JP4729366B2 - Double hydraulic clutch device for multi-stage automatic transmission - Google Patents

Description

The present invention relates to a vehicular automatic transmission, and more particularly to a dual hydraulic clutch device used in a multi-speed automatic transmission with 6 forward speeds and 1 reverse speed.

As is well known, an automatic transmission comprises a planetary gear train and a plurality of clutches and brakes that control its components. 2. Description of the Related Art In today's most widespread automatic transmissions using 4th forward speed and 1st reverse speed, a system having two planetary gear trains, three clutches and two brakes is often used.

In recent years, there has been a strong demand for fuel efficiency in automobiles due to global environmental problems, and automatic transmissions with multiple stages of 6 forward speeds and 1 reverse speed have been put into practical use. As a simple gear train of 6 forward speeds and 1 reverse speed, selectively input decelerated rotation and non-decelerated rotation to 3 components of 2 planetary gear trains with 4 components. There has been devised a simple automatic forward 6-speed reverse vehicle 1-speed vehicular transmission in which a brake is arranged on each component and the remaining one component is output. Patent Document 1 in which reduced rotation is input to one component, and decelerated rotation is input to the other two components, and reduced rotation is input to two components, and the other one component Japanese Patent Application Laid-Open No. H11-33583, which inputs a negative deceleration rotation. Patent Document 1 has three planetary gear trains, two clutches, and three brakes. Patent Document 2 has three planetary gear trains, three clutches, and two brakes. Yes.

In an automatic transmission with four forward speeds and one reverse speed, one of the three clutches is dedicated to the reverse direction and is not fastened simultaneously with the other clutches. There is also an example used as a dual hydraulic clutch. On the other hand, in the case of an automatic transmission of 6 forward speeds and 1 reverse speed, in either case of two clutches or three clutches, any one of the clutches can be engaged or two can be engaged at the same time. Therefore, it is impossible to adopt a double piston system that is used in forward four speeds and reverse first speeds.

Patent Literature 3, Patent Literature 5, and Patent Literature 6 are disclosed as dual hydraulic clutch devices for a multi-stage automatic transmission having three planetary gear trains, two clutches, and three brakes. Patent Document 4 and Patent Document 7 disclose a double hydraulic clutch device including a planetary gear for reduction as a multi-stage automatic transmission having a planetary gear train, three clutches, and two brakes. Although these two hydraulic clutch devices other than Patent Document 7 have been devised to be compact, not only does it require two canceller plates and two return springs to form the centrifugal hydraulic canceller chamber of each piston, but also increases costs. There is also a limit to compactness. In Patent Document 7, there is one canceller plate and two return springs, but it has a double piston structure, and it is not a structure in which the engagement and disengagement of the two clutches can be controlled separately and accurately.

JP 52-149562 A JP-A-4-219553 JP-A-5-33816 JP2000-220705 JP 2003-42184 A JP 2004-205027 A JP 2004-508502 A

The first problem of the present invention is that the canceller plate and the return spring are one, and any one or two can be fastened simultaneously, and the simple and compact that can be controlled separately and accurately. And providing a double hydraulic clutch device.

A second problem of the present invention is that the two clutch friction members have the same shape and are suitable for a front-wheel drive forward 6-speed forward 1-speed multi-speed automatic transmission that can be disposed radially outside the planetary gear train. A hydraulic clutch device is provided.

The third problem of the present invention is to make each constituent member of the double hydraulic clutch into a press-molded product that is integrated from a flat plate so that it can be mass-produced.

The fourth object of the present invention is to devise the arrangement of the return spring of the hydraulic piston in the dual hydraulic clutch and to realize further compactness.

The present invention according to claim 1 is means for solving the first and second problems, and has a side wall that is integral with the input member, and one side of the cylindrical clutch cover that is open at one side. A spline is formed in the peripheral part, a fixing member is arranged in the center part in the axial direction of the spline, friction members of the hydraulic clutches C1 and C2 are arranged on both sides of the fixing member, and arranged on the cylindrical inner side of the clutch cover. And a push type hydraulic piston that presses the friction member of the hydraulic clutch C1 toward the opening of the clutch cover, and a side wall portion of the clutch cover. And a pull-type hydraulic piston that presses the friction member of the hydraulic clutch C2 through the flange from the opening of the clutch cover, and the hydraulic piston of the hydraulic clutch C1. A centrifugal hydraulic canceller chamber is formed between them, and an axially movable canceller plate is arranged on the opening side. The canceller plate and the hydraulic piston of the hydraulic clutch C2 pass through the clutch cover and the hydraulic piston of the hydraulic clutch C1. Then, a return spring is arranged that is connected at a constant distance and biases the hydraulic piston of the hydraulic clutch C1 and the canceller plate.

The present invention according to claim 2 has three clutches and two clutches disclosed in Patent Document 2 in which reduced rotation is input to two components and non-decelerated rotation is input to the other component. A multi-stage automatic transmission having a brake is a means for solving the second problem. The sun gear is disposed radially inward of the friction members of the hydraulic clutches C1 and C2 disposed on the cylindrical inner peripheral portion of the clutch cover. And a planetary gear train for reduction composed of a planetary carrier supporting the planetary pinion gear and a ring gear, and connecting the planetary carrier to the input member 1 pivotally supported by the transmission case, and the sun gear to the transmission case The output member of the hydraulic clutch C2, the output member of the hydraulic clutch C1, and the hub welded to the ring gear are arranged in the radial direction in order from the opening side of the clutch cover to the canceller plate. Provided with a connecting portion and extending member, the output member of the hydraulic clutches C2, was ligated hub for locking the friction members of the brake B2 for braking the output member.

The present invention according to claim 3 is means for solving the third problem, wherein the clutch cover, the two hydraulic pistons, and the canceller plate are formed by pressing from a flat plate, and the side wall radius of the clutch cover is obtained. The center of the direction is cylindrical and protrudes in the direction of the opening to provide a stepped step, the inner diameter is welded to the outer periphery of the input member 1, enters the outer periphery of the step along the clutch cover, and is movable in the axial direction. A hydraulic piston of the hydraulic clutch C1 that forms a working hydraulic chamber by arranging a sealing material between the stepped portion and the input member, and enters the inner periphery of the stepped portion along the clutch cover to be freely movable in the axial direction. A hydraulic piston of the hydraulic clutch C2 that forms a working hydraulic chamber by arranging a sealing material between the members, and enters the outer periphery of the step portion along the hydraulic piston of the hydraulic clutch C1 to be axially movable; Part with arranging the sealing material between and Nobezai the sidewall to the inner periphery of the hydraulic piston of the hydraulic clutches C1, provided canceller plate that forms a centrifugal hydraulic pressure canceller chamber of the inner peripheral atmosphere.

The present invention according to claim 4 is a means for solving the fourth problem, wherein the hydraulic oil pressure chambers 20 and 30 and the centrifugal hydraulic pressure canceller chamber 40 are symmetric with respect to the rotational center on the radially outer side. The hydraulic piston of the hydraulic clutch C2 and the canceller plate are provided with rivet holes on the side walls of the hydraulic clutch C2 and the canceller plate, and the central portion has a larger diameter than both ends and the axial length of the central portion is constant. Are tightened so that they are integrally connected at a fixed distance, and through holes serving as guides for stud pins are provided at several locations on the circumference that are the same positions as the stud pins of the hydraulic piston of the clutch cover and the hydraulic clutch C1, One end is in the outer peripheral direction and the other end is in the inner peripheral direction at the remaining position that is the same position as the stud pin of the hydraulic piston of the clutch cover and the hydraulic clutch C1. A cylindrical spring holder with a cylindrical outer peripheral portion is provided with a through hole serving as a guide, and the outer peripheral flange of the spring holder is inserted into the clutch cover and the hydraulic piston of the hydraulic clutch C1 so as to contact the hydraulic piston of the hydraulic clutch C1, and the spring A coiled return spring using a stud pin as a guide was disposed between the inner periphery of the holder and the canceller plate.

The present invention according to claim 5 is another means for solving the fourth problem, and is provided with a plurality of the same symmetrical with respect to the rotational centers on the radially outer sides of the working hydraulic chambers 20 and 30 and the centrifugal hydraulic canceller chamber 40. In the position, a circumferentially rectangular window hole is formed in the side wall of the hydraulic piston of the hydraulic clutch C2, and a window hole arranged in the hydraulic piston of the hydraulic clutch C2 on the side wall of the hydraulic piston of the clutch cover and the hydraulic clutch C1. A wide flat through hole is formed in the canceller plate, and a rod extending through the through flat hole of the hydraulic piston of the hydraulic clutch C1 and extending to the hydraulic piston of the hydraulic clutch C2 is formed integrally with the hydraulic piston of the hydraulic clutch C2. The canceller plate is connected at a fixed distance with a retaining ring and a constriction at the heel, and the hydraulic clutch C1 hydraulic pipe is connected to the centrifugal hydraulic canceller chamber. The platen-shaped return spring that urges the ton and the canceller plate is arranged, and the hydraulic piston and canceller plate of the hydraulic clutch C2 are guided by the guide plate with the flange of the canceller plate and the through hole of the clutch cover and the hydraulic piston of the hydraulic clutch C1. Arranged to move axially.

The present invention according to claim 6 is an incidental means for solving the second problem, and is fixed by one retaining ring groove and the retaining ring provided on the inner side in the axial center of the spline of the clutch cover. The fixing member is fitted with a spline of the clutch cover at the outer periphery, and has a retaining ring groove on the outer side in the central portion radial direction. From the difference between the spline inner diameter of the clutch cover and the retaining ring inner diameter of the fixing member, Reduced the inner diameter difference of the retaining ring

According to the first aspect of the present invention, a spline is formed on the cylindrical inner peripheral portion of the clutch cover, a fixing member is disposed at the axial center of the spline, and the friction members of the hydraulic clutches C1 and C2 are disposed on both sides of the fixing member. Therefore, the friction member can be shared and can be linearly arranged in the axial direction. Further, the hydraulic piston of the push type hydraulic clutch C1 and the hydraulic piston of the pull type hydraulic clutch C2 that form the working hydraulic chambers on both sides of the clutch cover side wall are arranged, and the hydraulic pressure arranged on the cylindrical inner side of the clutch cover. An axially movable canceller plate that forms a centrifugal hydraulic canceller chamber is arranged between the hydraulic piston of the clutch C1, and the hydraulic piston and canceller plate of the hydraulic clutch C2 arranged on the cylindrical outer side of the clutch cover are connected to the clutch cover. And a return spring for energizing the hydraulic piston of the hydraulic clutch C1 and the canceller plate is arranged through the hydraulic piston of the hydraulic clutch C1, and the centrifugal hydraulic pressure in the centrifugal hydraulic canceller chamber and the return spring are directly When acting on the hydraulic piston of the hydraulic clutch C1 To act also on the hydraulic piston of the hydraulic clutch C2 via the canceller plate. Therefore, normally, two canceller plates and return springs are required for two hydraulic pistons. In the present invention, only one of each is sufficient, and the operating hydraulic chambers of the two hydraulic pistons are located on both sides of the clutch cover side wall. Since it is provided independently, it is possible to engage any one or two at the same time, and a simple and compact double hydraulic clutch device that can be controlled separately and accurately is possible.

According to the second aspect of the present invention, since only one canceller plate and one return spring are required, the reduction planetary gear train and its connecting member and the output members of the hydraulic clutches C1 and C2 are provided as clutch covers. Multi-stage automatic transmission having three clutches and two brakes which can be arranged on the radially inner side of the friction members of the hydraulic clutches C1 and C2 arranged on the cylindrical inner peripheral portion It becomes possible to make it compact.

In the configuration according to claim 3, since the clutch cover, the two hydraulic pistons and the canceller plate are formed as a press-molded product integrated from a flat plate, and the three hydraulic chambers are configured as four press-formed products, Mass production is possible at low cost.

In the configuration according to claim 4, the stud cover penetrates the clutch cover and the hydraulic piston of the hydraulic clutch C1, and the hydraulic piston and the canceller plate of the hydraulic clutch C2 are integrally formed at a constant distance outward in the radial direction of the working hydraulic chamber. Because of the connection, the two hydraulic pistons and the canceller plate are prevented from rotating with respect to the clutch cover, and the hydraulic piston and the canceller plate of the hydraulic clutch C2 are connected via a spring holder inserted into the stud pin near the hydraulic piston of the hydraulic clutch C2. Since it is urged by the coiled return spring, it is not necessary to provide a space in the axial direction of the return spring, and the axial direction becomes more compact.

In the configuration according to claim 5, instead of the stud pin according to claim 4, a hook extending to the hydraulic piston of the hydraulic clutch C2 is integrally formed on the canceller plate, and the clutch cover and the hydraulic piston of the hydraulic clutch C1 are formed. A flat plate-like return spring that energizes the hydraulic piston of the hydraulic clutch C2 and the canceller plate is arranged in the centrifugal hydraulic canceller chamber. Therefore, the axial direction becomes compact as in the fourth aspect.

In the configuration of the sixth aspect, since the friction members of the hydraulic clutches C1 and C2 are fixed by one fixing member and one retaining ring, not only the axial direction becomes compact, but the fixing member is made of the friction member. Since it does not move in the direction, it is possible to reduce the loss torque due to the accompanying rotation of the friction member in the non-fastened state.

FIG. 1 shows an embodiment of a dual hydraulic clutch device of the present invention, and FIG. 2 shows the details thereof. 3 and 4 show another embodiment of the present invention. These are intended for a multi-speed automatic transmission of 6 forward speeds and 1 reverse speed having three planetary gear trains, two clutches and three brakes. Implementation of a dual hydraulic clutch device equipped with a reduction planetary gear for a multi-speed automatic transmission of 6 forward speeds and 1 reverse speed having 3 planetary gear trains, 3 clutches and 2 brakes The form is shown in FIG.

First, referring to FIG. 1, the dual hydraulic clutch device according to the present invention is suitable for the power of the input member 1 to reach the output members 15 and 16 via the hydraulic clutches C1 and C2, and is integrated with the input member 1. The formed clutch cover 2, the hydraulic piston 3 of the hydraulic clutch C1, the friction members 13a and 13b, and the output member 15, the hydraulic piston 4 of the hydraulic clutch C2, the friction members 14a and 14b, the output member 16, and the hydraulic clutches C1 and C2. A common fixing member 10, a canceller plate 5, and a return spring 7a are used.

The clutch cover 2 has a cylindrical shape having a side wall and one side is opened. The clutch cover 2 is welded integrally with the input member 1 at the inner periphery of the side wall. A spline is formed in the cylindrical inner peripheral portion of the clutch cover 2, a groove for fitting the retaining ring 12 is provided in the axial central portion of the spline, and the spline processing is applied to the outer peripheral portion and the axial central portion. A fixing member 10 having a groove into which the retaining ring 12 is fitted is fixed by the retaining ring 12. The groove of the retaining ring 12 formed on the fixing member 10 can be incorporated in the spline portion of the clutch cover 2 by making the difference in the groove inner diameter from the inner diameter of the spline larger than the inner and outer diameter difference of the retaining ring 12. . Therefore, the fixing member 10 is fixed to the clutch cover 2 in the rotational direction and the left and right axial directions. Further, a plurality of friction members 13b of the hydraulic clutch C1 on the side wall side and a plurality of friction members 14b of the hydraulic clutch C2 on the opening side with the fixing member 10 sandwiched by splines provided on the cylindrical inner peripheral portion of the clutch cover 2 Are splined. Friction members 13a and 14a are alternately arranged between the plurality of friction members 13b and 14b and the fixed member 10, and are spline-coupled to output members 15 and 16 having splines formed on the outer periphery.

The clutch cover 2 that is integral with the input member 1 provided with a stepped stepped portion that protrudes in the direction of the opening in a cylindrical shape in the radial direction of the side wall has a stepped portion along the side wall of the clutch cover 2. A hydraulic piston 3 entering the outer periphery and a hydraulic piston 4 entering the inner periphery are disposed in contact with the clutch cover 2 at respective protrusions provided on the inner periphery side of the stepped portion. Bonded seals 21 and 22 for sealing the gap between the step with the clutch cover 2 and the input member 1 are welded to the hydraulic piston 3 to form a working hydraulic chamber 20. Further, the outer periphery of the hydraulic piston 3 is bent toward the opening side of the clutch cover 2 and has a clutch disengagement space with the friction member 13b. The hydraulic piston 4 is welded with a bonded seal 31 that seals between the stepped portion with the clutch cover 2, and an inner peripheral portion thereof is bent along the input member 1, and an O-ring 32 provided on the input member 1 is used. It is sealed to form a working hydraulic chamber 30. Further, the outer periphery of the hydraulic piston 4 extends in a cylindrical shape along the cylindrical outer periphery of the clutch cover 2 beyond the opening of the clutch cover 2, and the clutch is disconnected between the front end and the friction member 14b. A flange 9 having a margin is fixed by a retaining ring 11.

The canceller plate 5 disposed on the opening side of the clutch cover 2 along the hydraulic piston 3 enters the outer periphery of the step portion of the hydraulic piston 3 and is sealed with a bonded seal 41 welded to the outer periphery of the step portion of the hydraulic piston 3. At the same time, the material is extended to the inner periphery of the hydraulic piston 3 to form a centrifugal hydraulic canceller chamber 40 that is open to the atmosphere on the inner periphery.

The hydraulic oil pressure chambers 20 and 30 and the centrifugal hydraulic pressure canceller chamber 40 pass through oil holes 23, 33, and 43 provided in the input member 1 from the oil passage of the transmission case 100 through a rotary seal ring, and from a hydraulic control valve (not shown). Oil is led.

In addition to FIG. 1, FIG. 2 shows a cross section of A part and B part showing the connection details of the canceller plate 5 and the hydraulic piston 4. The XX cross section shows the details of the A portion provided at six places which are symmetric about the rotation center. Rivet holes are provided in the side walls of the hydraulic piston 4 and the canceller plate 5, and through-holes having a larger diameter than the rivet holes are provided in the side walls of the clutch cover 2 and the hydraulic piston 3. A cylindrical spring holder 8 having a flange at one end in the outer circumferential direction and the other end in the inner circumferential direction is disposed in the through-round hole so that the cylindrical portion side of the outer circumferential flange is in contact with the side wall of the hydraulic piston 3. In addition, a coiled return spring 7 a is arranged inside the spring holder 8 so as to urge the inner circumferential direction flange of the spring holder 8 and the canceller plate 5. Further, a stud pin 6a having a stepped portion whose central portion has a larger diameter than both ends and the central portion has a constant axial length is disposed inside the return spring 7a, and the stepped portion is connected to the hydraulic piston 4 and the canceller. The canceller plate 5 and the hydraulic piston 4 are integrally connected at a fixed distance by contacting the side wall of the plate 5 and narrowing the rivet portions at both ends. The Y-Y cross section shows the details of the B part provided at three places which are symmetric about the rotation center. Similar to the part A, rivet holes are provided in the side walls of the hydraulic piston 4 and the canceller plate 5, and through-holes having a larger diameter than the rivet holes are provided in the side walls of the clutch cover 2 and the hydraulic piston 3. The center part of the through hole has a diameter larger than both ends, and the center part of the stud pin 6b having a stepped portion whose axial length is the same as the stud pin 6a is prevented from rotating with respect to the through hole. The stepped portion is in contact with the side walls of the hydraulic piston 4 and the canceller plate 5, and the rivet portions at both ends are narrowed to integrally connect the canceller plate 5 and the hydraulic piston 4 at a fixed distance. The integrated canceller plate 5, the hydraulic piston 4, and the hydraulic piston 3 are arranged so as to be axially movable with respect to the clutch cover 2 and are prevented from rotating.

Therefore, the hydraulic piston 3 of the hydraulic clutch C1 is moved by the hydraulic pressure of the working hydraulic chamber 20, presses the friction members 13a and 13b, and transmits the power of the input member 1 from the clutch cover 2 to the output member 15. Further, the hydraulic piston 4 of the hydraulic clutch C2 is moved by the hydraulic pressure of the working hydraulic chamber 30, presses the friction members 14a and 14b, and transmits the power of the input member 1 from the clutch cover 2 to the output member 16. Since the operating hydraulic chambers 20 and 30 are arranged without affecting each other, the hydraulic pistons 3 and 4 can be operated by their own hydraulic control. Here, the oil in the centrifugal hydraulic canceller chamber 40 directly acts on the hydraulic piston 3 to cancel the centrifugal hydraulic pressure in the working hydraulic chamber 20 and is integrated with the canceller plate 5 via the stud pins 6a and 6b. The centrifugal hydraulic pressure in the working hydraulic chamber 30 of the hydraulic piston 4 is also canceled. Further, the return spring 7 a biases the canceller plate 5 and the hydraulic piston 3 and simultaneously biases the hydraulic piston 4 integrated with the canceller plate 5. That is, the hydraulic piston 3 and the hydraulic piston 4 act to return to the clutch cover 2. The spring holder 8 serves to secure the set length of the return spring 7a without requiring a special space, and the centrifugal force acts greatly by arranging the coiled return spring 7a around the stud pin 6a. It is possible to avoid the influence of centrifugal force on the outer periphery.

FIG. 3, which is another embodiment of the present invention, is a connection between the canceller plate 5 and the hydraulic piston 4 without using a stud pin. In FIG. 3, a plurality of constricted holes that are symmetrical with respect to the rotation center on the outer circumference in the circumferential direction of the working hydraulic chambers 20 and 30 and the centrifugal hydraulic canceller chamber 40 are rectangular in the circumferential direction on the side wall of the hydraulic piston 4. The clutch cover 2 and the hydraulic piston 3 are provided with through-holes that are wider in the circumferential direction than the constricted holes, and a rod extending through the through-hole to the hydraulic piston 4 is formed integrally with the canceller plate 5. A step portion is provided with a constant axial length and reduced, and the step portion is inserted into a constriction hole so as to abut against the hydraulic piston 4, and the portion 5a is constricted and connected integrally at a constant distance. Further, a dish-plate-like return spring 7 b that urges the hydraulic piston 3 and the canceller plate 5 is disposed in the centrifugal hydraulic canceller chamber 40. Therefore, the integrated canceller plate 5, the hydraulic piston 4, and the hydraulic piston 3 are disposed so as to be freely rotatable in the axial direction with respect to the clutch cover 2. The operation of the hydraulic pistons 3 and 4 is the same as that of the embodiment of FIG.

FIG. 4, which is still another embodiment of the present invention, shows that the connection between the canceller plate 5 and the hydraulic piston 4 can be disassembled. In FIG. 4, the connection position is the same as that in FIG. 3, and the canceller plate 5 has a shape similar to that in FIG. A fixed hole having a rectangular shape in the circumferential direction is formed in the side wall of the hydraulic piston 4, and a through flat hole that is wider in the circumferential direction than the fixed hole is provided in the side walls of the clutch cover 2 and the hydraulic piston 3, and the hydraulic piston passes through the through flat hole. 4 is formed integrally with the canceller plate 5, and a step portion is provided and reduced with a circumferential width of the heel constant in the axial direction, and the tip portion 5 a is bent inward in the circumferential direction. It is inserted into the fixing hole so as to come into contact with the hydraulic piston 4 and is integrally connected at a fixed distance by the retaining ring 17. As shown in the ZZ cross section of FIG. 4, the retaining ring 17 is squeezed with a window rod that can be squeezed with a relatively low load of the hydraulic piston 4. In addition, a return spring 7b on a tray plate that biases the hydraulic piston 3 and the canceller plate 5 is disposed in the centrifugal hydraulic canceller chamber 40. Therefore, the integrated canceller plate 5, the hydraulic piston 4, and the hydraulic piston 3 are disposed so as to be freely rotatable in the axial direction with respect to the clutch cover 2. The operation of the hydraulic pistons 3 and 4 is the same as that of the embodiment of FIG.

FIG. 5 shows a structure of a double hydraulic clutch device having a planetary gear for reduction, and forward 6-speed reverse 1 having three planetary gear trains, two clutches and three brakes to which FIG. 1 is applied. Unlike a high-speed multi-speed automatic transmission, the present invention is directed to a multi-speed automatic transmission of six forward speeds and one reverse speed having three planetary gear trains, three clutches, and two brakes.

In FIG. 5, the clutch cover 2 constituting the double hydraulic clutch device, the hydraulic piston 3 and the output member 15 of the hydraulic clutch C1, the hydraulic piston 4 and the output member 16 of the hydraulic clutch C2, the canceller plate 5, and the canceller plate The structure of 57a is exactly the same as in FIG. 1, and the planetary gear that supports the sun gear S0 and the planetary pinion gear is arranged radially inside the friction members of the hydraulic clutches C1 and C2 disposed on the cylindrical inner periphery of the clutch cover 2. A reduction planetary gear composed of a carrier P0 and a ring gear R0 is arranged. The input member 1 integrated with the clutch cover 2 is pivotally supported by the transmission case with two radial needle bearings, and the sun gear S0 is splined to the transmission case extended in the axial direction at the inner periphery. . In the planet carrier P0, the side members sandwiching the planetary pinion gear are integrally formed by welding or the like, and the side members adjacent to the canceller plate 5 are splined to the input member 1 at the inner periphery. Power is input from a connecting portion extending radially inward of the hub welded to the opening side of the clutch cover 2 of the ring gear R0. The output member 15 of the hydraulic clutch C1 engages the friction member of the hydraulic clutch C1 with a spline at the outer peripheral portion, and extends in the inner peripheral direction along the welded hub that extends radially inward from the outer peripheral portion of the ring gear R0. The output member 16 of the hydraulic clutch C2 engages the friction member of the hydraulic clutch C2 with a spline on the outer peripheral portion, and the hub welded to the outer peripheral portion is hydraulically connected. The material is extended to the outside in the radial direction of the hydraulic piston 4 of the clutch C2, and the friction member of the brake B2 is locked. The material is extended in the inner peripheral direction along the output member 15, and has a connecting portion on the inner peripheral portion. Is done.

The power is input to the ring gear R0 of the built-in reduction planetary gear as indicated by the arrow in FIG. 5, and the sun gear S0 is fixed to the transmission case, so the planetary carrier P0 is decelerated and connected to the input member 1 connected by the spline. It is transmitted. The members constituting the dual hydraulic clutch device are the clutch cover 2, the hydraulic pistons 3, 4 and the canceller plate 5, and the space for the return spring is not particularly required. The continuous hydraulic clutch device is compact.

Here, a description will be given of a front-wheel-drive forward 6-speed reverse 1-speed automatic transmission to which the two-stage hydraulic clutch device for a multi-stage automatic transmission according to the present invention can be applied. FIGS. 6A, 6B and 6C show three planetary gear trains, two clutches and three brakes to which the double hydraulic clutch device of the present invention shown in FIGS. FIG. 8 is a skeleton diagram of a forward transmission 6-speed forward reverse 1-speed automatic transmission having a front wheel, a fastening element of each shift stage, and an alignment chart thereof, and FIG. 8 shows a specific implementation structure. 7 (a), 7 (b), and 7 (c) show three planetary gear trains and three clutches to which the dual hydraulic clutch device including the reduction planetary gear of the present invention shown in FIG. 5 is applied. FIG. 9 is a skeleton diagram of a front-wheel drive forward 6-speed reverse 1-speed automatic transmission having two brakes, a fastening element of each shift stage, and an alignment chart thereof. FIG. 9 shows a specific implementation structure.

In FIG. 6 (a), the planetary gear for reduction is a planet carrier P0 that supports a double planetary pinion gear that meshes with each other, a sun gear S0 that meshes with one of the double planetary pinion gears, and a ring gear R0 that meshes with the other of the double planetary pinion gears. The brakes B3 and B2 are arranged on the planetary carrier P0 and the ring gear R0. The planetary gear train having four components constituting the main transmission is composed of first and second planetary gear trains including a sun gear, a planet carrier supporting a single planetary pinion gear, and a ring gear. The sun gear S1 of the first planetary gear train and the ring gear R2 of the second planetary gear train are connected to the ring gear R0 of the reduction planetary gear train, and the planet carrier P1 of the first planetary gear train and the planets of the second planetary gear train. The carrier P2 is connected, the brake B1 and the one-way clutch OWC are arranged, the output of the hydraulic clutch C2 of the present invention is used, the ring gear R1 of the first planetary gear train is used as the output of the transmission, and the sun gear of the second planetary gear train is used. S2 is an output part of the hydraulic clutch C1 of the present invention.

The power is input from the arrow pointing to the left at the right end of FIG. 6 (a), and one is input to the sun gear S0 of the reduction planetary gear disposed at the right end, while the other is disposed at the left end. Is input to the input member 1 of the dual hydraulic clutch device. The output of the transmission is between the planetary gear for reduction and the first and second planetary gear trains constituting the main transmission, and shows the arrangement for driving the front wheels.

FIG. 6B shows the fastening elements of the respective forward shift speeds of the sixth forward speed and the reverse first speed shown in the skeleton diagram of FIG. 6A, and each shift speed is determined by two fastening elements. In the dual hydraulic clutch device of the present invention, only the hydraulic clutch C1 is engaged at the first forward speed, the second speed, and the third speed, the hydraulic clutches C1 and C2 are simultaneously engaged at the fourth forward speed, and the hydraulic pressure at the fifth forward speed and the sixth speed. Only the clutch C2 is engaged. Therefore, either one of the hydraulic clutches C1 and C2 can be engaged, or two can be engaged simultaneously, and the engagement and disengagement must be separately and accurately controlled. In the collinear diagram of FIG. 6C representing the speed of each component, the hydraulic clutch C1 is engaged at the first forward speed, the second speed, the third speed, and the fourth speed, and the power is directly input to the sun gear S2. The other engagement element at the first forward speed is the brake B1 or the one-way clutch OWC, the planetary carriers P1 and P2 are fixed, and the power is decelerated by the first and second planetary gear trains. In the second forward speed, the brake B2 is engaged, and the sun gear S1 and the ring gear R2 are fixed. At the third forward speed, the brake B3 is engaged, and the power is decelerated and input to the sun gear S1 and the ring gear R2 via the planetary gear for deceleration. At the fourth forward speed, the hydraulic clutch C2 is engaged, and the first and second planetary gear trains rotate together. Further, the hydraulic clutch C2 is engaged at the fifth forward speed and the sixth speed, and the power is directly input to the planet carriers P1 and P2. The other engagement element in the fifth forward speed is the brake B3, and the power is decelerated and input to the sun gear S1 and the ring gear R2 via the planetary gear for reduction, and the brake B2 is engaged and the sun gear S1 in the sixth forward speed. The ring gear R2 is fixed. Therefore, the speed of the ring gear R1, which is an output in the nomograph, gradually increases from the first forward speed to the second forward speed and the third forward speed, and is equal to the input rotation at the fourth forward speed. Further, the forward rotation speed of the fifth forward speed and the sixth forward speed increase, and the forward drive speed of the fifth forward speed and the sixth forward speed is higher than the input rotation. In reverse, the brakes B1 and B3 are engaged, and the power is decelerated and input to the sun gear S1 via the planetary gear for deceleration, and the planet carrier P1 is fixed, so that the speed of the ring gear R1 as an output is reversed. Decelerated.

In FIG. 8 showing the specific structure of FIG. 6A, the dual hydraulic clutch device of the present invention is arranged at the rear end of the transmission. Here, the friction member 14a of the hydraulic clutch C2 in FIG. 1 is engaged with the connecting member of the planetary carrier P2 connected to the planetary carrier P1 on the outer side in the radial direction of the ring gear R2, and the second planetary gear train is 2 of the present invention. Since it enters the continuous hydraulic clutch device, the transmission becomes compact in the axial direction. 1 is integrated with an input shaft from a torque converter (not shown), that is, the dual hydraulic clutch device itself is integrated with the input shaft, and the entire transmission has a simple structure.

In FIG. 7A, the planetary gear for reduction is composed of a planet carrier P0 that supports the planetary pinion gear, a sun gear S0 and a ring gear R0 that mesh with the planetary pinion gear, the ring gear R0 is the input shaft, and the sun gear S0 is the speed change. The equipment case and the planet carrier P0 are connected to the input member 1 of the dual hydraulic clutch device in FIG. The Ravigneaux planetary gear train having four components constituting the main transmission device meshes with the short pinion gear and the planet carrier P that supports the long pinion gear that is long in the axial direction and the short pinion gear that is short in the axial direction. It consists of a sun gear S2, a sun gear S1 meshing with the long pinion gear, and a ring gear R meshing with the long pinion gear. The planetary carrier P is provided with a brake B1 and a one-way clutch OWC, which also serves as an output of a hydraulic clutch C3 provided independently on the power input side. Further, the sun gear S2 of the Ravigneaux planetary gear train becomes the output of C1 of the double hydraulic clutch device, the sun gear S1 becomes the output of the hydraulic clutch C2, and the ring gear R becomes the output of the transmission.

Power is input from the arrow pointing to the left at the right end of FIG. 7A, one is input to the hydraulic clutch C3 disposed at the right end, and at the same time, the ring of the reduction planetary gear disposed at the left end. Input to gear R0. The power input to the ring gear R0 is input to the dual hydraulic clutch device having the hydraulic clutches C1 and C2 as the planetary carrier P0 is decelerated by fixing the sun gear S0. Accordingly, the decelerated power is output to the sun gear S2 and the sun gear S1 by the hydraulic clutches C1 and C2.

FIG. 7B shows the fastening elements of the respective forward shift speeds of the sixth forward speed and the reverse first speed shown in the skeleton diagram of FIG. 7A, and each shift speed is determined by two fastening elements. In the dual hydraulic clutch device provided with the reduction planetary gear of the present invention, only the hydraulic clutch C1 is engaged at the first forward speed, the second speed and the fourth speed, and the hydraulic clutches C1 and C2 are simultaneously engaged at the third forward speed, In the fifth speed, only the hydraulic clutch C2 is engaged. Therefore, either one of the hydraulic clutches C1 and C2 can be engaged, or two can be engaged simultaneously, and the engagement and disengagement must be separately and accurately controlled. In the collinear diagram of FIG. 7C showing the speed of each component, the hydraulic clutch C1 is engaged at the first forward speed, the second speed, the third speed, and the fourth speed, and the power is decelerated and input to the sun gear S2. The other engagement element in the first forward speed is the brake B1 or the one-way clutch OWC, and the planet carrier P is fixed. In the second forward speed, the brake B2 is engaged and the sun gear S1 is fixed. In the third forward speed, the hydraulic clutch C2 is engaged, and power is decelerated and input to the sun gear S1 via the planetary gear for deceleration. At the fourth forward speed, the hydraulic clutch C3 is engaged and power is directly input to the planet carrier P. Further, the hydraulic clutch C3 is engaged at the fifth forward speed and the sixth speed, and the power is directly input to the planet carrier P. The other engagement element in the fifth forward speed is the hydraulic clutch C2, and the power is decelerated and input to the sun gear S1 via the planetary gear for reduction, and the brake B2 is engaged and the sun gear S1 is fixed in the sixth forward speed. . Therefore, the speed of the ring gear R, which is an output in the nomograph, gradually increases from the first forward speed to the second forward speed, and at the third forward speed, the rotation of the double hydraulic clutch devices C1 and C2 that is the output of the reduction planetary gear Will be equal. Further, the fourth forward speed and the output rotation are high, and the fifth forward speed and the sixth forward speed are overdrive higher than the input rotation. In reverse, the hydraulic clutch C2 and the brake B1 are engaged, and power is decelerated and input to the sun gear S1 via the planetary gear for deceleration, and the speed of the ring gear R that is output is decelerated to reverse rotation.

In FIG. 9 showing the specific structure of FIG. 7A, the dual hydraulic clutch device provided with the planetary gear for reduction shown in FIG. 5 of the present invention is arranged at the rear end of the transmission. Here, a connecting portion of a dual hydraulic clutch device having a planetary gear for reduction which cannot be shown in FIG. 5 is clearly shown, and the input member 1 is pivotally supported by the transmission case at the rear end of the transmission. At the same time, the sun gear S0 is connected to the transmission case. The transmission case supports an input shaft from a torque converter (not shown), and the input shaft is connected to a hub welded to the ring gear R0. The output members 15 and 16 of the hydraulic clutches C1 and C2 are respectively extended through the inner periphery in the inner circumferential direction of the support portion of the transmission case that pivotally supports the output gear of the transmission, and are arranged on the outer periphery of the input shaft. The output member 16 of the hydraulic clutch C2 is connected to the sun gears S2 and S1 of the Ravigneaux planetary gear train that is the main transmission, and the hub welded to the outer periphery extends to the outside in the radial direction of the hydraulic piston 4 of the hydraulic clutch C2. The friction member of the brake B2 is locked, and the hydraulic pressure chamber and the hydraulic piston of the brake B2 are disposed on the radially outer side of the hydraulic piston 4. The reduction planetary gear train and its connecting members and the output members of the hydraulic clutches C1 and C2 can be arranged radially inside the friction members of the hydraulic clutches C1 and C2 arranged on the cylindrical inner peripheral portion of the clutch cover. Moreover, since the brake B2 is arranged on the radially outer side of the hydraulic clutches C1 and C2, the multi-stage automatic transmission itself having three clutches and two brakes, which tend to be complicated and long in the axial direction, can be made compact. It becomes possible.

Structure diagram of double hydraulic clutch device for multi-stage automatic transmission of the present invention Detailed connection diagram of canceller plate 5 and hydraulic piston 4 of FIG. Detailed connection diagram of the canceller plate 5 and the hydraulic piston 4 different from the connection method of FIGS. Detailed connection diagram of the canceller plate 5 and the hydraulic piston 4 different from the connection method of FIG. 1, FIG. 2 and FIG. Structure of a double hydraulic clutch device provided with a planetary gear for reduction according to the present invention FIG. 5 is a front-wheel drive forward 6-speed reverse 1-speed automatic transmission having three planetary gear trains, two clutches, and three brakes, showing an application example of the present invention, (a) is a skeleton diagram, (b) ) Is a fastening element of each gear stage, and (c) is a nomographic chart. FIG. 4 is a front 6-speed forward and reverse 1-speed automatic transmission having three planetary gear trains, three clutches, and two brakes showing another application example of the present invention, (a) is a skeleton diagram; (B) is a fastening element of each gear stage, (c) is an alignment chart. Specific structure of the skeleton diagram of FIG. Specific structure of the skeleton diagram of FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Input member 2 Clutch cover 3, 4 Hydraulic piston 5 Canceller plates 15, 16 Output member 20, 30 Actuation hydraulic chamber 40 Centrifugal hydraulic canceller chamber C1, C2, C3 Clutch B1, B2, B3 Brake S0, S1, S2 Sun gear P0, P1, P2, P Planet carrier R0, R1, R2, R Ring gear

Claims (6)

A spline is formed on the cylindrical inner periphery of the cylindrical clutch cover 2 having a side wall that is integral with the input member 1 and one of the openings is opened, and a fixing member is disposed at the axially central portion of the spline.
The friction members of the hydraulic clutches C1 and C2 are arranged on both sides of the fixed member,
A push type that is disposed inside the cylinder of the clutch cover 2, forms a working hydraulic chamber 20 between the clutch cover 2, and presses the friction member of the hydraulic clutch C 1 toward the opening of the clutch cover 2. A hydraulic piston 3;
An operating hydraulic chamber 30 is formed between the clutch cover 2 and the side wall portion of the clutch cover 2, and the friction member of the hydraulic clutch C 2 is flanged from the opening of the clutch cover 2. A double-type clutch device for a multi-stage automatic transmission, in which a pull-type hydraulic piston 4 that is in pressure contact with each other is disposed;
A centrifugal hydraulic canceller chamber 40 is formed between the hydraulic piston 3 and an axially movable canceller plate 5 is arranged on the opening side. The canceller plate 5 and the hydraulic piston 4 are connected to the clutch cover. 2 and a hydraulic clutch device for a multi-stage automatic transmission, in which a return spring that urges the hydraulic piston 3 and the canceller plate 5 is disposed. A planetary gear for reduction comprising a sun gear, a planet carrier for supporting the planetary pinion gear, and a ring gear on the radially inner side of the friction members of the hydraulic clutches C1 and C2 disposed on the cylindrical inner periphery of the clutch cover 2. A gear is arranged to connect the planet carrier to the input member 1 pivotally supported by a transmission case, and to connect the sun gear to the transmission case, and from the opening side of the clutch cover 2 to the canceller plate 5. In this order, the output member 16 of the hydraulic clutch C2, the output member 15 of the hydraulic clutch C1, and the hub welded to the ring gear are extended radially inward to provide a connecting portion, and the hydraulic pressure The multi-stage motor according to claim 1, wherein a hub for engaging a friction member of a brake B2 for braking the output member 16 is connected to the output member 16 of the clutch C2. Twin hydraulic clutch device for transmission. The clutch cover 2, the hydraulic pistons 3, 4 and the canceller plate 5 are formed as a press-molded product integrated from a flat plate, and the radial center portion of the side wall of the clutch cover 2 is cylindrically projected in the direction of the opening. Provided with a stepped shape, and the inner diameter is welded to the outer periphery of the input member 1;
The hydraulic piston 3 that enters the outer periphery of the step portion along the clutch cover 2 and is axially movable, and a sealing material is disposed between the step portion and the input member 1 to form the hydraulic pressure chamber 20. ,
The hydraulic piston 4 which enters the inner periphery of the step portion along the clutch cover 2 and is movable in the axial direction, and forms a working hydraulic chamber 30 by arranging a seal material between the step portion and the input member 1. When,
Along the hydraulic piston 3, it enters the outer periphery of the step portion of the hydraulic piston 3 and is movable in the axial direction. A sealing material is disposed between the step portions of the hydraulic piston 3 and the side wall extends to the inner periphery of the hydraulic piston 3. The double hydraulic clutch device for a multi-stage automatic transmission according to claim 1, further comprising: the canceller plate 5 that forms the centrifugal hydraulic canceller chamber 40 that is open to the inner atmosphere. A rivet hole is provided in a side wall of the hydraulic piston 4 and the canceller plate 5 at a plurality of the same positions which are symmetric with respect to the rotation center on the radially outer side of the working hydraulic chambers 20 and 30 and the centrifugal hydraulic canceller chamber 40. Is narrowed so as to integrally connect the hydraulic piston 4 and the canceller plate 5 at a constant distance with a stud pin having a larger diameter than both ends and having a constant axial length at the center.
In the clutch cover 2 and the hydraulic piston 3, a through hole that serves as a guide for the stud pin is provided at several locations on the circumference that is the same position as the stud pin.
A cylindrical outer peripheral portion of a cylindrical spring holder 8 having a flange at one end in the outer peripheral direction and the other end in the inner peripheral direction at the remaining portion of the clutch cover 2 and the hydraulic piston 3 at the same position as the stud pin is a guide. A through hole is formed, and the outer peripheral flange of the spring holder 8 is inserted into the clutch cover 2 and the hydraulic piston 3 so as to contact the hydraulic piston 3, and between the inner peripheral flange of the spring holder 8 and the canceller plate 5. The double hydraulic clutch device for a multi-stage automatic transmission according to claim 1, wherein a coil-shaped return spring having the stud pin as a guide is disposed on the multi-stage automatic transmission. A plurality of symmetrical positions about the radially outer rotation center of the working hydraulic chambers 20 and 30 and the centrifugal hydraulic canceller chamber 40, and a window hole having a rectangular shape in the circumferential direction on the side wall of the hydraulic piston 4; A through flat hole that is wider in the circumferential direction than the window hole is provided in the side walls of the clutch cover 2 and the hydraulic piston 3, and a rod that extends through the through flat hole to the hydraulic piston 4 is integrated with the canceller plate 5. The hydraulic piston 4 and the canceller plate 5 are connected to each other at a fixed distance by providing a retaining ring and a constriction at the collar portion,
In the centrifugal hydraulic canceller chamber 40, a plate-like return spring for urging the hydraulic piston 3 and the canceller plate 5 is arranged,
2. The multi-stage automatic transmission according to claim 1, wherein the hydraulic piston 4 and the canceller plate 5 are arranged so as to be movable in the axial direction, with the flange of the canceller plate 5, the through hole of the clutch cover 2 and the hydraulic piston 3 as a guide. Double hydraulic clutch device for machine. An outer peripheral portion of the fixing member fixed by the retaining ring 12 and the retaining ring groove formed in one axial center of the spline of the clutch cover 2 is fitted to the spline of the clutch cover 2. And a retaining ring groove on the radially outer side of the central portion, and a difference in outer diameter of the retaining ring 12 is made smaller than a difference between a spline inner diameter of the clutch cover 2 and a retaining ring groove inner diameter of the fixing member. 2. Double hydraulic clutch device for multi-stage automatic transmission according to 1

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