JPH0226100B2 - - 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 or making them smaller and lighter. In addition, multi-stage automatic transmissions for F-F cars are small, lightweight, and easy to install, especially for F-F cars with transverse engines.
Automatic transmissions for F vehicles are required to have a short overall length with a shortened axial dimension. 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 reduction gear device receiving the output of the transmission are arranged on the second shaft, and both shafts are arranged in parallel. (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 all the parts are arranged on one shaft. Therefore, 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, a partition wall is provided between the torque converter housing and the transmission case to separate the torque converter chamber and the transmission chamber, but the frictional engagement elements that make up the transmission are used to operate the hydraulic servo. When engaged, a thrust force is generated that acts to separate the torque converter housing and transmission case or the transmission case and the bulkhead. As a result, it becomes difficult to provide a sufficient oil seal between the torque converter housing and the transmission case. The present invention solves the above-mentioned problems of the conventional automatic transmission, prevents the axial dimension of the transmission case from increasing due to the frictional engagement element incorporated in the transmission case, and prevents the frictional engagement element from increasing. The capacity of the coupling element can be increased, and it is possible to prevent insufficient sealing between the torque converter housing and the transmission case due to the trust force generated when the friction engagement element operates. The purpose is to provide automatic transmissions. (Means for Solving the Problems) For this purpose, the automatic transmission housing of the present invention includes a torque converter housing forming a torque converter chamber for accommodating a torque converter, and a torque converter housing disposed adjacent to the torque converter housing. The transmission case also has a transmission case which forms a transmission chamber for accommodating a transmission. 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. It is formed. Further, a frictional engagement element, in particular a hydraulic servo of a reverse brake, is formed in the cylindrical portion adjacent to the partition wall, and a frictional engagement plate that is engaged and disengaged by the hydraulic servo is located inside the cylindrical portion. The cylindrical portion is fitted into a spline groove formed in the cylindrical portion, and is disposed opposite to the regulating means fixed to the cylindrical portion on the opposite side from the hydraulic servo. (Operations and Effects of the Invention) According to the present invention, there is provided a torque converter housing which accommodates a torque converter and forms a torque converter chamber as described above, and a torque converter housing which is disposed adjacent to the torque converter housing and which is arranged adjacent to the torque converter housing. a transmission case that accommodates a transmission chamber to form a transmission chamber; 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: Since the cylindrical portion is formed to extend toward the transmission chamber and fit into the transmission case, the torque converter housing can be sufficiently positioned with respect to the transmission case. Further, a frictional engagement element, in particular a hydraulic servo of a reverse brake, is formed in the cylindrical portion adjacent to the partition wall, and a frictional engagement plate that is engaged and disengaged by the hydraulic servo is located inside the cylindrical portion. The partition wall is fitted into the formed spline groove and is disposed facing the regulating means fixed to the cylindrical portion on the opposite side from the hydraulic servo, so that the cylinder of the frictional engagement element is constituted by the partition wall. can do. Therefore, 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. Furthermore, since the thrust force generated when oil is supplied to the hydraulic servo of the friction engagement element is applied to the same cylindrical part, the torque converter housing and transmission case may be separated by the thrust force. , and a sufficient seal between the two can be ensured. In particular, when the frictional engagement element is a reverse brake, high reverse pressure is supplied to the hydraulic servo, but since the thrust force is absorbed by the cylindrical portion, the influence of the reverse pressure is prevented. be able to. (Example) Hereinafter, an example of the present invention will be described in detail with reference to the drawings. FIG. 1 is an external side view of the automatic transmission of the present invention, FIG. 2 is a diagram showing its internal structure, and FIG. 3 is a skeleton diagram of the 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 operated by a hydraulic servo, one multi-disc brake B ₄ and one one-way clutch F ₃ . The underdrive device 50 includes a differential device 70, an output gear 71 of the underdrive device, a differential device 70, an input gear 9, and an idler gear room 8.
A deceleration device 80 composed of the following is connected. 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 cylindrical part 123, which is a cylindrical transmission front case, provided at the rear of the torque converter housing 121 and separated by a partition between the torque converter chamber 200A and the transmission chamber 300A, that is, an intermediate support wall 122; Front cases 124, 125, and 126 are integrally formed with the output gear 71, idler gear 10, and differential device 70 of the underdrive device that are continuously adjacent to the side of the converter housing 121, respectively. The rear housing, that is, the transmission case 130 is the cylindrical front case 1.
23 and torque converter housing 12
a transmission rear case 131 connected to the rear end of the transmission device 1 and having a cylindrical rear side wall 132;
The cylindrical rear wall 1 is continuously adjacent to the side of 31.
Case 138 of an underdrive device having 34
and rear cover 135 of differential gear and rear case 1
31 and a case 133, and is integrally formed with a hydraulic control device cover connecting portion 136 having an opening at the top (left side in FIG. 2). The bearing retainer 140 includes rear cases 141, 142, and 143 integrally formed 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 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 170A 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. Torque converter 200 has front cover 20
1, a turbine runner 203 connected to the output shaft 1 through a turbine hub, and a one-way clutch 204 fitted into the center hole 122A of the intermediate support wall 122. It consists of a stator 206 engaged with a tubular fixed shaft, that is, a stator shaft 205, and a direct coupling clutch 207 connected to a turbine hub, and is installed in a torque converter case 121. The oil pump 90 has a cylindrical projection 95 provided around the outer peripheral side of the torque converter side of the intermediate support wall, that is, the partition wall 122, and an annular space formed between the fixed shafts 205, that is, the pump body fitting portion 9.
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. Further, the annular thin plate 92 prevents wear of the pump gear, and also serves to prevent the partition wall 122 from wearing.
Oil passage groove 9 formed on the side of the torque converter
7 is closed 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.
The cylindrical fixed shaft 20 is attached to the central rear surface of the partition wall 122.
The rear center support 11 and the coaxial front support 12 are fixed rearward. 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. A first intermediate shaft 2 is rotatably mounted, a cylindrical sun gear shaft 3 is rotatably mounted on the outside thereof, and the front center support 12 is spline-coupled with the tip of the first intermediate shaft 2. An output gear 4 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 is connected to the sun gear shaft 3.
A sun gear 31 formed at the rear end, a planetary gear set 30 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 C1, and a carrier 32. Rotatably supported on the shaft, sun gear 3
1 and a planetary gear 34 meshing with a ring gear 33. Center drum 21 and rear wall 13
2, an annular hydraulic servo rear drum 23 is rotatably fitted onto the rear center support 11.
is provided. 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 12 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 3, and an annular piston 27 is fitted into the front drum 26 so that the hydraulic servo b ₂ of the multi-disc brake B ₂ is activated. It is formed. On the inner surface of the cylindrical front case 123,
A spline groove 123A is formed, and the hydraulic servo
A multi-plate rake B ₂ is fitted in front of b ₂ , a one-way clutch F ₂ connected by an outer race FD is fitted in front of it, and a reverse multi-plate brake B ₃ is fitted in front of it. An annular reverse brake hydraulic cylinder 28 is formed by a cylindrical front case 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. An annular 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. Behind the multi-disc brake B ₃ above, 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 front case 123. Inside the brake B ₂ above, the sun gear shaft 3 is the inner race fa, and the outer race fd is the brake.
A one-way clutch _F1 is connected to the cylindrical front case 123 via _B2 , and a second planetary gear set 40 is provided in front of the one-way clutch _F1 . The second planetary gear set 40 includes a sun gear 41 formed at the tip of the sun gear shaft 3, and a one-way clutch.
A planetary carrier 42 connected to the inner race shaft fc of _F2 and connected to the cylindrical front case ₁₂₃ via a multi-plate brake B3, a ring gear 43 connected to the output gear 4, and the carrier 42 to be rotatable. Pivotally supported, sun gear 41 and ring gear 4
3 and a planetary gear 44 that meshes with the gear. The underdrive device chamber 50A has a rear wall 134
A forward-facing cylindrical rear center supporter 51 is protruded from the center of the rear case 141 of the output gear, and a rearward-facing cylindrical front center support 52 is protruded from the center of the rear case 141 of the output gear.
1 is rotatably supported by a tapered roller bearing 72 installed in the output gear chamber 71A, and a cylindrical second intermediate portion is provided on the outside of the rear side of the output shaft 7 and the rear center support 51. The shaft 6 is rotatably fitted onto the outside of the front center support 52.
An input gear 5 is rotatably supported. 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 is fitted with a tooth-shaped projection 541 that presses 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 drum 56 and the outer surface of the second intermediate shaft 6, thereby forming a multi-plate clutch.
A hydraulic servo C ₃ of C ₃ is formed, and an annular drum 5
6 is a multi-plate clutch formed within the outer peripheral wall 562
It is connected to the carrier 62 of the third planetary gear set 60 via _C3 , and is further connected to the cylindrical portion 561.
It is connected to the case 133 via a multi-disc brake _B4 formed on the outside. A third planetary gear set 60 is provided on the front side of the hydraulic servo _c3 ,
The third planetary gear set 60 is connected to the second intermediate shaft 6
A sun gear 61 formed at the tip of the output shaft 7 is spline-fitted to the multi-plate clutch.
A planetary carrier 62 connected to the annular drum 56 via _C3 , 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. Become. A chain 160 is provided between the output gear 4 of the transmission 10 and the input gear 5 of the underdrive device 50 in a driving manner, 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 9 and meshes 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 running conditions such as vehicle speed, throttle opening, etc.
The clutches and brakes are engaged or released by hydraulic pressure selectively outputted from the servo to each hydraulic servo, and four forward speeds or one reverse speed is achieved. 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 after being changed in speed is the output gear 71A, the idler gear 8
The rotation speed is reduced to a predetermined rotational speed by input gear 9 and transmitted to differential gear 70, which drives wheel axles 9A and 9B, which are output shafts of automatic transmission 100, via 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 drawings]

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 supporting wall which is a partition wall, 123...Cylindrical front case, 123A...Spline groove, 130...
Transmission case, 200...Torque converter, 300 Transmission, 400...
...Hydraulic control device, B ₃ ...Multi-disc brake for reverse.

Claims (1)

[Claims] 1. A torque converter housing that accommodates a torque converter and forms a torque converter chamber;
a transmission case disposed adjacent to the torque converter housing and accommodating a transmission to form a transmission chamber; a partition wall separating the torque converter chamber and the transmission chamber; A cylindrical part is formed integrally with the converter housing, and the partition wall is formed with a cylindrical part that extends toward the transmission chamber and fits into the transmission case. A hydraulic servo of the coupling element is formed, and a friction engagement plate that is engaged and disengaged by the hydraulic servo is fitted into a spline groove formed inside the cylindrical part, and is connected to the cylindrical part on the opposite side from the hydraulic servo. An automatic transmission characterized in that the automatic transmission is disposed opposite to a regulating means fixed to the. 2. The automatic transmission according to claim 1, wherein the friction engagement element is a reverse brake.