JPH085379Y2 - Friction engagement device for shifting of automatic transmission - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION [Industrial application] The present invention relates to a speed change friction engagement device for an automatic transmission used in a vehicle such as an automobile, and more particularly to a hydraulically actuated compound clutch.

[Prior Art] An automatic transmission used in a vehicle such as an automobile has a gear type transmission formed of a planetary gear unit and the like, and the gear type transmission includes a plurality of shifting frictions such as a clutch and a brake. The engagement device is engaged or disengaged in a predetermined combination to switch between a plurality of shift speeds to selectively establish a plurality of forward speeds and one reverse speed. .

The friction engagement device for shifting in an automatic transmission is generally
Is a hydraulically actuated multi-disc clutch or multi-disc brake,
In order to reduce the number of parts in this kind of automatic transmission and to increase the degree of freedom in downsizing design, some of the constituent members of a plurality of clutches arranged adjacent to each other are made common and frictional engagement is performed. A hydraulically actuated compound clutch has been proposed in which the number of constituent parts of the device is reduced and the device is miniaturized. This is disclosed in, for example, Japanese Patent Application Laid-Open No. 62-141343.

This composite clutch has an outer clutch member having a cylindrical portion and an end wall portion closing one end of the cylindrical portion, and a cylindrical portion arranged inside the outer clutch member and concentric with the cylindrical portion of the outer clutch member. The first inner clutch member and the cylindrical portion of the outer clutch member or the cylindrical portion of the first inner clutch member are spline-engaged with each other and are axially pressed against each other to frictionally engage with each other to form the outer clutch member and the outer clutch member. A first clutch plate and a first clutch disc that connect the first clutch member in a torque transmission relationship, a cylindrical portion and an end wall portion that closes one end of the cylindrical portion are provided inside the outer clutch member. The hydraulic clutch chamber is formed between the outer clutch member and the end wall portion of the outer clutch member by spline engagement so as to be movable in the axial direction. A first piston member for axially pressing the clutch plate and the first clutch disc with each other, and a cylindrical portion arranged inside the first piston member and concentric with the cylindrical portion of the first piston member. A second inner clutch member, the first piston member and the cylindrical portion of the first piston member or the cylindrical portion of the second inner clutch member is spline engaged and frictionally engaged by being pressed against each other, and the first piston member. A second clutch plate and a second clutch disc that connect the second inner clutch member to each other in a torque transmitting relationship with each other, and the second clutch plate and the second clutch disc are axially movably fitted to the inner side of the first piston member. And a hydraulic servo chamber is defined between the piston member and the end wall portion of the piston member, and the second clutch plate and the second clutch disc are axially pressed against each other. A second clutch member, and the first clutch is composed of the outer clutch member, the first clutch plate, the first clutch disc, the first inner clutch member, and the first piston member. A second clutch is constituted by the first piston member, the second clutch plate, the second clutch disc, the second inner clutch member, and the second piston member.

[Problems to be Solved by the Invention] In the compound clutch as described above, the piston member (first piston member) of one clutch is configured as an outer clutch member that is a drum member of the other clutch,
When the piston member of one clutch acts as the outer clutch member of the other clutch, the piston member is, as described above, so that the rotational force is input to the piston member from the outer clutch member of the one clutch. Splined to the outer clutch member of the clutch member. In this operating state, the rotational force is transmitted by metal contact at the spline engagement portion, so that wear and indentation occur on the side wall of the spline groove. Therefore, there is a possibility that the piston member may be caught by the outer clutch member of one of the clutches and may not be able to move in the axial direction due to long-term use, and a normal piston action may not be performed.

The present invention has been made in view of the above problems, and an object of the present invention is to provide a compound clutch type friction engagement device that guarantees normal operation even when used for a long period of time.

[Means for Solving the Problems] According to the present invention, the above-mentioned object is, in the above-described shift friction engagement device for an automatic transmission, the outer clutch member and the first clutch plate. Having a first spline for spline engagement and a second spline for spline engagement with the first piston member on the same inner diameter,
The first spline has a wider spline width than the second spline, and the tip edge of the first piston member on the side of the first clutch plate is located at the position where the first spline is disposed even in the retracted position. This is achieved by a shifting frictional engagement device characterized in that the axial dimension of the first spline is determined to be in a corresponding position.

[Operation and Effect of the Invention] According to the above-mentioned configuration, the transmission of the rotational force between the outer clutch member of the first clutch and the first piston member is performed only by the second spline, and Since the tip edge of the one piston member is always apart from the second spline and at a position corresponding to the first spline, that is, the tip edge of the first piston member is away from the second spline, Wear of the spline groove side wall of the spline, indentation occurs, even if the spline groove side wall is recessed, the first piston member does not get caught in the recess of the spline groove side wall,
The forward movement of the first piston member is not obstructed when the first clutch is engaged.

[Embodiment] An embodiment of the present invention will be described in detail below with reference to the accompanying drawings.

FIG. 1 shows an example of a planetary gear type transmission of an automatic transmission for a vehicle to which a friction engagement device for shifting according to the present invention is applied. In the figure, 10 is a first sun gear, 12 is a first ring gear concentric with the first sun gear 10, and 14 is a first sun gear 10.
And a first planetary pinion that meshes with the first ring gear 12, 16 is a first carrier that rotatably carries the first planetary pinion 14, 20 is a second sun gear, and 22 is a second sun gear that is concentric with the second sun gear 20. Two ring gears, 24 is the second sun gear
Reference numeral 26 denotes a second planetary pinion that meshes with the second ring gear 22 and 20, and 26 denotes a second carrier that rotatably carries the second planetary pinion 24. First ring gear
12 is connected to a second carrier 26 by a connecting element 30 and the first carrier 16 is connected to a second ring gear 22 by a connecting element 32.

Here, the simple planetary gear mechanism constituted by the first sun gear 10, the first ring gear 12, the first planetary pinion 14, and the first carrier 16 is referred to as a first-row planetary gear mechanism, and is referred to as the second sun gear 20. The simple planetary gear mechanism composed of the second ring gear 22, the second planetary pinion 24, and the second carrier 26 is referred to as a second-row planetary gear mechanism.

By the first carrier 16 and the connecting element 32, the first carrier
A first one-way clutch 34 and a second one-way clutch 36 are provided in series between the second ring gear 22 connected to 16 and the housing 50. In this case, the first one-way clutch 34 is provided on the first carrier 16 side, and the second one-way clutch 36 is provided on the housing 50 side. More specifically, the first one-way clutch 34
Is connected to the first carrier 16 by the inner race 34a, the outer race 34b is connected to the inner race 36a of the second one-way clutch 36 by the connecting member 31, and the outer race 36b of the second one-way clutch 36 is connected to the housing 50. There is.

The second carrier 26 is connected to the output gear 53 and always acts as an output member.

The first one-way clutch 34 is engaged when the outer race 34b attempts to rotate beyond the rotation speed of the inner race 34a during engine driving, and is engaged when the outer race 34b rotates in the opposite direction, and the second one-way clutch 34 The engagement 36 is engaged when the inner race 36a rotates in the reverse direction with respect to the outer race 36b when the engine is driven, and is engaged when the inner race 36a is reversed.

A first clutch 38 is provided between the second sun gear 20 and the input shaft 52 to selectively connect them to each other.

A second clutch 40 is provided between the first carrier 16 and the input shaft 52 to selectively connect the two to each other.

A third clutch 42 is provided between the first sun gear 10 and the input shaft 52 to selectively connect the both.

A fourth clutch 44 is provided between the first sun gear 10 and the connecting member 31 to selectively connect the both.

A first brake 46 that selectively fixes the connecting member 31 to the housing 50 is provided between the connecting member 31 and the housing 50.

A second brake 48 that selectively fixes the second ring gear 22 to the housing 50 is provided between the second ring gear 22 and the housing 50.

With the planetary gear type transmission configured as described above, the first step, the second step, the third step (direct connection step), the fourth step (increasing step) and the reverse step are achieved. It is as shown in Table 1. In this table, ○ indicates that the relevant clutch, brake or one-way clutch is engaged in the engine drive state, and (○) indicates that if the relevant clutch or brake is engaged, the shift It shows that the engine brake can act on the stage.

When the ratio of the number of teeth of the first sun gear 10 to the number of teeth of the first ring gear 12 is ρ ₁ and the ratio of the number of teeth of the second sun gear 20 to the number of teeth of the second ring gear 22 is ρ ₂ , The gear ratio is as shown in Table 2.

As shown in FIG. 2, the automatic transmission for a vehicle has a hydraulic torque converter 60 of a general structure having a pump element 62, a turbine element 64 and a stator element 66.
A hydraulic pump 68 serving as a hydraulic pressure supply source for the servo hydraulic pressure and the lubricating hydraulic pressure is provided on the side of the fluid torque converter 60.

The input shaft 52 is a turbine element of the hydraulic torque converter 60.
It is composed of a converter-side input shaft 52a connected to 64 and a gear-side input shaft 52b provided on the side of the planetary gear type transmission described above, and both input shafts are connected to each other by a spline 54.

The friction engagement device according to the present invention is, in this embodiment,
The second clutch 40 and the third clutch 42 are configured as a composite clutch, the third clutch 42 corresponds to the first clutch, and the second clutch 40 corresponds to the second clutch.

Details of the friction engagement device according to the present invention are shown in FIG.

The third clutch 42 is a dedicated clutch for establishing the reverse gear, and is the outer clutch member 10 as a clutch drum.
Has 0. The outer clutch member 100 has a cylindrical portion 102 and an end wall portion 104, and is integrally fixedly connected to the gear side input shaft 52b. A cylindrical first inner clutch member 106 is arranged inside the outer clutch member 100, and the first inner clutch member 106 is connected to the sun gear 10. The first inner clutch member 106 has a cylindrical portion 108 that is concentric with the cylindrical portion 102.

Between the cylindrical portions 102 and 108, a plurality of clutch plates 110 spline-engaged with the first splines 103a of the cylindrical portion 102 and clutch discs 112 spline-engaged with the splines 109 of the cylindrical portion 108 are alternately provided. Has been. The clutch plate 110 and the clutch disc 112 are pressed against each other in the axial direction to frictionally engage with each other and thereby the outer clutch member 100 and the first inner clutch member 1
06 and 06 are connected to each other in a torque transmission relationship.

Inside the outer clutch member 100 is a first piston member 1
14 are arranged. The first piston member 114 has a cylindrical portion 116 and an end wall portion 118, is spline-coupled to the second spline 103b of the outer clutch member 100 on the outer side of the cylindrical portion 116, and cannot rotate. Is in sliding contact with the inner peripheral surface of the outer clutch member 100, and the inner peripheral surface 122 is at the gear side input shaft.
The outer peripheral surface of 52b is slidably contacted, guided by these, and movable in the axial direction.

The first spline 103a and the second spline 103b are axially continuous with each other on the same inner diameter of the inner peripheral surface of the outer clutch member 100, and are well shown in FIGS. 3 and 4. As described above, the spline width of the first spline 103a is wider than the spline width of the second spline 103b. This spline width difference is equal to the second spline 10
It may be determined according to the durability period or the like in order to guarantee the wear amount of the side wall of the spline groove of 3b. The interrelationship between the axial dimensions of the first spline 103a and the second spline 103b and the axial dimension of the spline engagement portion of the first piston member 114 is as shown in FIG. Even when the first piston member 114 is most retracted, the first piston member 114
Is defined such that the tip of the is positioned within the first spline 103a.

The first piston member 114 defines a hydraulic servo chamber 124 between the end wall portion 118 and the end wall portion 104 of the outer clutch member 100. The first piston member 114 has a hydraulic servo chamber 124.
When hydraulic pressure is applied to the shaft, it moves axially to the right in the drawing, and engages with the clutch plate 110 at the tip of the cylindrical portion 116 to press the clutch plate 110 and the clutch disc 112 in the axial direction. It has become.

A cylindrical second inner clutch member 132 is arranged inside the first piston member 114, and the second inner clutch member 132 is a carrier by a sleeve member 134 fitted to the outer periphery of the gear side input shaft 52b. It is connected with 16. The second inner clutch member 132 has a cylindrical portion 136 concentric with the cylindrical portion 116 of the first piston member 114.

A spline 117 of the cylindrical portion 116 is provided between the cylindrical portions 136 and 116.
Clutch plate 138 and cylindrical portion 136 splined to
A plurality of clutch discs 140 spline-engaged with the splines 137 are alternately provided. The clutch plate 138 and the clutch disc 140 are axially pressed against each other to frictionally engage with each other to transmit torque between the first piston member 114, in other words, the outer clutch member 100 and the second inner clutch member 132. It is designed to connect to relationships.

A second piston member 144 is arranged inside the first piston member 114. The second piston member 144 slidably contacts the inner peripheral surface of the first piston member 114 on the outer peripheral surface and the outer peripheral surface of the input shaft 52 on the inner peripheral surface, and is guided by these to move in the axial direction. It is possible. The second piston member 144 defines a hydraulic servo chamber 150 between itself and the end wall portion 118 of the first piston member 114. The second piston member 144 is axially moved to the right in the figure by applying hydraulic pressure to the hydraulic servo chamber 150, and is engaged with the clutch plate 138 to move the clutch plate 138 and the clutch disc 140 in the axial direction relative to each other. It is designed to be pressed.

A spring retainer 154 is attached to the gear-side input shaft 52b, and a compression coil spring 156 is attached between the spring retainer 154 and the second piston member 144. The compression coil spring 156 applies an axial force, that is, a returning force, to the second piston member 144 toward the left in the figure. This returning force acts on the second piston member 144 and is further transmitted to the first piston member 114 via the second piston member 144. That is, the compression coil spring 156 includes the return spring of the first piston member 114 and the second piston member 144.
It also serves as a return spring.

Therefore, in this embodiment, the first piston member 11
4 also serves as the piston of the third clutch 42 and the outer clutch member of the second clutch 40, and the compression coil spring 15
6 also serves as a return spring for the two clutches.

The outer clutch member 100, the clutch plate 110, the clutch disc 112, the first inner clutch member 106, and the first piston member 114 constitute a third clutch 42 that is a dedicated clutch for the reverse gear. Piston member
The 114, the clutch plate 138, the clutch disc 140, the second inner clutch member 132, and the second piston member 144 constitute the second clutch 40 which is a dedicated clutch for the forward speed.

The second clutch 40 is supplied with hydraulic pressure to the hydraulic servo chamber 150 only when it is in the forward gear and is engaged, and the third clutch 42 is supplied with hydraulic pressure to the hydraulic servo chamber 124 only when it is in the reverse gear and is engaged. Does not engage simultaneously at any gear.

When the hydraulic pressure is supplied to the hydraulic servo chamber 124 when the reverse gear is achieved, the first piston member 114 moves the second spline 1
03b spline-engages and slides to the outer clutch member 100 in the axial direction to the right in the figure, and the leading edge thereof presses the first clutch plate 110. This brings the third clutch 42 into the engaged state, and the first sun gear 10
And the input shaft 52 are connected.

When the hydraulic pressure is supplied to the hydraulic servo chamber 150 to engage the second clutch 40 when the third speed or the fourth speed is achieved, the second piston member 144 moves to the right in the figure. Then, the second clutch plate 138 is pressed. As a result, the second clutch 40 is engaged, and the first piston member 114 is connected to the outer clutch member 100 by the second spline 103b. And the input shaft 52 are connected in a rotational force transmitting relationship. When the second clutch 40 is engaged, the rotational force is transmitted from the outer clutch member 100 to the first piston member 114 by the second spline 103b, so that the side wall of the spline groove of the second spline 103b is worn. However, dents are formed, and a dent is formed on the side wall of the spline groove after long-term use. Even if there is a depression on the side wall of this spline groove, the first piston member
Since the tip edge of 114 is located at a position corresponding to the first spline 103a apart from the second spline 103b, it does not get caught in the depression of the side wall of the spline groove, and the engagement of the third clutch 46 as described above. At times, the forward movement of the first piston member 114 is not hindered.

[Brief description of drawings]

FIG. 1 is a skeleton diagram showing an example of a planetary gear type transmission for an automatic transmission suitable for a vehicle in which the shifting friction engaging device of the present invention is incorporated, and FIG. 2 is a shifting friction engaging device of the present invention. FIG. 3 is a vertical cross-sectional view showing an embodiment of an automatic transmission for a vehicle in which is incorporated, FIG. 3 is a front view of an outer clutch member used in a friction engagement device for shifting according to the present invention, and FIG. 4 is FIG. FIG. 10 …… First sun gear, 12 …… First ring gear, 14 …… First planetary pinion, 16 …… First carrier, 20 …… Second sun gear, 22 …… Second ring gear, 24 …… Second planetary pinion , 26 …… Second carrier 30,31,32 …… Connecting element, 3
4 …… First one-way clutch, 36 …… Second one-way clutch, 38 …… First clutch, 40 …… Second clutch, 42…
… Third clutch, 46 …… First brake, 48 …… Second brake, 100 …… Outer clutch member, 101 …… Inner peripheral surface, 102 …… Cylindrical section, 103 …… Spline, 104 …… End wall section , 106 …… first inner clutch member, 108 …… cylindrical part, 109 …… spline, 1
10 …… Clutch plate, 112 …… Clutch disc, 113
a …… first spline, 113b second spline, 114 ……
1st piston member, 115 …… Inner peripheral surface, 116 …… Cylindrical part, 118
...... End wall part, 120 …… Outer peripheral surface, 122 …… Inner peripheral surface, 124 …… Hydraulic servo chamber, 132 …… Second inner clutch member, 134 …… Sleeve member, 136 …… Cylindrical part, 137… … Spline, 138 …… Clutch plate, 140 …… Clutch disc, 141 …… Spline, 144 …… Second piston member, 150 …… Hydraulic servo chamber, 152 …… Check valve, 154… Spring retainer, 156… ... Compression coil spring

Front page continued (72) Creator Masafumi Kinoshita 1 Toyota Town, Toyota City, Aichi Prefecture Toyota Motor Corporation (56) Reference JP 62-141343 (JP, A) U) Actual development Sho 57-79230 (JP, U)

Claims (1)

[Scope of utility model registration request] 1. An outer clutch member having a cylindrical portion and an end wall portion that closes one end of the cylindrical portion, and a cylindrical portion disposed inside the outer clutch member and concentric with the cylindrical portion of the outer clutch member. The first inner clutch member and the cylindrical portion of the outer clutch member or the cylindrical portion of the first inner clutch member are spline-engaged with each other and are axially pressed against each other to frictionally engage with each other to form the outer clutch member and the outer clutch member. A first clutch plate and a first clutch disc that connect the first clutch member in a torque transmission relationship, a cylindrical portion and an end wall portion that closes one end of the cylindrical portion are provided inside the outer clutch member. The hydraulic clutch chamber is formed between the outer clutch member and the end wall portion of the outer clutch member by spline engagement with the outer clutch member so as to be movable in the axial direction. And a first piston member that presses the first clutch disc in the axial direction, and a cylindrical portion that is arranged inside the first piston member and that is concentric with the cylindrical portion of the first piston member. A second inner clutch member, the first piston member and the cylindrical portion of the first piston member or the cylindrical portion of the second inner clutch member is spline engaged and frictionally engaged by being pressed against each other, and the first piston member. A second clutch plate and a second clutch disc that connect the second inner clutch member to each other in a torque transmitting relationship, and the second clutch plate and the second clutch disc are axially movably fitted inside the first piston member. Second piston plate for axially pressing the second clutch plate and the second clutch disc with each other by defining a hydraulic servo chamber between them and the end wall of the piston member. A tongue member, the first clutch is constituted by the outer clutch member, the first clutch plate, the first clutch disc, the first inner clutch member and the first piston member, Gear shift of an automatic transmission in which a second clutch is constituted by the first piston member, the second clutch plate, the second clutch disc, the second inner clutch member, and the second piston member. In the friction engagement device for a vehicle, the outer clutch member has a first spline spline-engaged with the first clutch plate and a second spline spline-engaged with the first piston member on the same inner diameter. The first spline has a wider spline width than the second spline,
The axial dimension of the first spline is determined so that the tip edge of the first piston member on the first clutch plate side is located at the position corresponding to the disposition position of the first spline even in the retracted position. And a frictional engagement device for speed change.