement device for an automatic transmission according to the present invention will be explained based on an embodiment shown in the drawings.

FIG. 1 is a sectional view showing a lubrication mechanism for a frictional engagement device of an automatic transmission of the present invention, and FIG. 2 is a sectional view of a vehicular automatic transmission to which the lubrication mechanism of a frictional engagement device of an automatic transmission of the present invention is applied. A cross-sectional view is shown.

The automatic transmission 100 includes a hydraulic torque converter 200, a transmission mechanism 300, and a hydraulic control device 400.

The transmission mechanism 300 includes an overdrive transmission 300A including one multi-disc clutch C01, one multi-disc brake BO1 and one one-sided clutch "0" operated by a first planetary gear device UO1 hydraulic servo, and a second planetary gear device. IJ1, third planetary gear unit U2, two multi-disc clutches C1, C2 operated by hydraulic servo, one belt brake B1, two multi-disc brakes B2, C3, and two one-way latches F1, F2. The underdrive transmission 300B has three forward speeds and one reverse speed.

A transmission case 110 of the automatic transmission 100 includes a torque converter housing 1 that accommodates a torque converter 200.
201 A fixed part If which is a transmission case formed by integrally forming a winter sky housing an overdrive transmission 300A and an underdrive transmission 300B.
The torque converter housing 120, the fixing member 130, and the extension housing 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 when driven by an engine (not shown), and a ring welded to the inner circumference of the front cover 201. A plate-shaped rear cover 202, 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 holding the turbine launch 204. 205, supported by a fixed shaft 207 connected to the transmission case 110 via a one-way clutch 206,
Stator 2 that increases torque capacity when the input rotation speed is low
08, the front cover 201 and the turbine shell 20
5 between the front cover 201 and the turbine shell 20.
5 is provided with a direct coupling clutch (lock-up clutch) 209 that rotates the same rotation. An internal gear oil pump 150 having an external gear 150a and an internal gear 1sob is housed between the cylindrical fixing member 130 continuous to the rear of the torque converter housing 120 and the torque converter housing 120, An oil pump body 152 having a cylindrical portion 151 protruding forward on the inner periphery is attached to the fixed member 1.
An extension member 210 fastened to the front part of the external gear 150a and connected to the inner circumferential end of the rear cover 202 is spline-fitted to the inner circumference of the external gear 150a via the inner circumference of the cylindrical part 151. Further, an oil pump cover 154 having a cylindrical front support 153 that is coaxial with the cylindrical portion 151 and protrudes rearward is fastened to the rear side of the oil pump body 152 to connect the oil pump housing 152 and the oil pump. The cover 154 is attached to the torque converter housing 12
0 and the fixing member 130 form a partition wall. Further, an overdrive transmission device 3 is provided in the middle of the fixed member 130.
Overdrive mechanism chamber 1, 30△ where 00A is formed
and the underdrive mechanism chamber 130B in which the underdrive transmission @30013 is formed.
32 are provided. At the rear of the fixing member 130 (on the right side in the figure), there is a cylindrical rear support 133 that protrudes forward.
A rear support wall 134 is provided.

Inside the front support 153 is a one-sided clutch 2 that supports the stator 208 of the torque converter 200.
A fixed shaft 207 of No. 06 is fitted, and a transmission mechanism 30, which is an output shaft of the torque converter 200, is fitted inside the fixed shaft 207.
0 input shaft 10 is rotatably supported. The input shaft 10 has a flange portion 101 at the rear end, and a rearward hole 102 is formed at the center of the rear end. An intermediate power transmission shaft 11 arranged in series with the input shaft 10 is rotatably attached to the rear of the input shaft 10, and the intermediate power transmission shaft 11 includes:
The tip of the intermediate transmission shaft 11 has a flange portion 111 at the rear end, and the tip of the output shaft 12, which transmits power to the driving wheels, slides into the rear end. A hole 112 is formed. The output shaft 12 has a sensor rotor 121 for rotation speed detection and a speedometer drive gear 122 fixed in a single extension housing 140, and a sleeve yoke for transmitting power to the driving wheels is fitted on the outer periphery of the rear end. A spline groove 123 is formed to allow the intermediate transmission shaft 11 to rotate, and is rotatably supported by the extension housing 140 via the sleeve yoke, and the front end is rotatably supported within the hole 112 of the intermediate transmission shaft 11.

The overdrive transmission 300A has the input shaft 10
A first planetary gear unit UO is provided behind the ring gear RO, whose ring gear RO is coupled to the intermediate transmission shaft 11 via a seven-lunge plate 113, the planetary carrier PO is coupled to the clutch portion 101 of the input shaft 10, and the sun gear SO is formed by the inner race shaft 13 of the one-way latch FO.

On the front side of the first planetary gear unit U0, there is a first
The hydraulic servo drum 14 is fixed to the inner race shaft 13, and the annular piston 15 is fitted between the outer circumferential wall 14A and the inner circumferential wall 14B of the first hydraulic servo drum 14, so that the gear rear PO and the first hydraulic servo drum 14 are engaged and A return spring 16 that forms a hydraulic force C-0 of the clutch CO that releases the clutch CO and presses the annular piston 15 toward the inner race shaft 13 toward the hydraulic servo C-0, and an outer peripheral wall 1.
A clutch CO is installed inside 4A, and the clutch CO
The first hydraulic servo drum 14 and the inner race shaft 13 are connected to the carrier PO. 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, a clutch CO and a brake BO are provided on the outer periphery between the outer race 17 and the fixing member 130, and the brake BO A piston 18 that presses the brake BO is fitted in front of the intermediate support wall 132 at the rear of the piston 18 and the intermediate support wall 1.
32, a hydraulic servo B-0 of the brake BO is formed, and a piston 1 is formed on the inner peripheral part 135 of the front end of the intermediate support wall 132.
A return spring 19 that presses the hydraulic servo 8 toward the hydraulic servo B-0 side is fitted.

In the underdrive transmission 300B, the second hydraulic servo drum 20 that opens rearward is connected to the intermediate support wall 13 at the front.
An annular piston 21 that presses the clutch C2 is fitted rotatably on the outer periphery of the second hydraulic servo drum 1-131, and an annular piston 21 that presses the clutch C2 is fitted between the outer circumferential wall 20A and the inner circumferential wall 20B. 20 forms the hydraulic pressure chamber C-2 of the clutch C2, and the inner peripheral wall 20B.
A return spring 22 that presses the annular piston 21 toward the hydraulic servo C-2 is installed on the side, and a clutch C2 is installed inside the outer peripheral wall 20. Said second hydraulic servo drum 2
At the rear of 0, there is an annular protrusion 2 that opens at the rear and at the front.
A third hydraulic servo drum 24 having a
A clutch C is fixed to the outer periphery of the flange portion 111 at the rear portion of
An annular piston 25 that presses the clutch C is fitted between the annular piston 25 and the third hydraulic servo drum 24.
1 hydraulic servo C-1 and clutch C1.
A return spring 26 presses and covers the annular screws 1 to 25 toward the hydraulic servo C-1 side, and an annular protrusion 23 on the inner peripheral side of the
A clutch C2 is attached to the outer periphery of the hydraulic servo drum 20.24, and the second and third hydraulic servo drums 20.24 are connected via the clutch C2. A second planetary gear device U1 is provided behind the third hydraulic servo drum 24, and its ring gear R1 is provided in front of a rotation support member 27 that rotatably supports the ring gear R1 on the outer periphery of the output shaft 12. Annular protrusion 2 provided in a protruding manner
8 and the third hydraulic servo drum 2 via the clutch C1.
The carrier P1 is spline-fitted to the front outer periphery of the output shaft 12, and the sun gear S1 is integrally formed at the tip of a ring gear shaft 29 rotatably provided on the outer periphery of the output shaft 12. In addition, the 2nd and 3rd hydraulic servo drum 2
0.24 and the second planetary gear unit U1 in a minimum space. The rotating member 30, which is a connecting drum that rotates in response to power transmission, is fixed to the outer periphery of the second hydraulic rib 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 a belt brake B1 for fixing and releasing the rotating member 30 is provided on the outer peripheral side. The rear corner of the rotating member 3 has a multi-disc brake on the front side that is engaged with a spline 136 formed on the inner periphery of the fixed member 130, and is engaged in a running state of 2nd speed or higher, and is released in other states. The outer peripheral friction engagement member 1, which is the brake plate of the friction engagement device 3, is spline-fitted to the rear side of the brake plate b3 of the brake B3. A fourth hydraulic servo drum 32 having an annular projection 31 on the front side is spline-fitted.

The frictional engagement device 3 is a brake disc arranged alternately with the outer periphery frictional engagement member 1 on the outer periphery of the outer race (inner periphery member) 35 of the one-way latch F1 which is rotatable in response to power transmission. An inner periphery friction engagement member 2 is attached to the outer periphery by spline fitting. .

A cylinder 5 is formed between the outer circumferential wall 328 of the fourth hydraulic zarpodrum 32 and the annular projection 31, and an annular piston 4 having a pressing surface 7 for pressing the frictional engagement device 3 is fitted into the cylinder 5. 7 is set so that the inner circumferential side and the outer circumferential side communicate with each other, and the lubricating oil supplied to the frictional engagement device 3 can be sufficiently released to the outer circumferential side even when the frictional engagement device 3 is engaged. A plurality of oil grooves 8 are provided radially. A hydraulic pressure cylinder B-2 of the frictional engagement device 3 is formed between the annular piston 4 and the fourth hydraulic servo drum 32, and the annular piston 4 is connected to the hydraulic servo drum B2 on the inner peripheral wall 32B side.
A return spring 34 is provided that presses to the side. Since the vehicle is usually running in second speed or higher, it is suitable to apply the present invention to a portion where the outer race 35 of the one-way latch F1 and the fixing member are fixed and released. . The outer peripheral side of the rear support 133 of the rear support wall 134 on the rear side of the frictional engagement device 3 and the fixing member 130
A plurality of pistons 371, 313 for pressing the brake B3 and a reaction sleeve 312 are fitted into the annular hole 36 formed between the hydraulic servo B-3 of the brake B3.
, and the pistons 371 and 373 are connected to hydraulic servo B
A return spring attachment 3 with a return spring 38 that presses towards the −3 side attached to the tip of the rear support 133
Supported by 8A. The inner race 39 of the one-way latch F2 arranged on the inner periphery of the brake B3 is connected to the fourth latch body drum 32 on the outer periphery of the ring gear shaft 29, and the brake B3 is arranged on the outer periphery of the outer race 40 of the one-way clutch F2. It is installed. In the third planetary gear device U2, a sun gear S2 is formed integrally with a sun gear shaft 29, a carrier P2 is connected to an outer race 40 of a one-way latch F2 on the front side, and a brake B3, and a parking gear 41 is attached to the outer periphery. A circumferential ring gear R2 is connected to the output shaft 12 via a connecting member 42 whose inner circumference is spline-fitted. The parking gear 41 is provided so that a parking pawl 43 engages with the parking gear 41 to fix the output shaft 12 when the shift lever of the automatic transmission is selected to the parking (P) position.

The transmission mechanism 300 controls various friction coefficients from a hydraulic control device 400 in a valve body 403 built in an oil pan 402 fastened to the lower part of a fixed member 130 with bolts 401 in accordance with vehicle running conditions such as vehicle speed and throttle opening. The hydraulic pressure selectively output to the hydraulic servo of the coupling device engages or disengages each clap and the brake gear 1, resulting in four forward speeds or one reverse speed change. Table 1 shows an example of the operation of each clutch, brake, and one-way clutch and the achieved gear position (RANGE).

Table 1 In Table 1, E indicates that the corresponding clutch or brake is engaged, and x indicates that the corresponding clutch or brake is disengaged.

The corresponding one-way latch of L is engaged in the engine drive state, but this engagement is not necessarily necessary as power transmission is guaranteed by a clutch or brake built in parallel. (lock). (L) indicates that the corresponding one-way latch engages only in the engine drive state and does not engage in the engine brake state. Roughly f indicates that the corresponding one-sided clutch is free.

[Brief explanation of the drawing]

FIG. 1 is a sectional view showing a lubrication mechanism for a frictional engagement device of an automatic transmission according to the present invention, and FIG. 2 is a vehicular automatic transmission to which the lubrication mechanism for a frictional engagement device for an automatic transmission according to the present invention is applied. FIG. In the figure 1... Outer peripheral frictional engagement member 2... Intermediate member 3
...Frictional engagement device 4 Piston 5...Cylinder 6
...Fluid actuator 7...Press surface 8...
Oil groove 1oo-automatic transmission

Claims (1)

[Scope of Claims] 1) Consists of an outer circumferential engaging member attached to a fixed member on the outer circumferential side and an inner circumferential engaging member attached to an inner circumferential member disposed on the inner circumference, and rotates in response to power transmission. A fluid actuator comprising: a frictional engagement part in which a rotating member is disposed on one side adjacent to the frictional engagement part; a piston attached to the other side adjacent to the frictional engagement part; and a cylinder fitted inside the piston. A friction engagement device for an automatic transmission, characterized in that an oil groove communicating between an inner circumferential side and an outer circumferential side is provided on a pressing surface of the piston that presses the frictional engagement part. Lubrication mechanism for the engagement device. 2) the frictional engagement portion engages in a running state of second speed or higher;
The lubrication mechanism for a frictional engagement device of an automatic transmission according to claim 1, wherein the lubrication mechanism is applied to a transmission mechanism of an automatic transmission that is released in other conditions. 3) The oil groove is set so that the lubricating oil supplied to the frictional engagement portion from the inner circumferential side can be sufficiently drained to the outer circumferential side. Lubrication mechanism for frictional engagement device of automatic transmission.