JPS6141064A - Hydraulic actuator of automatic speed change gear - Google Patents

Abstract

PURPOSE:To reduce a speed change shock by starting the supply of working fluid to one cylinder portion when a piston is displaced from a designated position by a preset distance in a fluid pressure actuator including a two-layer cylinder having inner and outer cylinder portions. CONSTITUTION:A hydraulic servo C-1 for operating a clutch C1 in a transmission includes a cylinder drum 1 integral with a flange-like portion 14A formed on one end of a power transmission shaft 14 and a two-layer cylinder 2 comprising inner and outer annular cylinder portions 2A, 2B. The two-layer cylinder 2 accommodates a piston 3 having inner and outer annular piston portions 3A, 3B fitted in the respective annular cylinder portions 2A, 2B, and the piston 3 is urged to the left by return urging means 4. In this case, when the piston 3 is displaced from the innermost stop point by a preset distance after the supply of pressure oil is performed to the inner cylinder 2A, an oil path 7 is formed for performing the supply of pressure oil to the outer cylinder 2B.

Description

DETAILED DESCRIPTION OF THE INVENTION [Technical Field] The present invention relates to a fluid pressure actuator for an automatic transmission that includes a two-layer cylinder section provided in two layers overlapping in the radial direction.

[Prior art] Automatic transmissions installed in vehicles, etc. are gear shift IIAM.
4, and a plurality of friction engagement elements such as a multi-disc clutch and a multi-disc brake for engaging the component with other components or an automatic transmission case (transmission case);
A fluid pressure actuator such as a hydraulic servo for engaging and disengaging the frictional engagement element, and a fluid sweat actuator are selectively operated according to the set position of the manual lever, vehicle speed, engine load, etc. to set a predetermined gear position. It has a hydraulic control device that configures. Among the frictional engagement elements,
A fluid actuator for a frictional engagement element that requires a particularly high transmission torque capacity, such as a multi-disc clutch for achieving forward travel, for example during first gear, is equipped with two annular cylinder sections arranged in parallel in the radial direction. A cylinder and two pistons (m) slidably attached to each of the two cylinder parts.
A combination with a bisline having ; is effective.

[Problem to be Solved] However, in this type of fluid pressure actuator of a conventional automatic transmission, the supply of hydraulic fluid to each of the two-layer cylinders is started almost simultaneously to both cylinders.
The configuration was such that only the supply speed of hydraulic oil after the start of supply was adjusted.

Therefore, it is a frictional engagement element that is engaged to achieve forward running in an automatic transmission, and as shown in FIG. an inner annular piston portion 3A slidably fitted into the inner annular cylinder portion; and an outer annular piston portion 3A slidably fitted into the outer annular cylinder portion. The piston 3 has a screw 1-ring part 3B, and the working fluid supply IJI to the outer annular cylinder part 2B is between the innermost part of the inner annular cylinder part 2A and the outer annular cylinder part 2B. In the hydraulic nervo C-1 of the multi-disc clutch C1 of the automatic transmission, which is performed via the hydraulic oil supply oil passage 7a that connects the innermost part fi, the pressure increase characteristic P2 of the hydraulic pressure of each annular cylinder part 2A and 2B A, P2
The change in B and the output shaft torque T1 of the automatic transmission is shown by the solid line in FIG. According to the graph in Figure 3, □ peaks m1 and m2 of transmission toilet fluctuation occur, and N
It can be seen that the impact was large at -0871.

An object of the present invention is to provide a fluid pressure actuator for an automatic transmission having the above-mentioned two-layer cylinder, in which near-ideal transmission torque change and hydraulic servo pressure increasing characteristics can be obtained.

[Solution Means] The fluid pressure actuator of the automatic e-transmission of the present invention has an inner annular cylinder portion 2A and an outer cylinder portion σ arranged in parallel on its outer periphery, as illustrated as a hydraulic servo C-1 in FIG. A two-layer cylinder 2 having an annular cylinder portion 2B, an inner annular piston portion 3A slidably fitted into the inner annular cylinder portion, and an inner annular piston portion 3A slidably fitted into the outer annular cylinder portion. The automatic transmission has a piston 3 having an outer annular piston portion 3B, and supply and discharge of working fluid to one of the annular cylinder portions is performed via an externally applied annular cylinder portion. Fluid pressure actuator■
- In the evening, the supply of working fluid to the other annular cylinder part is carried out via the working oil supply oil passage 7 that communicates when the piston 3 is displaced by a set distance from the stopping point at the innermost part of the cylinder. That is the composition.

[Effect] Since the present invention has the above configuration, it has the following effects.

The timing for starting the supply of working fluid to the outer cylinder section can be set as desired, and as a result, P2B shown by the dashed line in FIG.
The rise of oil pressure in the outer annular cylinder can be delayed, as shown in
Therefore, the change in the transmission torque capacity T2 of the frictional engagement device also has a characteristic curve ideal for reducing shift shock in an automatic transmission.

[Example] Next, the present invention will be explained based on a first example shown in FIG.

14 is an intermediate transmission shaft of a transmission of a vehicle automatic transmission, C1 is a clutch which is a multi-plate friction engagement element, and C-
1 indicates a hydraulic servo which is the fluid pressure actuator.

A collar-shaped portion 14A with a large outer diameter is provided on the outer periphery of the rear portion (right side portion in the figure) of the transmission shaft 14, and a rear end portion 15 at the rear of the rib-shaped portion 14A has a center hole 16 with a slightly larger outer diameter. At the front end of the outer periphery 14C of the collar portion 14Δ, there is a bottom wall portion 1A flush with the front surface 14D of the collar portion 14A, which extends from the outer periphery of the bottom wall portion 1Δ. A cylinder drum 1 is welded to the cylinder drum 1. The cylinder drum 1 is made up of an outer part 1B and a cradle drum part 1C which is further extended from the outer cylinder part 1B and has a spline ID on its inner periphery.

The hydraulic servo C-1 has an inner annular cylinder part (hereinafter referred to as the inner cylinder) 2A and an outer annular cylinder part (otherwise referred to as the outer cylinder) 2B provided on the outer periphery of the inner cylinder part 2A. Layer cylinder 2, said inner cylinder 2A
an inner annular piston part (hereinafter referred to as the inner piston) 3A that is slidable in the outer cylinder; an outer annular piston part (hereinafter referred to as the outer piston) 3B1 that is slidably fitted into the outer cylinder; Inner side screw 1 ~ Outer side screw 1
A screw 1 having an intermediate cylindrical portion 3C provided at the connecting portion of the hem
The piston 3 consists of a return mechanism 4, a return mechanism 4, and the like.

The inner cylinder 2A of the two-layer cylinder is an intermediate cylinder of the piston that slides on the outer peripheral surface 14E of the rear end portion of the transmission shaft in this embodiment, and the outer peripheral surface 140 of the tongue-shaped portion of the transmission shaft in this embodiment. The inner circumferential surface 3D of the portion 3C and the brim portion 14Δ
It is formed by the rear surface 14F of. The outer cylinder 2A of the two-layer cylinder is formed by the outer circumferential surface 440 of the brim portion 14A, the inner circumferential surface 1F of the outer cylindrical portion 1B of the drum 1, and the inner surface 1T of the bottom wall portion 1A. There is.

The inner piston 3Δ of the piston has an inner periphery 3E that slides on the outer periphery 14G of the rear end of the transmission shaft, and the outer periphery is continuous with the rear end of the inner periphery 3D of the intermediate cylindrical portion 3C of the piston. , the outer piston 3B has an inner periphery 3F surrounding the outer periphery 14C of the collar-shaped part of the transmission shaft, and an outer periphery 3G slidingly in contact with the inner periphery 1E of the outer cylindrical part of the drum.
A protrusion 3H is provided around the rear surface between the piston 3B and the outer piston 3B. Outer annular piston portion 3B of piston 3
A relief valve 3e consisting of a plug 3a with an A-recess and a ball valve 3b is taken.

The return force means 4 is a snap ring 4 fitted into a groove 4A provided on the outer periphery of the rear end of the transmission shaft 14.
B. An annular plate-shaped spring retainer 4C whose inner circumferential portion is locked by the snap ring 4B and externally fitted onto the rear octopus portion 148 of the transmission shaft; between the protrusion 3H of the piston and the outer circumferential portion of the spring retainer 4C; The return spring 4D is interposed between the return springs 4D and 4D.

The transmission shaft 14 has a hole 14 forming a lubricating oil supply path and a side hole 6 for supplying hydraulic oil to the inner cylinder 2A. In this embodiment, the sleeve hole G is formed from the center hole 16, and has an inner shaft 6A with a legal frame 6a fitted at the opening end, a radial hole 6B that communicates and covers the axial hole 6A and the outside of the shaft, The axial hole 6A and the inner cylinder 2
It consists of a diagonal hole 6C that communicates with A. In addition, the transmission shaft 1
The collar-shaped portion 14A of No. 4 is provided with an inner/outer cylinder communication oil passage that communicates the inner cylinder 2Δ and the outer cylinder 2B. In this embodiment, the inner and outer cylinder communication oil passages include an axial hole 7A provided from the rear surface 14F of the flange-shaped portion and a radial hole 7B opened at an intermediate position of the outer peripheral surface 14C of the flange-shaped portion. The oil passage 7, the shaft hole 8A formed in the axial direction from the rear surface 14F of the collar, the shaft hole 8Δ, and the radial hole 8 opened at the front side of the outer peripheral surface of the collar.
B and a hydraulic oil discharge passage 8 consisting of a check ball 8C provided in the shaft hole 8Δ.

The import 7C of the oil passage 7 into the outer cylinder is set to open when the piston 3 is displaced to the position indicated by the dashed line, and has an opening 8D at almost the innermost part of the outer cylinder of the oil passage 8. Zuru.

The clutch C1 includes an outer friction plate 9A meshed with a spline 1D with the clutch drum 1C, a clutch hub 9B provided coaxially with the clutch drum and connected to an output member (not shown), and an outer periphery of the clutch hub. The inner friction plate 9D is meshed with a spline 9C installed in the outer friction plate 9A, and is overlapped with the outer friction plate 9A by 6 points.

In this hydraulic servo C-1, when hydraulic oil is supplied from the oil passage 6 in a state where the piston 3 is stopped at the innermost part of the cylinder 2 (as indicated by the solid line in Fig. 1), the innermost part first turns out. Pressure oil enters cylinder 2A.

As a result, the piston 3 compresses the return spring 4D and is quickly displaced by the play clearance between the piston 3 and the friction plates 9A, 9D. Next, as the hydraulic pressure increases, the frictional force between the friction plates 9A and 90 is increased. In this state, the inboard 7G of the oil passage 7 opens and hydraulic oil begins to be supplied to the outer cylinder 3B. As a result, the transmission torque capacity (2) of the clutch C1 changes as shown in FIG. 3(b), reducing shift shock during gear changes.

FIG. 2 shows an automatic transmission for a vehicle using the hydraulic acticoator of the automatic transmission of the present invention. In this embodiment, the cylinder drum 1 is applied to a third hydraulic force driver 1146 forming a hydraulic force cylinder C-1 of the clutch C1.

Automatic transmission TA100 is hydraulic torque converter 200
, transmission 300 , and hydraulic control device 400
It consists of

The transmission 300 is an overdrive planetary gear shift comprising a first planetary gear set I-pl, one multi-disc clutch C0 operated by a hydraulic servo, one multi-disc brake BO1 and one one-way latch FO! ! The device 10, the second planetary gear head p2, the third
Forward with planetary gear set p3, two multi-disc clutches C1, C2 operated by hydraulic 1-nervo, one belt brake B1, two multi-disc brakes B2, B3 and two one-way runners F1, F2 It is comprised of an underdrive planetary gear transmission 40 with three reverse speeds and one reverse speed.

The case 110 of the automatic transmission is 1 to Lucon Hearta 20.
Torque converter housing 120, A-
It consists of a transmission case 130 that accommodates the bar drive planetary gear transmission 10 and the underdrive planetary gear transmission 40, and an extension housing 140 that covers the rear side of the automatic transmission 100. The mission case 130 and the extension housing 140 are each connected coaxially through a large number of ports 1 to 1.

The torque converter 200 is housed in a torque converter chamber 121 facing forward (engine side), includes a front cover 111 connected to an engine output shaft (not shown), and a circular ring welded to the front cover 111 at its outer periphery. A plate-shaped rear cover 112, a pump impeller 205 disposed around the inner peripheral wall of the rear cover 112, a turbine shell 20G disposed opposite the pump impeller 205,
A turbine shell 207 holding the turbine runner 206, a holder 201 supported by a fixed shaft 203 via a one-way clutch 202, and the front cover 11
I installed on the inside of 1! It consists of an annular plate-shaped clutch disc 50 whose inner periphery is connected to the J friction surface 20 and the turbine huff 208 which is an output member, and the front saw bar 11
1 and a turbine hub 208. Between the cylindrical transmission chamber 132 continuous to the rear of the torque converter chamber 121 and the torque converter chamber 121, there is provided a cylindrical portion 152 which is shaped like a single plate and projects forward from the center, and which accommodates the A-il pump 150 therein. An oil pump front cover 151 having an oil pump front cover 151 is bolt-fitted and fastened to the front end surface of the transmission case 130, and the cylindrical portion 152 is provided on the rear side of the oil pump front cover 151.
An oil pump cover 154 having a cylindrical 71 connector port 153 coaxial with and projecting rearward is fastened. The oil pump front cover 151 and the oil pump cover 154 are connected to the oil pump housing 155.
forming a torque converter chamber 121 and a transmission chamber 13.
2 Which bulkhead is it? In addition, an overdrive mechanism chamber 133 and an underdrive mechanism chamber 134 are partitioned between the transmission chamber 132 and the overdrive mechanism chamber 134. : An intermediate support wall 159 having a cylindrical center portion 158 projecting rearward is separately cast and fitted. At the rear, a rear support wall 157 is provided by integral casting, which supports a cylindrical rear bow 156 that projects forward.The space between the partition wall 155 and the rear support wall 157 is a transmission chamber. 132, a rear support wall 157 and an extension housing 140.
The output shaft chamber 141 of the gearbox is provided with an electronically controlled sensor rotor 143 and a speedometer drive gear 144. A sleeve yoke (not shown) coaxial with 153 is inserted.

The fixed shaft 203 of the one-way clutch 202 that supports the stator 201 of the torque converter 200 is fitted inside the front ribs 1 to 153, and the fixed shaft 203 of the one-way clutch 202 that supports the stator 201 of the torque converter 200 is fitted inside the fixed shaft 203. Input W011 is rotatably supported.

The input shaft 11 has a clutch portion 12a behind the front shafts 1 to 153, and a center hole 13 is formed in the center of the rear end portion 12 having a large diameter. At the rear of the input shaft 11, an intermediate transmission shaft 14 whose tip is in sliding contact with the center hole 13 and arranged in series with the pano J-shaft 11 is rotatably installed, and its large diameter rear end 15 A center hole 16 is formed in the center of which the tip of the output shaft 36 adheres. The output shaft 36 is connected to the intermediate portion 3
7 is the third planetary gear set 1-p3 ring gear R2
The sleeve yoke is spline-fitted to a flange handle 82 having a protruding shaft support 81 at the rear that meshes with the sleeve yoke.

In the overdrive 148 chamber 133, a first planetary gear set p1 is installed on the rear side of the input shaft 11, its ring gear RO is connected to the intermediate transmission shaft 14 via a flange handle 22, and the planetary carrier PO is connected to the input shaft 14. It is connected to the flange part 12a of the shaft 11, and the 1 Nankia SO
is formed on the in-place shaft 23. On the front side of the first planetary gear hit p1, a first hydraulic servo drum 24 that opens rearward is fixed to the inner race shaft 23, and an annular piston 25 is attached between the outer peripheral wall and the inner race shaft 23.
is fitted to form the hydraulic pressure 4)--bo C-0 of the clutch CO, and a return spring 26 is attached to the inner race shaft 23 side, and a Clara yCO is attached to the inside of the outer peripheral wall, and the carrier PO is connected to the clutch CO via the clutch CO. connected.

First hydraulic pressure υ - In-place shaft 23 on the inner circumference of the bottom drum 24
A one-way latch FO that connects the inner race is provided,
A clutch CO and a brake 80 are installed between the outer race 27 and the transmission case 130 on its outer periphery.
The screws 1 to 29 are fitted into the front side of the intermediate support wall 159 on the rear side to form the hydraulic lever B-0 of the brake BO, and the return spring 32 is fitted into the inner periphery 31 of the outer cylindrical part of the intermediate support wall 159. ing.

Inside the underdrive mechanism chamber 134, at the front, a second hydraulic rib drum 41 that opens rearward is rotatably fitted onto the center support 158, and an annular piston 42 is fitted between its inner and outer circumferential walls to control the hydraulic pressure of the clutch C2. A return spring 44 is installed on the inner peripheral wall side, and a clutch C2 is installed on the inside of the outer peripheral wall. At the rear side of the second hydraulic revo drum 41,
A third hydraulic servo drum 1 which forms a cylinder of a hydraulic actuator of an automatic transmission according to the present invention opens rearward and has a cylindrical clutch hub 35 welded to the front thereof. 1, the rear end 15
An annular piston 3 is fitted between the cylindrical clutch hub 35 and the outer peripheral wall to form a hydraulic servo C-1 of the clutch C1, and a return biasing means 4 is provided on the inner peripheral side. is attached, and the second and third hydraulic servo drums 41 are connected via a clutch C2. A second planetary gear set p2 is provided on the rear side of the third hydraulic servo drum 46, and its ring gear R1 is connected to the third planetary gear set p2 via a cylindrical clutch hub 48 and a clutch C1.
The carrier P1 is connected to the hydraulic nervo drum 4G, spline-fitted to the tip of the output shaft 3G, and the sun gear 81
is formed integrally with the sun gear shaft 45. Also, the second
．． A connecting drum 60, which is molded to cover the 3-hydraulic revo drum 41, 46 and the 2nd planetary gear set p2 in a minimum space, is fixed at its tip to the outer periphery of the 2nd hydraulic 1-no small drum 41, and at its rear end. is connected to the sun gear shaft 45 on the rear side of the second planetary gear L p2, and a belt brake B1 is provided on the outer circumferential side.

Transmission case 1 on the rear side of the brake B2
A brake eye flap b2 of the brake B2 and a brake eye flap b3 of the brake B3 are spline-fitted from the front to the spline 15 formed on the inside of the brake pad 30, and the outer peripheral side of the rear support 156 of the rear support wall 157 on the rear side and the transmission case. Insert screws 1 to 77 into the annular hole between 130 and 130.
is fitted to form a hydraulic servo B-3 of the brake B3, and a return spring 79 of the hydraulic servo B-3 is fitted.
is the flange plate 82 attached to the tip of the rear support 156
Supported by Inside the brake B2,
One-way landing F with sun gear shaft 45 as inner race
1 is tier I, outer lace 39 is Plei 2F 82
A one-way landing gear F2 is attached to the rear side of the one-way clutch F1 and has a return biasing means 90 and an inner race 83 spline-fitted to the fourth hydraulic servo drum 72 at the outside inner diameter. In the third planetary gear set ρ3, the sun gear S2 is formed integrally with the sun gear shaft 45, the carrier P2 is connected to the outer race 86 of the one-sided clutch F2 on the front side, and is also connected to the brake B3, and the parking gear 85 is arranged around the outer periphery. A ring gear R2 provided therein is connected to an intermediate portion 37 of the output shaft 36. The parking gear 85 engages the parking pawl 8 when the shift 1 lever of the automatic transmission is selected to the parking (P) position.
4 meshes with the parking gear 85 to fix the output shaft 36.

An intermediate cylinder 71 is press-molded on the annular fourth hydraulic servo drum 72 that is open to the front, and an annular piston 73 is fitted between the fourth hydraulic servo drum 72 and the intermediate cylinder 11 to control the hydraulic servo B of the brake B2. -2, a return spring 74 is installed between the inner peripheral wall of the fourth hydraulic servo drum 72 and the intermediate cylinder 71, and a brake B2 is installed inside the outer peripheral wall.

The transmission 300 is configured to adjust the transmis- sion case 1 depending on the driving conditions of the vehicle such as vehicle speed and throttle opening.
Each clutch and brake is controlled by hydraulic pressure selectively outputted to the hydraulic servo of each friction engagement device from a hydraulic control device 400 in a valve body 403 built in a delta oil pan 401 which is fastened to the bottom of a 30 with a bolt 402. is engaged or released, resulting in four forward speeds or one reverse speed change. Each clutch, brake,
Operation of the one-way clutch and the gear position achieved (RANGE)
) - Examples are shown in Table 1.

Table 1 In Table 1, E indicates that the corresponding clutch, brake, or one-way clutch is engaged.

([-) indicates that the corresponding one-way lunge is engaged only in the engine drive state, and is not engaged in the engine play 4= state. Furthermore, L is engaged in J3 in the corresponding one-way lunge engine drive state, but this engagement is not necessary because power transmission is guaranteed by a clutch or brake built in parallel. (lock).

Roughly, "" indicates that the corresponding one-sided clutch is free.Furthermore, "X" indicates that the corresponding clutch and brake are released.

[Brief explanation of the drawing]

FIG. 1 is a cross-sectional view of an embodiment of a fluid pressure actuator for an automatic transmission according to the present invention, FIG. 2 is a cross-sectional view of an automatic transmission employing the fluid pressure actuator, and FIG. 3 is a diagram showing hydraulic pressure rise characteristics and 2 is a graph showing changes in transmission 1 to torque capacity. In the diagram 2...Cylinder 3...Piston 100
... Automatic transmission 200 ... 1 ~ Luk converter 3
00...Transmission 400...Hydraulic control device C1...Multi-plate gangway-C-1...Hydraulic servo 2A...Inner annular cylinder part 2B...Outer annular cylinder part 3A.・Inner ring screw] Hen part
3B...Outer annular piston part

Claims (1)

[Scope of Claims] 1) A two-layer cylinder having an inner annular cylinder part and an outer annular cylinder part arranged in parallel on the outer periphery thereof, and a two-layer cylinder that is slidably fitted into the inner annular cylinder part. a piston having an inner annular piston part and an outer annular piston part slidably fitted in the outer annular cylinder part, the actuation of one of the annular cylinder parts; In a fluid pressure actuator for an automatic transmission in which fluid is supplied and discharged through the other annular cylinder part, the one annular cylinder part is arranged so that the piston is displaced by a set distance from a stopping point at the innermost part of the cylinder. A fluid pressure actuator for an automatic transmission, wherein the fluid pressure actuator communicates with the one annular cylinder.