JPS61252964A - Directly coupled clutch for hydraulic transmission - Google Patents

Abstract

PURPOSE:To enlarge the range of absorbable torque capacity without increasing the diameter of damper mechanism by holding the first plate between first shock-absorbing member and second plate. CONSTITUTION:First plate 24 is held between first shock-absorbing member 23 and second plate 25. The output transmitted through a piston 21 is transmitted through the first plate 24, the first shock-absorbing member 23, second plate 25, second shock-absorbing member 26 and third plate 27 to the output member serially. Consequently, the absorbable torque capacity can be enlarged without increasing the diameter of the damper mechanism 22.

Description

[Detailed description of the invention] [Industrial application field] The present invention relates to a direct coupling clutch for a fluid transmission device.

[Prior Art] A direct coupling clutch used in a fluid transmission device is a fluid transmission device that connects via fluid between an input member that receives the output of an engine mounted on a vehicle and an output member that outputs output to a transmission mechanism. a piston that removably engages with the input member of the
It consists of a drive plate connected to the piston, and a damper mechanism consisting of a driven plate connected to the output member of the fluid transmission device connected via the drive plate and the Ii member, which is required for a direct coupling clutch of the fluid transmission device. The characteristic is to smoothly absorb the torque difference between the drive plate and the driven plate connected via the buffer member,
It is required to reduce the torsional rigidity of the drive plate and the driven plate and to increase the torsional angle.

A conventionally used damper mechanism is provided by arranging two types of springs in series on the same circumference on the outer peripheral side of a driven plate, and the characteristics of this conventional damper mechanism are shown by the broken line ( As shown in a), when the load is low (torque -b to C), a spring with a small spring constant is operated to cope with the torsion angle -d to e, and when the load is high (torque -f<-b, C< 1ll), a spring with a large spring constant is activated at the same time to adjust the torsion angle -h<-d, e<
i was set up to deal with it.

[Problems to be Solved by the Invention] However, with the increase in engine output in recent years, there is a demand for increasing the range of torque fluctuations that damper mechanisms can absorb. The range of torsion angle between the connected drive plate and driven plate is small, and the range in which torque can be absorbed is limited to a narrow range.

An object of the present invention is to provide a direct coupling clutch for a fluid transmission device that can increase the range of torque capacity that can be absorbed without increasing the diameter of the damper mechanism.

[Means for Solving the Problems] In order to solve the above problems, the direct coupling clutch of the fluid transmission device of the present invention includes a piston that removably engages with an input member of the fluid transmission device, and a piston that is connected to the piston. a first plate, the first plate and the first! i! A direct coupling clutch for a fluid transmission device comprising a second plate connected through a shock member, and a third plate connected to the second plate through a second buffer member and connected to an output member of the fluid transmission device. , the first plate holds the first buffer member and the second plate by sandwiching them from both sides.

[Operation and Effects of the Invention] In the direct coupling clutch of the fluid transmission device of the present invention having the above configuration, buffer members are provided on the outer periphery and the inner periphery, and the output transmitted from the piston is transmitted to the first plate and the first buffer member. Since the torque is transmitted in series to the output member via the second plate, the second buffer member, and the third plate, the torque capacity that can be absorbed can be increased without increasing the diameter of the damper mechanism. In addition, if the torque absorption capacity is the same as before,
The diameter of the damper mechanism can be reduced, and the direct coupling clutch can be made lighter and more compact.

(Effects of the Embodiment) The first plate is provided as a pair of plates, and the connecting position of the pair of plates is provided at the spline fitting portion connected to the piston by spline, thereby producing the following effects.

b) Since the circumferential length of the first loose VIJ part can be maximized, the stroke length of the first and second buffer members can be maximized, reducing the torsion of the damper mechanism. By increasing the angle, the torque capacity that can be absorbed can be increased.

Mouth) 1st! Since the circumferential length of the shock member can be maximized, the number of the 1aItr member and the second buffer member can be increased, and the maximum permissible limit per buffer member can be reduced. As a result, the diameter of the buffer member can be reduced, so the axial dimension of the damper mechanism can be shortened.

[Embodiment] Next, a direct coupling clutch of a fluid transmission device of the present invention will be described based on an embodiment shown in the drawings.

FIG. 1 shows a sectional view of a fluid transmission device with a direct coupling clutch to which the present invention is applied.

A fluid transmission device with a direct coupling clutch, which is a power transmission device for a vehicle automatic transmission, has a torque converter 1 and a direct coupling clutch 2.
It consists of a power transmission case 11 which is a case of the torque converter 1, and a fluid transmission part 12 that transmits power by interposing fluid (hydraulic oil) within the power transmission case 11. The direct coupling clutch 2 is disposed between the transmission case 11 and the fluid transmission section 12 and is driven by a hydraulic oil supply means 13 .

The torque converter 1 is disposed in a torque converter case 31 between an engine (not shown) and a transmission mechanism (not shown), and is located at the rear of the torque converter case 31 (on the right side in the figure).
A transmission case 32 in which a transmission mechanism is installed
are fastened, and an oil pump housing 33 is connected between the torque converter case 31 and the transmission case 32.
It is separated by walls.

The power transmission case 11 is connected to a crankshaft of an engine (not shown) via a starter wheel, and includes a front cover 111 that includes a direct coupling clutch 2 therein, and a fluid transmission section welded to the inner circumference of the front cover 111. 1
2, and a pump drive sleeve 113 provided around the inner wall of the rear cover 112.
The rear end of 3 is connected to the interior of a cylindrical portion 331A that protrudes from the front of an oil pump cover 331 fastened between the torque converter case 31 and the transmission case 32, a metal bearing 130^, and an oil seal 130.
The oil pump cover 3 is rotatably installed inside via B.
In order to drive the external gear 51 of the internal gear oil pump 5, which is provided with an external gear 51 and an internal gear 52, which are disposed in an oil pump housing 33 consisting of a 31 catcher cover 332, the internal gear 51 of the external gear 51 is The circumference is connected by splines.

The fluid transmission section 12 is integrally formed inside the rear cover 112, and corresponds to a pump impeller 121 that causes hydraulic oil to flow from the inner circumferential side to the outer circumferential side by centrifugal force by rotation of the rear cover 112, and the pump impeller 121. A turbine impeller 122 is provided with the pump impeller 121, and the pump impeller 121 receives the hydraulic oil that has flowed to the outer circumferential side and transmits the rotation of the pump impeller 121 by making the hydraulic oil flow to the inner circumferential side again. A stator 123 that changes the flow direction of hydraulic oil between the inner peripheral sides of the turbine impeller 122 and increases torque.
It consists of An outer race 1 of a one-way clutch 124 that can rotate in only one direction is provided on the inner periphery of the stator 123.
248, and the inner race 124B of the one-way clutch 124 is spline-fitted with the outer circumference of the front end of the fixed sleeve 125 connected to the rear cover 332 of the oil pump housing 33 which is connected to the transmission case 32, and passes through the stator 123. It is provided so that it can rotate only in one direction depending on the direction of the flow of hydraulic oil.

Further, the turbine flange 122A supporting the turbine impeller 122 is centered with the output shaft 126, which is the output member of the torque converter 1, which is disposed via metal bearings 130C, 1300 at the front and rear ends of the inner circumference of the fixed sleeve 125. The outer periphery flange 127A of the output shaft connection hub 127 whose side is spline-connected and the inner periphery of the fourth guide plate 27B of the third plate 21 extending downward are fixedly connected by rivets 128.

The direct coupling clutch 2 is disposed between the front cover 111 of the power transmission case 11 and the turbine impeller 122 of the fluid transmission unit 12, and includes an inner cylindrical portion 211 and an outer cylindrical portion 212.
, the front cover 11 of the power transmission case 11, which is an input member of the torque converter 1, is composed of an annular plate portion 213.
1 and IIIR, a disc-shaped piston 21 that can be freely engaged with the piston 21, and a damper mechanism 22 that absorbs the impact when lock-up engagement occurs.
It consists of The inner cylindrical portion 211 of the piston 21 is inserted into the annular recess 127B of the output shaft connection hub 127 with the seal ring 1.
27C so that it is slidable in the axial direction. The annular plate portion 213 has an outer circumferential side formed as a flat ring-shaped lock-up engagement surface 213A corresponding to a friction material 21A provided inside the front cover 111 that increases frictional force during lock-up engagement, and an outer circumferential cylindrical portion. 212 is a spline 212 which is a plurality of notches that open rearward.
is formed.

As shown in FIG. 2, the damper mechanism 22 is connected to the piston 21 and has a part of the first buffer member 23 made of a compression coil spring with a small spring constant and a large stroke length on the outer circumferential side. The first slidably held
A first plate 24 consisting of a guide plate 24A and a second guide plate 24B is slidably sandwiched in the circumferential direction between the first guide plate 24A and the second guide plate 24B of the first plate 24, and a second plate connected to the first plate 24 via the first buffer member 23;
A third guide plate 27^ that slidably holds the plate 25 and a second buffer member 26 made of a compression coil spring with a large spring constant and a small stroke length in the circumferential direction.
and a fourth guide plate 27B, the second plate 25 is slidably held in the circumferential direction by the third guide plate 27A and the fourth guide plate 27B, and the second plate 25 is held via the second buffer member 26. 25, a spline fitting part 242 is provided on the outer periphery of the first plate 24 to be spline fitted with the spline 212A of the piston 21, and the first guide plate of the first plate 24 is 24A and the second guide plate 24B are fixed to each other by a plurality of rivets 241 on the outer peripheral side of the first buffer member 23. The third guide plate 27A and the fourth guide plate 28B of the third plate 27 are
The second plate 25 held between the buffer members 26 is fixed with rivets 271 so that it can slide. The sliding range (torsion angle) between the first plate 24 and the second plate 25 is between -β and γ, and the sliding range between the second plate 25 and the third plate 27 is between δ and ε. By setting the spring constants of the first buffer member 23 and the second buffer member 26, the torsion angle between the first plate 24 and the second plate 25 is set to 1 δ or less or γ or more. The second plate 25 and the third plate 27 are provided to start sliding.

The hydraulic oil supply means 13 includes an oil passage 131 formed in the rear cover 332 of the oil pump housing 33;
Oil passage 1 formed in fixed sleeve 125 corresponding to 31
32. Oil passage 1 formed between metal bearing 130C11300 between output shaft 126 and fixed sleeve 125
33, an oil passage 135 communicating with the oil passage 133 via the oil passage 134 and formed at the axial center of the output shaft 126;
A first oil passage 13A consisting of an oil passage 136 formed by the front cover 111 and the gate of the piston 21, and an oil bone aperture of the oil pump housing 33 communicating between the pump drive sleeve 113 and the fixed sleeve 125. An oil passage (not shown) formed in the cover 331, an oil passage 137 formed between the pump drive sleeve 113 and the fixed sleeve 125, communicating with the oil passage 137, and the pump drive sleeve 1
13 and the one-way latch 124, and stator 1.
23 and the pump impeller 121, a second oil passage 13B consisting of an oil passage 138 communicating with the first oil passage 1 is formed.
Switching of the supply direction of the hydraulic oil between the hydraulic oil passages 3A and 13B is performed by a hydraulic control device (not shown), and when one side is selected and connected to the hydraulic power source, the hydraulic oil is discharged from the other side.

Next, the operation of the fluid transmission device having the above configuration will be explained.

When the hydraulic control device is not set to a lock-up state.

The hydraulic oil supply means 13 supplies hydraulic oil from a hydraulic source to the first oil path 1.
It is set to form a circulation passage that fills the inside of the power transmission case 11 through the oil passage 3A and discharges hydraulic oil from the second oil passage 13B.

Since hydraulic oil is supplied into the power transmission case 11 through the space between the front cover 111 and the piston 21, the friction material 21A fixed to the front cover 111 and the lock-up engagement surface 213^ of the piston 21 are hydraulically connected. They are pulled apart by the difference, and the frictional engagement surface between them is released, and the hydraulic fluid flows between the friction material 21A and the lockup engagement surface 213A, fills the inside of the power transmission case 11, and circulates through the fluid transmission part 12. It is discharged through the second oil passage 13B. At this time, from the crankshaft to the starter wheel, power transmission case 1
1 to the pump impeller 121 is transmitted to the turbine impeller 122 by fluid transmission of hydraulic oil circulating within the fluid transmission section 12. Therefore, rotational torque based only on the action of the torque converter of the fluid transmission section 12 is output to the output shaft 126, and the direct coupling clutch 2 does not transmit torque.

When the hydraulic control device is set to a lock-up state.

The hydraulic oil supply means 13 supplies hydraulic oil from a hydraulic source to the second oil path 1.
It is set to form a circulation passage that fills the inside of the power transmission case 11 via 3B and discharges hydraulic oil from the first oil passage 13A.

Hydraulic oil is supplied into the power transmission case 11 through the fluid transmission unit 1.
Since this is carried out from the 2nd side, the pressure inside the power transmission case 11 becomes higher than the filling pressure of the hydraulic oil, and the front cover 11
1 and the piston 21 is discharged from the first oil passage 13A, the friction material 21A provided on the front cover 111 and the piston 21's
A is compressed and engaged by the filling pressure of the hydraulic oil in the power transmission case 11, and as a result, the output transmitted from the crankshaft to the power transmission case 11 via the starter wheel is transmitted to the FJ friction material 21A1 piston 21, The rotation output of the engine is transmitted to the output shaft 126 via the damper mechanism 22 and the output shaft connection hub 127, thereby directly transmitting the rotational output of the engine to the output shaft 126.

Next, the characteristics of the damper mechanism will be explained using the solid line (α) in FIG.

The engine is driven to rotate in the direction of the arrow in FIG. When the torsion angle of the first plate 24 and the second plate 25 when no stress is applied to the first plate 24 and the third plate 27 and the torsion angle of the first plate 24 and the second plate 25 are in the range of −β to γ. The torsion angle of the second plate 25 and third plate 27 is O. Here, when the rotational torque received by the first plate 24 is larger than the rotational torque of the third plate 27, such as during lock-up engagement, the biasing force of the first buffer member 23 having a small spring constant is reduced from the torque difference O to the torque difference in this range. The torsion angle is from 0 to γ, and in the range from the torque difference ζ to the torque difference η, which is larger than the torque difference ζ, the 211i1 member 26 with a large spring constant is biased by the second plate 25 and twisted. Deal with it within the range of angle γ to ε. For example, when the rotational torque received by the third plate 27 is larger than the rotational torque of the first plate 24, such as when the engine speed decreases while the vehicle is in a lock-up engaged state while the vehicle is running, in the range from torque difference O to torque difference O. , the torsion angle O to -0 is handled by the biasing force of the first buffer member 23 with a small spring constant, and in the range from torque difference B to a torque difference larger than torque difference O, the first buffer member 23 with a large spring constant 2 [The biasing force of the i member 26 is used to deal with the twist angle within the range of -β to -δ.

In the above embodiment, the second plate is formed of one plate, and the third plate is held by sandwiching the 21st plate and the 2nd plate from both sides, but the second plate is the 21st plate. The impact member and the third plate may be provided so as to be sandwiched and held from both sides.

In the above embodiment, the connection position of the first plate is set to 1! Although an example has been shown in which they are provided at 1' and 1 of the first shock absorbing members, they may also be provided between the first shock absorbing members lυ and at the inner peripheral position of the first shock absorbing members.

In the above embodiment, an example was shown in which the pair of plates forming the first plate were connected by rivets, but other connecting means such as fastening with bolts and nuts, welding, etc. may be used.

In the above embodiment, an example was shown in which the first plate was formed from a pair of plates, but it is also possible to form the first plate from a single press-formed product, for example, with a bent portion on the outer or inner periphery of the first plate. may be provided so as to sandwich the first buffer member and the second plate.

In the above embodiment, an example was shown in which a torque converter was applied to a fluid transmission device, but the present invention may also be applied to other fluid transmission devices such as a fluid coupling.

In the above embodiment, compression coil springs are used as the first and second buffer members, but other buffer members such as leaf springs, tension coil springs, and rubber members may also be used. good. In addition, there are various types of springs, such as dual coil springs with a compression coil spring inside a compression coil spring, and a combination of a compression coil spring and a rubber member. 1Ili members may be used in combination.

[Brief explanation of drawings]

Fig. 1 is a side sectional view of a fluid transmission device with a direct coupling clutch to which the direct coupling clutch of the fluid transmission device of the present invention is applied, Fig. 2 is a front view of the damper mechanism, and Fig. 3 shows a drive plate and a driven plate on the horizontal axis. Torsion angle is shown on the vertical axis, torque is shown on the vertical axis,
It is a graph showing the characteristics of the damper mechanism of the present invention and the conventional damper mechanism. In the diagram 1... Torque converter 2... Direct clutch 11... Power transmission case 21... Piston
22... Damper mechanism 23... First buffer member 24
...First plate 25...Second plate 26...
-Second buffer member 27...Third plate 126...
・Output shaft 127...Output shaft connection hub

Claims (1)

[Scope of Claims] 1) a piston that removably engages with an input member of a fluid transmission device, a first plate that connects with the piston, and a first plate that connects with the piston;
A fluid transmission device comprising: a second plate connected to the plate via a first buffer member; and a third plate connected to the second plate via the second buffer member and connected to an output member of the fluid transmission device. In the direct coupling clutch, the first plate is connected to the first buffer member and the second buffer member.
A direct coupling clutch for a fluid transmission device, characterized by a plate held by sandwiching it from both sides. 2) A direct coupling clutch for a fluid transmission device according to claim 1, wherein the first plate is a pair of plates connected to each other. 3) A direct coupling clutch for a fluid transmission device according to claim 2, wherein the pair of plates forming the first plate are connected at an outer peripheral position of the first buffer member. 4) Claim 1, wherein the first plate is spline-fitted to the piston at its outer peripheral portion.
A direct coupling clutch for a fluid transmission device according to any one of items 1 to 3. 5) A direct coupling clutch for a fluid power transmission device according to claim 4, wherein the connecting position for connecting the first plate is provided at a spline fitting portion that connects the piston with a spline. 6) The direct coupling clutch for a fluid transmission device according to claim 1, wherein the third plate holds the second buffer member and the second plate by sandwiching them from both sides. 7) A direct coupling clutch for a fluid transmission device according to claim 6, wherein the third plate is a pair of plates connected to each other. 8) A direct coupling clutch for a fluid transmission device according to claim 7, wherein the pair of plates forming the third plate are connected between the second buffer members.