JPH0128258B2 - - Google Patents

Description

[Detailed description of the invention]

<Industrial Application Field> The present invention relates to an automatic transmission for automobiles. <Conventional Technology> Conventionally, FF (Front Wheel Front Drive) has been adopted as a drive system for automobiles due to the desire to expand the living space of automobiles. However, the automatic transmission used in this front-wheel drive vehicle must have a reduced axial dimension due to increased living space, a more compact engine compartment, and wheelbase limitations. Therefore, as shown in Japanese Patent Application Laid-Open No. 19861/1986, an automatic transmission having a gear transmission mechanism consisting of a planetary gear set, a multi-disc clutch, a multi-disc brake, and a one-way brake (clutch), A method of shortening the axial dimension by disposing a one-way brake (clutch) inside the multi-disc brake in the radial direction has been considered. <Problems to be Solved by the Invention> However, in such a structure, the reaction plate connected to the inner race of the one-way brake (clutch) is fitted by the same spline as the multi-plate brake, and the rear Since the front plate also serves as the pressure end plate of the multi-disc brake, the outer race of the one-way brake is likely to be misaligned with respect to the rotation center axis due to, for example, dimensional tolerances in manufacturing each component. Therefore, when the other race of the one-way clutch, for example the inner race, is fixed to the housing via the reaction plate, the outer race of the one-way clutch will rotate eccentrically relative to the inner race even when the one-way clutch is free. This causes wear on the one-way clutch. Furthermore, since the multi-disc brake is engaged and the reaction plate also serves as the pressure end plate of the multi-disc brake, the reaction plate is fixed in an eccentric state, and the one direction connected to the reaction plate The inner race of the clutch became eccentric, causing deformation of the end bearing of the one-way clutch, and there was a risk that the durability of the one-way clutch would be impaired. Therefore, the present invention aims to solve the above problems. <Means for Solving the Problems> The automatic transmission of the present invention includes a multi-disc brake B4 that locks one element of the planetary gear set 60 to the case, and a multi-disc brake B4 disposed radially inside the multi-disc brake B4. The one-way brake F3 has an inner race fe connected to another element of the planetary gear set 60, an outer race ff of the one-way brake F3 connected to a ring plate 55, and an inner race fe of the one-way brake F3 connected to another element of the planetary gear set 60. 55 is connected to the case and is provided with a plurality of holes 551, and the multi-disc brake B4 is connected to the cylinder 5 disposed in the case.
3, a piston 54 having a plurality of protruding members 541 slidably disposed on the cylinder 53;
It consists of a multi-plate disk pressed by a protruding member 541 of the piston, the protruding member of the piston is passed through a plurality of holes in the ring plate, and as the piston slides in the axial direction. , the protruding member presses the disk. Further, the automatic transmission of the present invention includes an input shaft 5, an output shaft 7, and a ring gear 63 connected to the input shaft.
a planetary gear set 60 comprising a carrier 64 and a sun gear 61 connected to the output shaft;
A multi-disc brake B4 for slidably connecting the sun gear to the case; a multi-disc clutch C3 for releasably connecting the sun gear 61 and the carrier 64; One-way brake F that engages with
3, the one-way brake is an F3 multi-disc brake B4.
The inner race fe of the one-way brake is connected to the sun gear 61 of the planetary gear set, the outer race ff of the one-way brake is connected to a ring plate 55, and the ring plate 55 is connected to the case. A plurality of holes 551 are connected to each other.
The multi-disc brake B4 includes a cylinder 53 disposed in the case, a piston 54 having a plurality of protruding members 541 slidably disposed on the cylinder, and a protrusion of the piston 54. Part 5
41, the protruding member 541 of the piston is passed through the plurality of annular holes 551, and as the piston slides in the axial direction, the protruding member 541 is characterized in that it presses the disk. <Operation and Effect> A one-way brake F3 is disposed inside the multi-disc brake B4 in the radial direction, and an outer race ff of the one-way brake F3 is connected to the case by a ring plate 55, and the ring plate 55 is connected to the case. A plurality of holes 551 are connected to each other, and the piston 54 of the multi-disc brake is disposed to be slidable in the axial direction with respect to the case, and the piston 54 of the multi-disc brake is connected to the multi-disc brake through the hole 551 of the ring plate. By pressing the disc, the axial dimension of the automatic transmission can be shortened. In addition, regardless of whether the multi-disc brake is engaged or released, the outer race ff of the one-way brake is locked to the case in the direction of rotation so that it cannot rotate relative to the case, and can slide freely in the direction of the center axis of rotation with an appropriate distance apart. Since the one-way brake can be fitted into the case and supported in the case in a floating manner at all times, wear and loss of function of the one-way brake caused by the dimensional tolerances allowed during manufacturing of each element of the planetary gear set 60 can be prevented, and durability can be improved. can be improved. Furthermore, the present invention provides that when the multi-disc clutch C3 is engaged to change speed from a directly coupled state to a deceleration state where the multi-disc clutch C3 is released and the one-way brake F3 and the multi-disc brake B4 are engaged, When the protruding member 541 of the piston slides in the axial direction to engage the multi-disc brake 4B, the protruding member passes through the hole 551 of the ring plate 55 connected to the outer race ff of the one-way brake. Since the disc of the multi-disc brake is pressed, the one-way brake can be brought into a locked state without being affected by the operation of the piston. Therefore, it is possible to maintain a compact axial dimension of the automatic transmission and to perform smooth downshifts. <Example> Next, the present invention will be described based on an example shown in the drawings. FIG. 1 is a side view of the exterior of automatic transmission 100, FIG. 2 is a sectional view showing its internal structure, and FIG. 3 is a skeleton diagram of the transmission. The automatic transmission 100 includes a hydraulic torque converter 200, a transmission 300, and a hydraulic control device 400. The transmission 300 includes a first planetary gear set 30 and a second planetary gear set 4.
0, two multi-disc clutches C ₁ , C 2 operated by hydraulic servos, one belt brake B ₁ , two multi-disc brakes B _{2 ,} B ₃ , one one-way clutch F ₁ , one single-disc brake A three-speed forward and one-reverse transmission with a directional brake _F2 , a first gear train 10, a third planetary gear set 60, and one multi-disc clutch operated by a hydraulic servo.
C ₃ , an underdrive device or second gear train 50 comprising one multi-plate brake B ₄ and one one-way brake F ₃ , a differential device 70 , and an output gear 71 of the underdrive device and a differential device The reduction gear device 80 includes an input gear 9 and an idler gear 8. The housing 110 of the automatic transmission is composed of a front housing 120 on the front side (engine side), that is, the upper side in FIG. The front housing 120 is a torque converter housing 12 whose front side (engine side) is open.
1 and a cylindrical transmission front case provided at the rear of the housing 121 and separated by a partition wall of the torque converter chamber 200A and the first gear train chamber, that is, in this embodiment, the transmission chamber 10A, that is, an intermediate support wall 122. a cylindrical portion 123 and an output gear 71 of an underdrive device that is continuously installed adjacent to the side of the torque converter housing 121;
The idler gear 10 and the front cases 124, 125, 126 of the differential device 70 are integrally formed. The rear housing, that is, the transmission case 130 is fitted onto the cylindrical front case 123 and connected to the rear end of the torque converter housing 121, and includes a transmission rear case 131 that is cylindrical and has a rear side wall 132; A second gear train chamber having a cylindrical shape and having a rear side wall 134 that is continuously adjacent to the side of the case 131, that is, the case 13 of the underdrive device in this embodiment.
3 and a rear cover 135 of the differential, a rear case, that is, the first gear train case 131, and a case, that is, the second gear train case 133.
An opening 137 is formed in the upper part (the upper part in FIG. 1, the left part in FIG. 2), and the box body 136 is integrated with a box body 136 that has an oil reservoir 138 with a sufficient capacity on the lower side of the rear case 131. It is formed into. The bearing retainer 140 is formed by integrally forming the output gear 71, the idler gear 8, and the rear cases 141, 142, and 143 of the differential gear 70, respectively. In the automatic transmission housing 110,
The connecting portions of the front housing 120 and the bearing retainer 140 are formed in a ferrule structure, and the corresponding portions of the front cases 124, 125, 126 and the rear cases 141, 142, 143 fit together. By being attached and fastened with bolts 144, a differential housing 170 having an output gear chamber 71A, an idler gear chamber 8A, and a differential gear chamber 70A communicating with each other is formed, and a torque converter which is a solid fastening body between the two is formed. A differential housing 500 is formed. The rear housing, that is, the transmission case 130 is connected to the rear part of the torque converter differential housing 500, and the transmission case 130 is connected to the rear part of the torque converter differential housing 500.
A hydraulic control device case 150 forms an underdrive device chamber 50A and an underdrive device chamber 50A, and further houses a hydraulic control device 400 consisting of various valve bodies (not shown), communication oil passages (not shown), etc. in the opening 137 of the box body. They are connected to form a housing 110 of an automatic transmission. The torque converter 200 has a front cover 2
The pump impeller 202 is connected to the engine output shaft through the turbine hub, and the output shaft 1 is connected to the output shaft through the turbine hub.
a stator 206 connected to a turbine hub, a stator 206 engaged with a tubular fixed shaft or stator shaft 205 that fits into the center hole 122A of the intermediate support wall 122 via a one-way brake 204; It has a known configuration consisting of a direct coupling clutch 207, and the torque converter case 12
It is installed in 1. The oil pump 90 has an annular space formed between the fixed shaft 205 and a cylindrical protrusion 95 provided on the outer circumferential side of the intermediate support wall or partition wall 122 on the torque converter side.
6, a cylindrical pump drive shaft 94 rotatably fitted onto the fixed shaft 205 and integral with the pump impeller 202;
A pump body 91 housing a pump gear 93 driven by the pump body 91 is formed by sandwiching and fastening an annular steel plate 92. In addition, the annular thin plate 92 prevents wear of the pump gear, and also serves to prevent the pump gear from wearing out.
Oil passage groove 9 formed on the side of the torque converter
7 is closed, and an oil passage 98 is formed. In the transmission chamber 10A, a forward cylindrical rear center support 11 is provided protruding from the center of the rear side wall 132, and the tubular fixed shaft 2 is provided at the center rear surface of the intermediate support wall 122.
A front center support 1 which has a large diameter cylindrical shape and is integral with 05 and is coaxial with the rear center support 11.
2 is fixed backwards. Inside the rear center support 11 and the tubular fixed shaft 205, a torque converter output shaft as well as the input shaft 1 of the transmission 10 and transmission 100 is rotatably supported. Output of a transmission 10 in which a first intermediate shaft 2 is rotatably mounted, a cylindrical sun gear shaft 3 is rotatably mounted on the outside thereof, and the tip of the first intermediate shaft 2 is spline-coupled to the front center support 12. A gear 4 is rotatably supported. The input shaft 1 of the transmission is connected to the forward facing rear center support 11 at its rear part.
It is spline-fitted to an annular hydraulic servo center drum 21 which is rotatably fitted onto the tip of the cylinder. The hydraulic servo center drum 21 is open at the front, has a rearward-facing cylindrical protrusion 211 formed in the middle part, and is located between an inner circumferential wall 212 and an outer circumferential wall 213 that are fitted onto the tip of the rear center support 11. The annular piston 22 is fitted to form a hydraulic servo c1 of the clutch _C1 , and is connected to the ring gear 33 of the first planetary gear set 30 via a multi-plate clutch _C1 formed in the outer peripheral wall 213. . The first planetary gear set 30 is provided in front of the hydraulic servo c1, includes a sun gear 31 formed at the rear end of the sun gear shaft 3, and a planetary carrier 32 spline-coupled to the rear end of the first intermediate shaft 2. , a ring gear 33 connected to the center drum 21 via the multi-plate clutch C ₁ , and a planetary gear 34 rotatably supported by a carrier 32 and meshed with the sun gear 31 and the ring gear 33. An annular hydraulic servo rear drum 23 is rotatably fitted onto the rear center support 11 between the center drum 21 and the rear side wall 132. The rear drum 23 is open at the front, and the inner peripheral wall 23
1 and the outer circumferential wall 232 to form a hydraulic servo _c2 of a multi-disc clutch _C2 , and the cylinder of the center drum protrusion 2
11 and to the front side of the sun gear 31 of the sun gear shaft 3 via a connecting drum 25 connected to the rear end of the outer peripheral wall 232. The connecting drum 25 covers the center drum 21 and the first planetary gear set 30, and has an outer peripheral wall 25.
Friction engagement plate 25 of belt brake B 1 is operated by a hydraulic servo (not shown) on the outside of B ₁ .
2 is installed. A front drum 26 for hydraulic servo which is annular and open at the front is fitted into the rear end of the inner surface of the cylindrical front case 123 which is fitted into the rear case 131 on the front side of the connecting drum 25. The piston 27 is fitted to form a hydraulic servo _b2 of the multi-disc brake _B2 . A spline groove 123A is formed on the inner surface of the cylindrical front case 123, and a multi-disc brake B ₂ is installed in front of the hydraulic servo B ₂ , and a one-way clutch F 2 connected to the front side by an outer race FD is connected to the multi-disc brake B ₂ in front of the hydraulic servo B 2 .
A reverse multi-disc brake _B3 is fitted in front of it. The rear surface of the intermediate support wall 122 of the front housing 120, which is the front wall of the transmission chamber 10A, is equipped with an annular reverse brake hydraulic cylinder 28.
An annular piston 29 is formed in the cylinder 28, and a cylindrical pressure transmission ring 291 for pressing a multi-disc brake _B3 extending rearward from the outer periphery is protruded from the cylinder 28.
is fitted to form _the hydraulic servo _b3 of the reverse brake B3. Further, a protrusion 292 for preventing rotation of the annular piston 29, which is engaged with the spline groove 123A, is provided on the outer side of the rear end of the pressure transmission ring 291 of the piston. Inside the brake _B2 , there is a one-way clutch _F1 in which the sun gear shaft 3 is an inner race fa and an outer race fb is connected to the case ₁₂₃ via the brake B2.
A second planetary gear set 40 is provided in front of the one-way clutch _F1 .
The second planetary gear set 40 is connected to the sun gear 41 formed at the tip of the sun gear shaft 3 and the inner race fc of the one-way brake _F2 , and is connected to the front case ₁₂₃ via the multi-disc brake B3.
It consists of a planetary carrier 42 connected to the output gear 4, a ring gear 43 connected to the output gear 4, and a planetary gear 44 rotatably supported by the carrier 42 and meshed with the sun gear 41 and the ring gear 43. The underdrive device chamber 50A has a rear wall 134
A forward cylindrical rear center support 51 is protruded from the center of the rear case 141 of the output gear, and a rear cylindrical front center support 52 is protruded from the center of the rear case 141 of the output gear. The output shaft 7 forming the gear 71 is rotatably supported by a tapered roller bearing 72 installed in the output gear chamber 71A, and a cylindrical second The intermediate shaft 6 is rotatably fitted onto the outside, and the input gear 5 is rotatably supported by the front center support 52. An annular hydraulic cylinder 53 is formed on the front surface of the rear wall 134 of the underdrive device chamber 50A, and the cylinder 53 has an annular hydraulic cylinder 53 with protruding rods for pressing the brake B ₄ arranged circumferentially at the tips of an annular projection on the outer circumferential side. An annular piston 54 having a tooth-like protrusion 541 provided therearound is fitted therein to form a hydraulic servo _b4 of a multi-disc brake _B4 . On the front side of the hydraulic servo _b4 , the rear end of the second intermediate shaft 6 is an inner race fe,
The outer race ff is provided with a one-way brake F ₃ connected to the case 133 via a connecting ring 55 having a plurality of holes 551 around it through which the toothed protrusions 541 pass. Case 1 on the front side of the connecting ring 55
A multi-disc brake _B4 is fitted inside 33. On the front side of the one-way brake F ₃ , a rearward cylindrical portion 561 is provided at the intermediate portion thereof and is connected to a hydraulic servo annular drum 56 that is open toward the front. The outer peripheral wall 562 of the drum 56 and the second intermediate shaft 6
An annular piston 57 is fitted between the outer surface of the multi-plate clutch C3 and a hydraulic servo _C3 of the multi-disc clutch C3.
Further, the annular drum 56 is connected to a carrier 62 of a third planetary gear set 60 via a multi-disc clutch _C3 formed within the outer circumferential wall 562, and a multi-disc brake formed outside the cylindrical portion 561.
It is connected to the case 133 via _B4 . A third planetary gear set 60 is provided on the front side of the hydraulic servo c3, and the third planetary gear set 60 is spline-fitted to a sun gear 61 formed at the tip of the second intermediate shaft 6 and to the output shaft 7. The annular drum 56 is connected to the annular drum 56 via the multi-plate clutch _C3 .
It consists of a planetary carrier 62 connected to the input gear 5, a ring gear 63 connected to the input gear 5, and a planetary gear 64 rotatably supported by the carrier 62 and meshed with the sun gear 61 and the ring gear 63. A chain 160 for drivingly connecting the output gear 4 of the transmission 10 and the input gear 5 of the underdrive device 50 is stretched, and the chain 160 connects the pressure transmission ring 2 of the annular piston 29.
Two notches 161 provided at predetermined positions of 91
and a cylindrical portion 12 which is a transmission front case.
Two notches 162 provided at predetermined positions of 3
and two notches 163 provided at predetermined positions of the transmission case 130.
It passes through two communication holes. The speed reducer 80 includes an output gear 71 of an underdrive device formed at the tip of the output shaft 7 and rotatably supported in the output gear chamber 71A by a tapered roller bearing 72, and an idler gear chamber 8A.
An idler gear 8 that is rotatably supported by a tapered roller bearing 82 mounted on a fourth shaft 81 fixedly installed between the front case 125 and the rear case 142, and meshes with the output gear 71.
and is formed on the rear outer periphery of the differential gear input section 701 rotatably supported within the differential gear chamber 70A by a tapered roller bearing 901,
It is composed of an input gear 9 that meshes with the idler gear 8. The differential device 70 includes a differential gear 702 having a known configuration attached to wheel axles 9A and 9B, which are output shafts of an automatic transmission. The transmission 300 controls the hydraulic control device 40 according to vehicle running conditions such as vehicle speed and throttle opening.
The clutches and brakes are engaged or released by hydraulic pressure selectively output from zero to each hydraulic servo, and four forward speeds or one reverse speed change is performed. Three examples of the gears (RANGE) and reduction ratios (RATIO) achieved with the operation of each clutch, brake, and one-way clutch are shown in Table 2, respectively.

【table】

【table】

[Table] In the table, ○ indicates the engaged state, △ indicates the engine brake, and × indicates the disengaged state. The rotation outputted from the output shaft 7 of the underdrive device 50 after being changed in speed as shown in the above table is reduced to a predetermined rotation speed by the output gear 71, the idler gear 8, and the input gear 9, and the rotation is reduced to a predetermined rotation speed by the differential device 70. and drives the wheel axles 9A and 9B, which are the output shafts of the automatic transmission 100, through a known differential gear 702. As described above, the automatic transmission of the present invention provides a first gear train with three forward gears and a reverse gear on the first shaft, which is the output shaft of the torque converter and the input shaft of the transmission. The transmission is configured by providing a second gear train with a two-speed underdrive on a second shaft arranged parallel to the second shaft, and drivingly connecting the first gear train and the second gear train with a chain. The automatic transmission has a planetary gear set, one multi-disc clutch C ₃ operated by a hydraulic servo, one multi-disc brake B ₄ and one one-way brake F ₃ . In the second gear train, the outer race of the one-way brake F ₃ is welded to an annular plate-shaped connecting ring that is secured to the transmission case, and this connecting ring connects the multi-disc brake B ₄ and the hydraulic pressure of the multi-disc brake. Built in between servo B ₄ , the annular piston of hydraulic servo B ₄ has
At the tip of the annular projection, an annular tooth-like projection in which protruding rods for pressing the brake _B4 are arranged circumferentially is provided, and the tooth-like projection is inserted into a hole provided around the connecting ring at a position corresponding to the tooth-like projection. The configuration in which the multi-plate brake B ₄ is pressed through the brake cylinder reduces the axial dimension, ensures reliability by floating the outer race of the one-way brake F ₃ , and improves durability by enabling one-way brake forced lubrication. Since it can be formed into the transmission case, it achieves many results such as reducing the number of parts and making it easier to supply hydraulic pressure to the hydraulic servo.

[Brief explanation of drawings]

FIG. 1 is a side view of the external appearance of an automatic transmission according to the present invention, FIG. 2 is a sectional view showing its internal structure, and FIG.
The figure is a skeletal diagram of the transmission. In the figure, 1...first shaft, 4...output gear of first gear train, 5...input gear of second gear train, 7...second shaft, 10...first gear train,
50... Second gear train, 53... Annular hydraulic cylinder, 54... Annular piston, 55... Connecting ring, 541... Teeth, 551... Hole, B ₄ ...
... Brake, b ₄ ... Hydraulic servo, F ₃ ... One-way brake, fe ... Inner race, ff ... Outer race, 130 ... Transmission case, 20
0...Torque converter, 300...Transmission, 400...Hydraulic control device.

Claims (1)

[Scope of Claims] 1. A multi-disc brake for locking one element of a planetary gear set to a case, and a one-way brake disposed radially inside the multi-disc brake, and an inner race of the one-way brake. is connected to another element of the planetary gear set, the outer race of the one-way brake is connected to a ring plate, the ring plate is connected to the case and is provided with a plurality of holes, and the multi-plate brake consists of a cylinder disposed in the case, a piston having a plurality of protruding members slidably disposed on the cylinder, and a multi-plate disk pressed by the protruding members of the piston, An automatic transmission characterized in that a protruding member of the piston is passed through a plurality of holes in the ring plate, and as the piston slides in the axial direction, the protruding member presses the disc. 2. A planetary gear set consisting of an input shaft, an output shaft, a ring gear connected to the input shaft, a carrier and a sun gear connected to the output shaft, and a multi-disc brake that slidably connects the sun gear to a case. , an automatic transmission having a deceleration mechanism comprising a multi-disc clutch that connects the sun gear, the sun gear, and the carrier in a detachable manner; and a one-way brake that engages the sun gear with the case in only one rotational direction. In the machine, the one-way brake is arranged radially inside the multi-disc brake, an inner race of the one-way brake is connected to a sun gear of the planetary gear set, an outer race of the one-way brake is connected to a ring plate, The ring plate is connected to the case and is provided with a plurality of holes, and the multi-plate brake includes a cylinder disposed in the case and a plurality of protrusions slidably disposed on the cylinder. The piston comprises a piston having a member, and a multi-plate disk pressed by a protruding member of the piston, the protruding member of the piston being passed through a plurality of holes in the ring plate, and the piston being slid in the axial direction. The automatic transmission is characterized in that the protruding member presses the disk as the movement of the automatic transmission occurs.