JPS61252962A - Directly-coupled clutch for hydraulic transmission - Google Patents

Abstract

PURPOSE:To shorten the dimension of damper mechanism in axial direction by holding two groups of buffer members between two plates then securing two plates between outer and inner circumference buffer members. CONSTITUTION:Outer and inner circumference buffer members 23, 24 are held between first and second guide plates 25, 26 which are secured through ribet 29 approximately in central position between said members 23, 24 in circumferential direction. Consequently, the outer circumference buffer member 23 can be arranged to the outermost circumference of damper mechanism 22 while sufficient arranging position of inner circumference buffer member 24 can be ensured resulting in increase of the arranging number of said members 23, 24. As a result, allowance per single buffer member can be reduced thus to shorten the axial dimension of 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] An input member that receives the output of an engine mounted on a vehicle and is removably engaged with an input member of a fluid transmission device that is connected via fluid between an input member that inputs the output of an engine mounted on a vehicle and an output member that outputs output to a transmission mechanism. A buffer member for a direct coupling clutch of a fluid transmission device, which includes a piston, a drive plate connected to the piston, and a tamper mechanism including a driven plate connected to an output member of the fluid transmission device connected to the drive plate via a buffer member. is held between two plates. The plate that holds these two buffer members had the risk that the buffer member held inside would push the plates apart due to centrifugal force and pop out to the outer periphery, so in order to prevent the plates from opening, Provide a fixing means,
This prevented the shock absorber from popping out.

[Problems to be solved by the invention] A buffer member used in a direct coupling clutch of a fluid transmission device is
In order to shorten the fluid transmission device in the axial direction and improve its durability, it is advantageous to provide a large number of buffer members, reduce the permissible amount per buffer member, and achieve compactness. As shown in <mw, since the fixing means was provided at the outer periphery of the member, the circumferential length for arranging the buffer member was shortened by the space for providing the fixing means on the outer periphery of the buffer member, and the space for arranging the buffer member was reduced. In addition, in order to increase the range of torque fluctuations that can be absorbed by the damper mechanism due to the increase in the output of engines in recent years, a damper mechanism in which a buffer member is provided on the outer circumference of the fluid transmission device and the inner circumference thereof has been proposed.
(USP 4.138.003, USP 4,347,
717, Japanese Unexamined Patent Publication No. 57-195957). These outer and inner buffer members are provided with fixing means on the outer circumference of the outer buffer member to prevent the outer buffer member from popping out, and the inner buffer member is held in place by centrifugal force. Since there is a risk that the buffer member may fly out from the holding chamber, a fixing means is also provided on the outer periphery of the buffer member on the inner periphery side. Therefore, the space for arranging the buffer members is restricted, making it difficult to increase the number of buffer members, make the buffer members more compact, and make the damper mechanism more compact. Moreover, the number of fixing means for the damper mechanism increases, resulting in a problem that the structure becomes complicated.

SUMMARY OF THE INVENTION An object of the present invention is to provide a direct coupling clutch for a fluid transmission device in which the range of the torsion angle of the damper mechanism can be widened and the dimensions of the damper mechanism in each direction can be reduced.

[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 drive plate; two groups of buffer members disposed concentrically on an outer periphery and an inner periphery; drivingly connected to the drive plate via the two groups of buffer members, and coupled to an output member of the fluid transmission device; In a direct coupling clutch of a fluid transmission device comprising a damper mechanism consisting of driven plates, the two groups of buffer members are sandwiched between two plates, and the two plates are placed between the outer circumferential 1117 member and the inner circumferential buffer member. It is assumed that it is fixed in place.

[Operations and Effects of the Invention] The direct coupling clutch of the fluid transmission device of the present invention having the above configuration has two groups of buffer members sandwiched between two plates, and the two plates are placed between the outer circumferential buffer member and the inner circumferential buffer member. By fixing the outer circumferential buffer member at the outer circumference, the outer circumferential shock absorbing member can be disposed up to the outermost periphery of the damper mechanism, and the inner circumferential shock absorbing member can be disposed at a position that eliminates the space for disposing the fixing means at the outer circumferential position of the outer circumferential shock absorbing member. As a result, the number of outer and inner circumference mw members can be increased, and the allowable amount per buffer member can be reduced, which allows the diameter of the buffer member to be reduced. The axial dimension of the damper mechanism can be shortened. Since the stroke length of the buffer member can be increased by increasing the space for arranging the outer and inner buffer members, it is easy to increase the torsion angle of the damper mechanism and increase the torque range that can be absorbed. Since the outer and inner buffer members can be prevented from popping out from the two plates by the fixing means provided between the outer and inner buffer members, the number of fixing means can be reduced. Since the structure is simplified, the productivity of the damper mechanism can be increased.

[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.

Direct-coupled clutch, which is a power transmission device for a vehicle automatic transmission.The fluid transmission device consists of a torque converter 1 and a direct-coupled 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 the crankshaft 41 of the engine via the starter wheel 42, and includes a front cover 111 that includes the direct coupling clutch 2 therein, and a fluid transmission section welded to the inner periphery of the front cover 111. 12
The pump drive sleeve 113 is composed of an annular plate-shaped rear cover 112 containing the rear cover 112 and a pump drive sleeve 113 provided around the inner wall of the rear cover 112.
The rear end is connected to the inside of a cylindrical portion 331A protruding from the front of an oil pump cover 331 fastened between the torque converter case 31 and the transmission case 32, a metal bearing 130A, and an oil seal 130B.
The oil pump cover 33 is rotatably installed inside the oil pump cover 33.
In order to drive the external gear 51 of the internal gear oil pump 5, which includes an external gear b1 and an internal gear 52, which are disposed in the oil pump housing 33 consisting of a catcher cover 332, It is connected to the circumference by a spline.

The fluid transmission unit 12 is integrally formed inside the rear cover 112, and includes a pump and an impeller 121 that causes hydraulic oil to flow from the inner circumferential side to the outer circumferential side by centrifugal force as the rear cover 112 rotates.
The rotation of the ribbon impeller 121 is transmitted by receiving the hydraulic oil that the pump impeller 121 has caused to flow toward the outer circumference and causing it to flow toward the inner circumference again. A stator 123 that changes the flow direction of hydraulic oil between the turbine impeller 122 and the inner peripheral sides of the pump impeller 121 and the turbine impeller 122 to increase torque.
It consists of The inner periphery of the stator 123 is connected to an outer race 124A of a one-way clutch 124 that can rotate in only one direction, and an inner race 124B of the one-way clutch 124 is connected to a rear cover 332 of the oil pump housing 33 that is connected to the transmission case 32.
The stator sleeve 125 is spline-fitted to the front end outer periphery of the fixed sleeve 125 connected to the stator 123, and is provided to rotate only in one direction depending on the flow direction of the hydraulic oil passing through the stator 123. Further, the turbine 2 flange 122A that supports the turbine impeller 122 is connected to the output shaft 122, which is the output member of the torque converter 1, which is disposed at the front and rear ends of the inner circumference of the fixed sleeve 125 via metal bearings 130C11300.
and an output shaft connection hub 127 whose center side is spline-connected.
The outer periphery flange 127^ and the inner periphery of the second guide plate 26 of the direct coupling clutch 2 described above are fixedly connected by rivets 128.

The direct coupling clutch 2, as shown in FIGS. 2 and 3,
Arranged between the front cover 111 of the power transmission case 11 and the turbine impeller 122 of the fluid transmission section 12, the inner circumferential side cylindrical part 211, the outer circumferential side cylindrical part 212, and the annular plate part 213
A disk-shaped piston 21 is removably engaged with the front cover 111 of the power transmission case 11, which is an input member of the torque converter 1, and an impact during lock-up engagement shown in FIGS. 4 and 5. Damper mechanism 2 that absorbs
It consists of 2. The inner cylindrical portion 211 of the piston 21 is externally fitted into the annular recess 127B of the output shaft connection hub 127 via a seal ring 127C so as to be slidable in the axial direction.

The outer J'ffl side of the annular plate part 213 is the front cover 1
The lock-up engagement surface 213A is formed as a flat ring-shaped lock-up engagement surface 213A corresponding to the friction material 21A provided inside the lock-up engagement surface 21A that increases the friction force during lock-up engagement, and the outer circumferential side cylindrical portion 212 has a plurality of notches opening rearward. A spline 212A is formed.

The damper mechanism 22 includes two groups of outer periphery buffer members 23 consisting of compression coil springs with a small spring constant and a large stroke length on the outer periphery side, and compression coils with a large spring constant and a small stroke length on the inner periphery of the outer periphery buffer members 23. From FIG. 6 to FIG. 9, an outer circumferential buffer member holding chamber 23A and an inner circumferential m-plane member holding chamber 24A, which contain a part of the inner circumferential buffer member 24 made of a spring and hold it slidably in the circumferential direction, are formed. Also shown is the first outer circumference buffer member holding frame 25A and the first inner circumference! ! A first guide plate 25 equipped with an impact member holding frame 25B, a second
As shown in FIGS. 10 and 11, the trian plate 27 includes a second guide plate 26 having an outer buffer member holding frame 26A and a second inner buffer member holding frame 26B, and as shown in FIGS. 212 splines 212
It has a spline 281 that is spline-fitted with A, and is held slidably in the circumferential direction between the first guide plate 25 and the second guide plate 26 of the outer periphery buffer member holding chamber 23A, and the outer periphery Wi It has an outer buffer member biasing window 282 in which the member 23 is disposed and urges the outer buffer member 23 by sliding of the driven plate 27, and an inner buffer member that biases the inner buffer member 24 on the inner periphery. The first inner buffer member holding frame 25B of the first guide plate 25, which is composed of a drive plate 28 having a push-in protrusion 283 and forms the inner buffer member holding chamber 24A, is provided with an opening in the clockwise direction of rotation in the figure. A circumferential buffer member 24 is provided so as to partially protrude, and the circumferential sliding range (torsion angle) of the driven plate 27 and drive plate 28 is between -β and γ, and the torsion angle δ and γ are between -β and γ. An inner buffer member biasing protrusion 283 is provided between the inner buffer member holding chamber 24^ to press the inner buffer member 24 protruding from the inner buffer member holding chamber 24^, and the first guide plate 25 and the second guide plate 26 Member 23 and inner peripheral buffer member 2
The first guide plate 25 and the second guide plate 2 are fixed to each other by a rivet 29 at approximately the center of the outer buffer member 23 and the inner buffer member 24 in the circumferential direction, which is the middle part of the outer buffer member 23 and the inner buffer member 24.
6 from opening, and prevents the outer buffer member 23 and the inner buffer member 24 from jumping out from the outer buffer member holding chamber 23A and the inner buffer member holding chamber 24^. A spline 281 formed on the outer periphery of the drive plate 28
is located approximately at the center of the outer peripheral buffer member 23, and the piston 2
The spline 212A of the outer peripheral side cylindrical portion 212 is formed to correspond to the spline 281 of the drive plate 28.

Further, the second guide plate 26 of the driven plate 27 has an inner circumference connected to the output shaft connection hub 127 as described above.

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 bearings 130C and 1300 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 between the front cover 111 and the piston 21 and an oil pump cover of the oil pump housing 33 communicating with the pump drive sleeve 113 and the fixed sleeve 125. 331, an oil passage 137 formed between the pump drive sleeve 113 and the fixed sleeve 125, which communicates with the oil passage 137, and the pump drive sleeve 1.
13 and the one-way clutch 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 snowmaking device constructed as described above 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, there is a hydraulic pressure difference between the friction material 21A fixed to the front cover 111 and the lock-up engagement surface 213A of the piston 21. The frictional engagement surface between the two is released, and the hydraulic fluid flows between the friction material 21A and the lockup engagement surface 213A, filling the power transmission case 11, circulating through the fluid transmission part 12, and releasing the frictional engagement surface between the two. 2 oil passage 13B. At this time, the output input from the crankshaft 41 to the pump impeller 121 via the starter wheel 42 and the power transmission case 11 is transmitted to the turbine impeller 122 by fluid transmission of the 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 side a 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 lock-up engagement surface 213A of the piston 21
are 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 41 to the power transmission case 11 via the starter wheel 42 is transmitted to the friction material 21^, the piston 21, damper mechanism 2
2 and the output shaft connection hub 127 to the output shaft 126, whereby the rotational output of the engine is transmitted to the output shaft 126 through the output shaft connection hub 127.
6.

Next, the characteristics of the damper mechanism will be explained using the solid line (α) in FIGS. 4 and 12.

The engine is driven to rotate in six directions indicated by arrows in FIG. The position (torsion angle) of the drive plate 28 and the driven plate 27 where no stress is applied to the drive plate 28 and the driven plate 27 is O. Here, for example, during lock-up engagement, the drive plate 28
When the rotational torque of the driven plate 27 is larger than the rotational torque of the driven plate 27, in the range of torque difference 0 to torque difference ε, the torsion angle O is reduced by the biasing force of the outer peripheral buffer member 23 having a small spring constant.
In this range, the inner buffer member 24 with a large spring constant urges the inner buffer member biasing protrusion 283 of the drive plate 28. Then, the outer circumference buffer member 23 and the inner circumference 1111i member 24 are operated simultaneously to cope with the torsion angle within the range of δ to γ. Also, for example, when the engine speed decreases while the A-Tsukaku knob is engaged while the vehicle is running,
When the rotational torque of the driven plate 21 is larger than the rotational torque of the drive plate 28, the range of torque difference from 0 to torque difference η, and the torsion angle from O to −β are dealt with only by the biasing force of the outer peripheral buffer member 23 with a small spring constant. .

A second embodiment of the present invention is shown in FIGS. 13, 14, and 15.

The damper mechanism 22a of this embodiment has a group of outer periphery buffer members 23a made of compression coil springs with a small spring constant and a large stroke length on the outer periphery side, which are held together with the inner periphery of the outer cylindrical portion 212 of the piston 21. A member holding chamber 23Aa is formed on the inner periphery of the outer M cylinder member 23a to form an inner buffer member holding chamber 24^a that holds a group of inner buffer members 24a made of compression coil springs with a large spring constant and a small stroke length. First outer peripheral buffer member holding frame 2
5Aa and a first inner peripheral buffer member holding frame 25Ba,
A spline fitting portion 25C corresponding to the spline 1270a provided on the outer periphery of the output shaft connection hub 127 on the inner periphery.
The first guide plate 25a1 in which a is formed, the second outer circumferential buffer member holding frame 26Aa, and the second inner circumferential buffer member holding frame 2
It consists of a second guide plate 26a equipped with 6Ba. The first guide plate 25a and the second guide plate 26a are fixed with rivets 29a in the circumferential direction at an intermediate portion between the outer circumferential buffer member 23a and the inner circumferential buffer member 24a, and the first guide plate 25a and the second guide plate 26a are Driven plate 27a that prevents opening and prevents outer buffer member 23a and inner buffer member 24a from jumping out of outer buffer member holding chamber 23Aa and inner buffer member holding chamber 24Aa.
It is held slidably in the circumferential direction between the first guide plate 25a and the second guide plate 26a of the outer circumferential buffer member holding chamber 23^a section, and the outer circumferential buffer member 23a is disposed inside and the outer circumferential m cylinder. The member 23a is connected to the driven plate 27a.
The drive plate 28a has an outer buffer member biasing frame 282a that biases the inner buffer member 24a by sliding, and a drive plate 28a that has an inner buffer member biasing protrusion 283a on the inner periphery that biases the inner buffer member 24a. Member biasing protrusion 283a and piston 21
are fixed by rivets 30a, and the piston 21 and drive plate 28a are connected. First guide plate 25a forming inner peripheral buffer member holding chamber 24Aa
The first inner periphery m1lj member holding frame 25Ba is opened in the left rotation direction in the figure and is provided so that the inner periphery buffer member 24a partially protrudes, and the inner periphery buffer member biasing protrusion 283a is connected to the inner periphery buffer member holding chamber 24Aa. It is provided so as to press the inner circumferential buffer member 24a that protrudes further. Also, the driven plate 27a
The spline fitting portion 25Ca on the inner circumference of the first guide plate 25a is connected to the spline 127Da of the output shaft connection hub 127 so that the damper mechanism 22a can be slid in the axial direction.
are connected by splines.

FIG. 14 shows a third embodiment of the present invention.

The damper mechanism 22t) includes a spline 21 of the piston 21.
The outer periphery 11 connected to 2^ and provided inside! A drive plate 28b has an outer buffer member 23b disposed inside the i-member biasing window 282b, and a part of the outer buffer member 23b, which is made of a compression coil spring with a small spring constant and a large stroke length, is arranged in the circumferential direction. A first guide plate 25b that slidably holds an inner peripheral buffer member 24b made of a compression coil spring with a large spring constant and a small stroke length on its inner peripheral side so as to be slidable in the circumferential direction.
and a second guide plate 26b, and the outer peripheral buffer member 2
3b and inner circumference II! A plate 20b is fixed with a rivet 29b at the middle part of the member iiib and holds the outer periphery 111 member 23b and the inner periphery buffer member 24b, and an inner periphery buffer whose inner periphery is connected to the output shaft connection hub 127 and provided inside. The driven plate 27b has an inner buffer member 24b disposed within the member biasing window 283b, and the power transmitted to the piston 21 is transmitted to the drive plate 28b connected to the piston 21, and then to the drive plate 28b. The generated power is transmitted to the outer buffer member 23b via the outer buffer member biasing window 282b, and the power transmitted to the outer buffer member @23b is transmitted to the inner buffer member 24b via the plate 20b, and the power is transferred to the inner buffer member 24b via the plate 20b. The power transmitted to the member 24b is transmitted to the driven plate 27b via the inner buffer member biasing window 283b, and the power transmitted to the driven plate 27b is transmitted to the output shaft 12 via the output shaft connection hub 127.
6.

Although the above embodiment shows an example in which a torque converter is applied to a fluid transmission device, it may be applied to other fluid transmission devices such as a fluid coupling (fluid coupling).

Although the above embodiment shows an example in which compression coil springs are applied to the outer and inner buffer members, other buffer members such as leaf springs, tension coil springs, rubber members, etc. may also be used. . Further, various shock absorbing members may be used in combination, such as a dual coil spring in which a compression coil spring is disposed within a compression coil spring, or a combination of a compression coil spring and a rubber member.

In the above embodiment, an example is shown in which rivets are used as means for fixing the pair of plates, but other fixing means may be used, such as fixing by fastening bolts and nuts, fixing by a joining method such as welding.

[Brief explanation of drawings]

Fig. 1 is a side sectional view of a fluid transmission device with a direct coupling clutch according to a first embodiment 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 piston, and Fig. 3 is a side sectional view of the piston. 4 is a front view of the damper mechanism, FIG. 5 is a sectional view of the damper mechanism shown in FIG. 4 taken along line I-I, FIG. 6 is a front view of the first guide plate, and FIG. A cross-sectional view along the line ■-■ of the first guide plate shown in Fig. 6, No. 8
The figure is a front view of the second guide plate, FIG. 9 is a sectional view of the second guide plate shown in FIG.
The figure is a front view of the drive plate, Figure 11 is a cross-sectional view of the drive plate shown in Figure 10 along the line ■-■,
The figure shows the torsion angle between the drive plate and the driven plate on the horizontal axis, and the torque on the vertical axis, and is a graph representing the characteristics of the damper mechanism according to the first embodiment of the present invention. 14 is a front view of the damper mechanism shown in FIG. 13, and FIG. 15 is a sectional view taken along line v-v of the damper mechanism shown in FIG. FIG. 16 is a side sectional view of a fluid transmission device with a direct coupling clutch according to a third embodiment of the present invention. In the figure: 1... Torque converter 2... Direct clutch 11... Power transmission case 20b... Plate 21... Pistons 22.22a, 22b -.
- Damper mechanism 23.23a, 23b--Outer buffer member 24.24a, 24b--Inner buffer member 25.25a, 25b--First guide plate 26.26a, 26b--Second guide plate 27.27a, 27b--Driven plate 28.28a, 28b--Drive plate 29.29a, 29b...Rivet 126-
...Output shaft 127...Output shaft connection hub Fig. 3 Fig. 2

Claims (1)

[Scope of Claims] 1) A piston that removably engages with an input member of a fluid transmission device, a drive plate that is connected to the piston, and two groups of buffer members that are concentrically arranged on the outer and inner peripheries. , a direct coupling clutch for a fluid transmission device comprising a damper mechanism including a driven plate drivingly connected to the drive plate via the two groups of buffer members and connected to an output member of the fluid transmission device; A direct coupling clutch for a fluid transmission device, characterized in that the buffer member is sandwiched between two plates, and the two plates are fixed between the outer circumferential buffer member and the inner circumferential buffer member. 2) A direct coupling clutch for a fluid transmission device according to claim 1, wherein said two plates are said driven plates. 3) A direct coupling clutch for a fluid transmission device according to claim 1, wherein the fixation is provided at a central portion of the inner peripheral buffer member. 4) Claim 1 or 2, characterized in that the fixation is provided at a central portion of the outer periphery buffer member.
A direct coupling clutch for the fluid transmission device described in Section 1.