JPH0250344B2 - - Google Patents

Description

[Detailed description of the invention]

(Industrial Application Field) The present invention relates to an automatic transmission for automobiles. (Prior Art) In recent years, front-engine, front-drive (hereinafter referred to as "FF") automobiles have been provided with the aim of reducing fuel consumption, making them smaller and lighter. In addition, multi-stage automatic transmissions for front-wheel drive vehicles are also required to be compact, lightweight, and easy to mount.In particular, automatic transmissions for front-wheel drive vehicles with horizontal engines are required to have shortened axial dimensions. In this type of automatic transmission, a transmission case is disposed adjacent to a torque converter housing that houses a torque converter, and a transmission is disposed within the transmission case. A multi-shaft transmission is used, and a transmission receiving the output of the torque converter is disposed on the first shaft.
An underdrive device and a speed reduction device receiving the output of the transmission are arranged on the second shaft, and both ends are arranged in parallel. The output shaft of the transmission and the input shaft of the underdrive device are connected via a chain on the rear side of the automatic transmission, that is, on the side opposite to the engine. (Problems to be Solved by the Invention) However, in the automatic transmission having the above configuration, the torque converter and the transmission device are arranged on the first shaft, and the underdrive device and the speed reduction device are arranged on the second shaft. Because it is arranged on one shaft, the axial dimension can be made shorter than when everything is arranged on one shaft. Since it is configured to transmit power, it is necessary to increase the axial dimension of the second shaft to the position where the chain is disposed. Furthermore, an axial dimension is required to ensure the capacity of the frictional engagement elements constituting the transmission, such as a reverse brake, and there is a limit to reducing the axial dimension of the automatic transmission. Furthermore, the torque converter housing that accommodates the torque converter and the transmission case that accommodates the transmission are formed separately for convenience of assembly. In this case, it is difficult to achieve concentricity between the torque converter supported by the torque converter housing and the transmission supported by the transmission case. The present invention solves the problems of the conventional automatic transmission described above, and prevents the axial dimension of the transmission case from increasing due to the chain and frictional engagement elements incorporated into the transmission case. It is an object of the present invention to provide an automatic transmission in which the capacity of a friction engagement element can be increased, concentricity can be easily achieved between a torque converter and a transmission, and the assembly is easy. (Means for solving the problem) For this purpose, in the automatic transmission of the present invention,
a torque converter coaxially disposed on the output shaft of the engine; a first shaft coaxially disposed on the output shaft of the torque converter and extending rearward; and a first planetary gear disposed on the first shaft. a second shaft disposed parallel to the first shaft; a second planetary gear set disposed on the second shaft; and a first planetary gear set disposed on the first shaft. a first gear connected to the output side of the second planetary gear set; a second gear disposed on the second shaft and connected to the input side of the second planetary gear set;
and a second gear at a position adjacent to the torque converter. Further, a torque converter housing that accommodates the torque converter and forms a torque converter chamber, and a transmission that is disposed adjacent to the torque converter housing and that accommodates the transmission and forms a transmission chamber. Has a case. A partition wall separating the torque converter chamber and the transmission chamber is formed integrally with the torque converter housing, and the partition wall includes a cylindrical portion extending toward the transmission chamber and fitting into the transmission case. is formed in the cylindrical portion, and a hydraulic servo whose cylinder wall is the partition wall, and a frictional engagement member which is engaged and disengaged by a piston moved by the hydraulic servo and spline-engaged with the inner peripheral edge of the cylindrical portion. Elements are placed. Also,
A rotation stopping portion is provided on the outer circumferential edge of the piston and is engaged with the inner circumferential edge of the cylindrical portion. moreover,
A notch is formed in the piston to accommodate the chain. (Operation and Effects of the Invention) According to the present invention, as described above, there is provided a torque converter coaxially disposed on the output shaft of the engine, and a torque converter coaxially disposed on the output shaft of the torque converter and extending rearward. a first shaft, a first planetary gear set disposed on the first shaft, a second shaft disposed parallel to the first shaft, and a second planetary gear set disposed on the second shaft. a first gear disposed on the first shaft and connected to the output side of the first planetary gear set; and a first gear disposed on the second shaft and connected to the input side of the second planetary gear set. the first gear and the second gear
The torque converter has a chain that connects the gears at a position adjacent to the torque converter. Therefore, since the chain is disposed on the torque converter housing side, the second shaft is prevented from becoming longer than necessary, and the axial dimension is shortened. Furthermore, since the second shaft is shortened, there is no interference between the suspension portion and the second shaft. Further, a torque converter housing that accommodates the torque converter and forms a torque converter chamber, and a transmission that is disposed adjacent to the torque converter housing and that accommodates the transmission and forms a transmission chamber. a case, a partition wall separating the torque converter chamber and the transmission chamber is formed integrally with the torque converter housing;
The partition wall is formed with a cylindrical part that extends toward the transmission chamber and fits into the transmission case, and within the cylindrical part is a hydraulic servo that uses the partition wall as a cylinder wall, and a hydraulic servo that is operated by the hydraulic servo. A frictional engagement element is disposed that is engaged and disengaged by the moving piston and spline-engaged with the inner circumferential edge of the cylindrical portion, and is engaged with the inner circumferential edge of the cylindrical portion on the outer circumferential edge of the piston. The piston is further provided with a notch for arranging the chain. Therefore, there is no need to provide a separate cylinder to the hydraulic servo, the axial dimension of the transmission case can be shortened by the lack of a cylinder, and the capacity of the hydraulic servo can be increased. (Example) Hereinafter, an example of the present invention will be described in detail with reference to the drawings. FIG. 1 is an external view of the automatic transmission of the present invention, FIG. 2 is a diagram showing the internal structure of the automatic transmission, and FIG. 3 is a skeletal diagram of the transmission of the automatic transmission. In the figure, an 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 servo, one belt brake B ₁ , two multi-disc brakes B _{2 ,} B ₃ and two one-way clutches F ₁ , F ₂ . It has a transmission 10 with three forward speeds and one reverse speed, and includes a third planetary gear set 60, one multi-disc clutch C ₃ , one multi-disc brake B ₄ and one one-way clutch F ₃ operated by a hydraulic servo. The underdrive device 50 includes a differential device 70 and an output gear 7 of the underdrive device 50.
1, a differential gear 70, an input gear 9, and an idler gear room 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 cover 120 includes a torque converter housing 121 whose front side (engine side) is open.
and a partition wall between the torque converter chamber 200A and the transmission chamber 10A, that is, an intermediate support wall 1 provided at the rear of the torque converter housing 121.
A cylindrical part 123 that is a cylindrical transmission front case separated by 22, an output gear 71 of an underdrive device, and an idler gear 1 that are continuously adjacent to the side of the torque converter housing 121.
0 and the differential gear 70 are integrally formed with respective front cases 124, 125, and 126. The rear housing, that is, the transmission case 130 is fitted onto the cylindrical portion 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, and the rear case It is a box body that encloses the case 138 of the underdrive device, the rear cover 135 of the differential device, the rear case 131, and the case 133, which are cylindrical and have a rear side wall 134 that is continuously adjacent to the side of the case 131. A hydraulic control device cover connecting portion 136 having an opening (left side in FIG. 2) is integrally formed. The bearing retainer 140 includes rear cases 141, 142, and 143 formed integrally with the output gear 71, idler gear 8, and differential gear 70, respectively. In the automatic transmission housing 110,
The front housing 120 and the bearing retainer 140 have a connecting portion formed in a ferrule structure, and the front case 1, which is a corresponding portion between them,
24, 125, 126 and the above rear case 141,
142 and 143 are fitted, and the bolt 144
The output gear chamber 71 communicates by being fastened with the
A, a differential housing chamber 70A having an idler gear chamber 8A and a differential gear chamber 70A is formed, forming a torque converter/differential housing 500 that is a solid fastening body between the two. A transmission case 130 is connected to the rear portion of the torque converter differential housing 500 to form a transmission chamber 10A and an underdrive device chamber 50A, and the cover connecting portion 136
A hydraulic control device cover 150 is connected to the housing 110 of the automatic transmission. The torque converter 200 has a front cover 20
1, a pump impeller 202 (FIG. 3) connected to the engine output shaft 1, a turbine runner 203 connected to the output shaft 1 through a turbine hub, and a one-way clutch 204 connected to the intermediate support wall 1.
a tubular fixed shaft that fits into the center hole 122A of 22;
That is, it is composed of a stator 206 engaged with a stator shaft 205, a direct coupling clutch 207 connected to a turbine hub, and a torque converter case 12.
It is installed in 1. The oil pump 90 includes a cylindrical projection 9 provided around the outer circumferential side of the intermediate support wall 122 on the torque converter side.
5 is rotatably fitted onto the fixed shaft 205 in an annular space formed between the fixed shafts 205, that is, the pump body fitting portion 96, and the pump impeller 2
A pump body 91 housing a pump gear 93 driven by a cylindrical pump drive shaft 94 integral with 02 is formed by being fastened with a steel annular thin plate 92 in between. Further, the annular thin plate 92 prevents wear of the pump gear and closes an oil passage groove 97 formed on the side surface of the torque converter of the intermediate support wall 122 to form an oil passage 98. The transmission chamber 10A has a forward-facing cylindrical rear center support 11 protruding from the center of the rear wall 132.
On the central rear surface of the intermediate support wall 122, a large-diameter cylindrical body integral with the cylindrical fixed shaft 205 and the rear center support 11 and a coaxial front center support 12 are fixed rearward. Inside the rear center support 11 and the tubular fixed shaft 205 is a torque converter output shaft and a transmission device 1.
0 and transmission 100 are rotatably supported, a cylindrical first intermediate shaft 2 is rotatably mounted on the outside of the input shaft 1, and a cylindrical sun gear shaft 3 is rotatably mounted on the outside of the first intermediate shaft 2. The output gear 4 of the transmission 10 is freely mounted and spline-coupled to the tip of the first intermediate shaft 2 to the front center support 12.
is rotatably supported. The input shaft 1 of the transmission is connected at its rear to the forward facing rear center support 1.
The hydraulic servo center drum 21 is spline-fitted to an annular hydraulic servo center drum 21 which is rotatably fitted onto the tip of the hydraulic servo. The hydraulic servo center drum 21 is open at the front, has a rearward-facing cylindrical protrusion 211 formed in the middle, 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 c ₁ of the clutch C ₁ , and is connected to the ring gear 33 of the first planetary gear set 30 via a multi-plate clutch C ₁ formed in the outer peripheral wall 213 . The first planetary gear set 30 is provided in front of the hydraulic servo _c1 , and includes a sun gear 31 formed at the rear end of the sun gear shaft 3, a planetary carrier 32 spline-coupled to the rear end of the first intermediate shaft 2, It consists of 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 planetary 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 the multi-disc clutch _C2 .
The cylindrical protrusion 211 of the center drum via C ₂
It is also connected 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 a friction engagement plate 252 of a belt brake _B1 operated by a hydraulic servo (not shown) is attached to the outside of its outer peripheral wall 251. . A cylindrical front case 123 that fits inside the rear case 131 on the front side of the connecting drum 25
A front drum 26 for a hydraulic servo which is annular and open at the front is fitted into the rear end of the inner surface of the brake, and an annular piston 27 is fitted into the front drum ₂₆ to form a hydraulic servo _b2 of a multi-disc brake B2. has been done. A spline groove 123A is formed on the inner surface of the cylindrical portion 123, and a multi-disc brake B ₂ is provided in front of the hydraulic servo b ₂ , a one-way clutch F ₂ connected by an outer race FD is provided in front of the multi-disc brake B 2 , and a reverse brake is provided in front of the multi-disc brake B 2 . A multi-disc brake _B3 is fitted. An annular reverse brake hydraulic cylinder 28 is formed by a cylindrical portion 123 on the rear surface of the intermediate support wall 122 of the front housing 120, which is the front wall of the transmission chamber 10A. A piston 29 is slidably disposed to form a hydraulic servo _{b3 of} a reverse brake B3. A cylindrical pressure transmission ring 291 is provided on the piston 29 to press the multi-disc brake B ₃ when engaged. At the rear of the above multi-disc brake B ₃ , there is a hydraulic servo
A regulating member such as a snap spring is provided to restrict the movement of the friction engagement plate in the axial direction and to apply a reaction force to the pressure transmission ring 291 when b ₃ is activated and the friction engagement plate engages. be done. Therefore, the thrust force generated when the hydraulic servo _b3 is activated is absorbed by the cylindrical portion 123. On the inside of the above brake B ₂ , the sun gear shaft 3 is the inner race fa, and the outer race fd is the brake.
A one-way clutch F ₁ connected to the cylindrical portion 123 via B ₂ is provided, and a second planetary gear set 4 is disposed in front of the one-way clutch F ₁ .
0 is set. The second planetary gear set 40 is connected to a sun gear 41 formed at the tip of the sun gear shaft 3, an inner race fc of a one-way clutch _F2 , and connected to the cylindrical portion ₁₂₃ via a multi-disc brake B3. Ring gear 4 connected to planetary carrier 42 and output gear 4
3 and a planetary gear 44 rotatably supported by a carrier 42 and meshed with a sun gear 41 and a ring gear 43. The underdrive device chamber 50A has a rear wall 134
A forward-facing cylindrical rear center support 51 is protruded from the center of the output gear, and a rearward-facing cylindrical front center support 52 is protruded from the center of the rear case of the output gear, and an output gear 71 is formed at the front of the center. The output shaft 7 is rotatably supported by a tapered roller bearing 72 installed in the output gear chamber 71A, and the rear side of the output shaft 7 and the rear center support 5
A cylindrical second intermediate shaft 6 is rotatably fitted on the outside of the front center support 52, 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 an annular piston 54 is fitted into the cylinder 53, and the cylinder 53 has a tooth-like protrusion 541 for pressing the brake B ₄ on the outer circumferential side. A hydraulic servo _b4 of a multi-disc brake _B4 is formed. 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 clutch F ₃ connected to the case 133 via a connecting ring 55 passing through the toothed protrusion 541 . A multi-disc brake _B4 is formed inside the case 133 on the front side of the connecting ring 55. The front side of the one-way clutch _F3 has a rearward-facing cylindrical part 5 in the middle part.
61 is provided in a protruding manner, and a hydraulic servo annular drum 56 which is open to the front is connected thereto. An annular piston 57 is fitted between the outer circumferential wall 562 of the annular drum 56 for hydraulic servo and the outer surface of the second intermediate shaft 6, forming _a hydraulic servo _c3 of a multi-plate clutch C3;
Further, the annular drum 56 for hydraulic servo has an outer peripheral wall 562.
It is connected to the carrier 62 of the third planetary gear set 60 via a multi-disc clutch C ₃ formed inside, and further connected to the case 133 via a multi-disc brake B ₄ formed outside the cylindrical part 561. There is. 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, as well as the above-mentioned gear set 60. A planetary carrier 62 connected to the annular drum 56 for hydraulic servo via a plate clutch _C3 , a ring gear 63 connected to the input gear 5, and a carrier 62 rotatably supported,
It consists of a sun gear 61 and a planetary gear 64 meshing with a 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 29 of the annular piston 29.
Two notches 161 provided at predetermined positions of 1
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. The speed reduction device 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 a front case 125 of the idler gear chamber 8A. The idler gear 8, which is rotatably supported by a tapered roller bearing 82 mounted on a fourth shaft 81 fixedly installed between the rear case 142 and meshes with the output gear 71, and the tapered roller bearing 901 move the differential gear chamber 70A. The input gear 9 is formed on the rear outer periphery of a differential gear input section 701 that is rotatably supported within the input gear 701, and is configured to mesh with the idler gear 8. The differential device 70 is a differential gear 702
are attached to wheel axles 9A and 9B, which are the output shafts of the automatic transmission. Transmission 300, hydraulic control device 400 according to vehicle driving conditions such as vehicle speed, throttle opening, etc.
The clutches and brakes are engaged or released by the hydraulic pressure selectively outputted from the servo to each hydraulic servo, and four forward speeds or one reverse speed change is performed. First, three examples of the operation of each clutch, brake, and one-way clutch, and the achieved gear range and reduction ratio (RATIO) are shown below.
The results are shown in Table 2, Table 2, and Table 3, respectively.

【table】

【table】

[Table] In Tables 1, 2, and 3, 〇 indicates engagement.
△ indicates the engine brake, and × indicates the released state. As shown in Tables 1, 2, and 3 above, the rotation output from the output shaft 7 of the underdrive device 50 is controlled by the output gear 71, the idler gear 8, and the input gear 9 to a predetermined rotation speed. It is decelerated and transmitted to the differential device 70, and drives the wheel axles 9A and 9B, which are the output shafts of the automatic transmission 100, via the differential gear 702. Note that the present invention is not limited to the above-mentioned embodiments, and various modifications can be made based on the spirit of the present invention, and these are not excluded from the scope of the present invention.

[Brief explanation of the drawing]

FIG. 1 is a side view of the case of an automatic transmission according to the present invention, FIG. 2 is a sectional view showing the internal structure of the automatic transmission, and FIG. 3 is a skeleton diagram of the transmission of the automatic transmission. 1... Torque converter output shaft, 28... Annular cylinder for reverse, 29... Annular piston, 1
21...Torque converter housing, 122...
...Intermediate support wall which is a partition wall, 123...Cylindrical part, 1
23A...Spline groove, 130...Transmission case, 200...Torque converter,
300...Transmission, 400...Hydraulic control device, _B3 ...Multi-plate brake for reverse.

Claims (1)

[Claims] 1 a torque converter coaxially disposed on the output shaft of the engine; a first shaft coaxially disposed on the output shaft of the torque converter and extending rearward;
a first gear transmission disposed on a shaft;
a second shaft disposed parallel to the shaft; a second gear transmission disposed on the second shaft; and a second gear transmission disposed on the first shaft. a first gear connected to the output side; and a first gear disposed on the second shaft;
a second gear connected to the input side of the second gear transmission;
a chain connecting the first gear and the second gear at a position adjacent to the torque converter; a torque converter housing accommodating the torque converter to form a torque converter chamber; a transmission case that is disposed adjacent to the housing and that houses the transmission to form a transmission chamber; and a transmission case that is integrally formed with the torque converter housing and separates the torque converter chamber and the transmission chamber. A partition wall that
a cylindrical portion extending from the partition wall toward the transmission chamber and fitting into the transmission case;
A hydraulic servo disposed within the cylindrical portion and having the partition wall as a cylinder wall, and a frictional engagement that engages and disengages as a piston of the hydraulic servo moves and engages with an inner peripheral edge of the cylindrical portion by a spline. and a rotation preventing portion formed on the outer circumferential edge of the piston and engaged with the inner circumferential edge of the cylindrical portion, and a notch for arranging the chain is formed in the piston. An automatic transmission featuring: