JPH0246813B2 - - Google Patents

Description

[Detailed description of the invention]

(Industrial Application Field) The present invention relates to a gear transmission of an automatic transmission installed in an automobile, in particular, to a second transmission attached to the front or rear of a first transmission having a plurality of forward gears. This invention relates to a gear transmission for an automatic transmission. (Prior Art) Conventionally, an automatic transmission that enables shifting of four forward speeds by adding a second transmission to the rear of a first transmission that has three forward speeds has a first transmission and a first transmission. The two transmissions are housed in independent cases, and the output shaft of the first transmission is placed in the case housing the first transmission.
The output shafts of the second transmission are each supported by a case housing the second transmission. The pressure oil supply oil passage to the frictional engagement element of the first transmission is provided in a case housing the first transmission, and the pressure oil supply oil passage to the frictional engagement element of the second transmission is provided in the case housing the first transmission. It is provided in a case that houses a two-speed transmission (US Pat. No. 3,797,332). (Problems to be Solved by the Invention) However, in the gear transmission device of the automatic transmission having the above configuration, since the first transmission and the second transmission are housed in independent cases, the case In addition to complicating the installation, the pressure oil supply passages to the friction engagement elements of the first and second transmissions are provided in separate cases, making the structure of the pressure oil supply passages complicated. This not only makes it difficult to perform a smooth gear shifting operation, but also increases the axial dimension of the automatic transmission, which impairs its mountability in an automobile. Therefore, a method can be considered in which the first transmission and the second transmission are housed in an integrated case, but in that case, a hydraulic servo is used to engage and disengage the frictional engagement elements of the first transmission and the second transmission. An intermediate support wall must be provided between the first transmission and the second transmission. However, when an intermediate support wall is provided, a cylindrical part that extends in the axial direction is required in the portion where the intermediate support wall surrounds the transmission shaft, and the size of the automatic transmission increases by the length of the cylindrical part. Become. The present invention solves the problems of the conventional gear transmission of an automatic transmission, and accommodates the first transmission and the second transmission of the automatic transmission in an integrated case, which enables shifting of four forward speeds. A gear for an automatic transmission that simplifies case installation, simplifies the structure of the pressure oil supply oil passage, enables smooth gear shifting, and reduces the axial dimension of the automatic transmission. The purpose is to provide a transmission. (Means for Solving the Problems) For this purpose, in the gear transmission device of the automatic transmission of the present invention, an intermediate support wall is formed radially inward from the transmission case, and a center A hole is formed. A central cylindrical portion is formed at the periphery of the center hole, and a peripheral cylindrical portion is formed at the periphery of the intermediate support wall. An annular cylinder constituting the hydraulic servo of the brake is formed on one surface of the intermediate support wall facing the first transmission, and an annular cylinder constituting the hydraulic servo of the brake is formed on the other surface facing the second transmission. A clutch drum is formed. A stepped portion having a large diameter is formed on the first transmission side of the center hole, and a sleeve is fitted outside the stepped portion. An eccentric notch is formed in the center hole, and an oil chamber is formed between the center hole and the sleeve. The piston of the brake has a friction plate pressing portion on the outer circumferential side that protrudes beyond the cylinder sliding portion on the inner circumferential side, and the ring gear of the first transmission is spline-fitted with the output shaft of the first transmission within the stepped portion. are doing. Pressure oil is supplied to the brakes of the first transmission through an oil passage provided in the transmission case, an oil passage provided radially on the intermediate support wall, and an oil passage provided axially on the intermediate support wall. Pressure is supplied to the clutch of the second transmission through an oil passage provided in the transmission case, an oil passage provided radially in the intermediate support wall, and the eccentric notch. It will be done. In the brake, the cylinder sliding part on the inner circumferential side of the piston is shorter than the friction plate pressing part on the outer circumferential side, and the oil passage provided in the axial direction in the intermediate support wall has a large passage cross section. Further, the intermediate support wall is fixed by bolts extending in the axial direction from the transmission case into the intermediate support wall, and is attached to the inner wall of the transmission case by clips on both end surfaces of the peripheral cylindrical portion of the intermediate support wall. Fixed. (Operations and Effects of the Invention) According to the present invention, as described above, the intermediate support wall is formed radially inward from the transmission case, the center hole formed in the intermediate support wall, and the center hole formed in the intermediate support wall. A central cylindrical part formed on the periphery of the hole, a peripheral cylindrical part formed on the periphery of the intermediate support wall, and a brake hydraulic pressure formed on one surface of the intermediate support wall facing the first transmission. an annular cylinder constituting a servo, a clutch drum supported by the outer circumferential portion of the central cylindrical portion on the other surface of the intermediate support wall facing the second transmission, and a clutch drum formed on the first transmission side of the center hole. a step portion having a large diameter; a sleeve fitted to a portion other than the step portion of the center hole; and an eccentric notch provided in the center hole and forming an oil chamber between the sleeve and the center hole; In the brake piston, the friction plate pressing part on the outer circumferential side protrudes beyond the cylinder sliding part on the inner circumferential side, and the ring gear of the first transmission is spline-fitted with the output shaft of the first transmission within the step part. Pressure oil is supplied to the brake of the first transmission through an oil passage provided in the transmission case, an oil passage provided radially in the intermediate support wall,
Pressure is supplied to the clutch of the second transmission via an oil passage provided in the axial direction on the intermediate support wall, and pressure is supplied to the clutch of the second transmission through an oil passage provided in the transmission case and provided in the radial direction on the intermediate support wall. The intermediate support wall can accommodate the first transmission and the second transmission, and the oil passage for supplying oil to the hydraulic servo of both transmissions can be installed by the intermediate support wall. It becomes possible to form channels in the intermediate support wall. Therefore, the structure of the oil passage is simplified and the transmission can be operated smoothly. In addition, a stepped portion is formed on the inner circumferential side of the central cylindrical portion of the intermediate support wall, and the ring gear and output shaft of the first transmission are spline-fitted within the stepped portion, so that Dimensions can be reduced. Further, in the brake, the cylinder sliding portion on the inner circumferential side of the piston is formed shorter than the friction plate pressing portion on the outer circumferential side, thereby reducing the axial dimension. and,
Since the oil passage provided in the axial direction in the intermediate support wall has a large passage cross section, the dynamic pressure applied by the supplied oil to the surface of the piston is reduced, so that the oil passage on the inner peripheral side of the piston is By shortening the cylinder sliding portion, it is possible to prevent the piston from operating in an inclined state. The intermediate support wall is fixed by bolts extending in the axial direction from the transmission case into the intermediate support wall, and is attached to the inner wall of the transmission case by clips at both end surfaces of the peripheral cylindrical portion of the intermediate support wall. Since it is fixed, sufficient space for the oil passage can be taken within the intermediate support wall.
The axial dimension can be reduced. (Example) Hereinafter, an example of the present invention will be described in detail with reference to the drawings. FIG. 1 is a sectional view of a gear transmission of an automatic transmission showing an embodiment of the present invention, FIG. 2 is a right side view of an intermediate support wall, FIG. 3 is a sectional view taken along line DD in FIG. The figure is a sectional view taken along the line AA in FIG. 2, and FIG. 5 is a sectional view taken along the line BB in FIG. 4. In FIG. 1, a hydraulic torque converter case A and a transmission case 10 disposed adjacent thereto are fastened together, the transmission case 10 is open on the torque converter side, and the rear wall 110 has an output shaft hole. 11 are provided. A gear transmission 2 is disposed between the torque converter 1 and a propeller shaft (not shown), and a hydraulic control device 3 for the gear transmission 2 is disposed below the transmission case 10. The torque converter 1 is housed in a torque converter case A, and includes a pump impeller 4 connected to the crankshaft of the engine, a stator 7 connected to a fixed part 6 via a one-way clutch 5, and a turbine runner 8. We are prepared. The gear transmission 2 is housed in a cylindrical transmission case 10 having a side wall 110 with an open end 100 and an output shaft hole 11 at the rear, and is arranged on the open side of the transmission case 10. Ru. The gear transmission 2 is arranged on the opening side of the transmission case 10 and has an input shaft 14.
A first transmission or underdrive device 12 connected to the transmission case, a second transmission or overdrive device 13 connected to the output shaft 50 provided on the side wall 110, and an intermediate position between the two devices and the transmission case. The intermediate support wall 6 is sandwiched and fixed to the inner wall 10B of 10 with clips 121 and 122.
0, and an intermediate shaft 40 which is pivotally supported by the intermediate support wall 60, serves as an output shaft of the underdrive device 12, and transmits power to the overdrive device 13. The input shaft 14 of the underdrive device 12 is
It extends coaxially with the crankshaft and is connected to the turbine runner 8 . Further, the underdrive device 12 includes first and second planetary gear devices 15, 16 and clutch devices 23, 2.
4. Brake devices 25, 35, 37 and one-way clutches 34, 36 are provided. The first planetary gear device 15 includes a sun gear 17, a planetary pinion 18, a ring gear 19, and a carrier 20 that rotatably supports the planetary pinion 18. The clutch device 23 is operated by a hydraulic servo 23A formed in a drum 79 connected to the input shaft 14, and controls the connection between the input shaft 14 and the ring gear 19. Further, the clutch device 24 is connected to the intermediate shaft 40 via a drum-shaped coupling mechanism 80, and is equipped with a hydraulic servo provided in a drum 81 supported by a central cylindrical portion 521 formed in the pump cover 52. 24A, and controls the connection between the input shaft 14 and the sun gear shaft 27 coupled to the sun gear 17. The brake device 35 is operated by an annular hydraulic servo 35A provided on the inner wall 10B of the transmission case 10, and controls the connection between the gear shaft 27 and the transmission case 10. The second planetary gear device 16 includes a sun gear 30, a planetary pinion 31, a ring gear 32, and a carrier 33 that rotatably supports the planetary pinion 31. The sun gear 30 is connected to a sun gear shaft 27, and a one-way clutch 34 and the brake device 35 are provided in series between the sun gear shaft 27 and the transmission case 10. Carrier 33 and transmission case 10
A one-way clutch 36 and a brake 37 operated by a hydraulic servo 37A provided on the torque converter side of the intermediate support wall 60 are provided in parallel with each other. One way clutch 3
4 and 36 are arranged concentrically in the radial direction, that is, so as to overlap in the axial direction. A hollow intermediate shaft 4 extending to the center of the gear transmission 2
0 is pivotally supported on one side by the intermediate support wall 60, and on the other hand is pivotally supported in a shaft hole 11 formed in a side wall 110 of the transmission case 10 via an output shaft 50, and is coaxial with the input shaft 14. It is placed according to the The intermediate shaft 40 is spline-fitted to the carrier 20 and the ring gear 32 to transmit power from the underdrive device 12 to the overdrive device 13. A hollow portion 401 of the intermediate shaft 40 communicates with a radial lubricating oil supply hole 402 provided at a predetermined position. The overdrive device 13 is a planetary gear device 4
1. It is equipped with a clutch device 48, a brake device 49, and a one-way clutch. The planetary gear device 41 includes a sun gear 42, a planetary pinion 43, a ring gear 44, and a carrier 45 that rotatably supports the planetary pinion 43. The carrier 45 is the intermediate shaft 40
The clutch 48 is connected to the sun gear 42 and is connected to the central cylindrical portion 61 of the intermediate support wall 60.
The clutch drum 82 is rotatably supported by a hydraulic servo 48A provided in the clutch drum 82 to control the connection between the carrier 45 and the sun gear 42. The brake device 49 is operated by a hydraulic servo 49A composed of an annular hydraulic cylinder 102 formed around the shaft hole 11 in the side wall of the transmission 1, and an annular piston 103 fitted into the annular hydraulic cylinder 102. , controls the connection between the sun gear 42 and the transmission case 10. The ring gear 44 corresponds to the output shaft of the gear transmission 2 and the overdrive device 13;
An output shaft 50 supported via an iron bearing 70 fitted in a shaft hole 11 of the transmission case is integrally connected to the output shaft 50 . One-way clutch 54 controls the connection between carrier 45 and sun gear 42 . Table 1 shows the relationship between the operation of the gear transmission and the operation of the clutch, brake and one-way clutch.

[Table] In this table, the numbers 23, 24, ..., 54 are the numbers of the illustrated clutch device, brake device, and one-way clutch, and 0 indicates that the clutch device and brake device are in the engaged state. , △ means that the one-way clutch is in the engaged state when the engine is running. A transmission case 10 is located between the torque converter 1 and the underdrive device 12.
Transmission cover 5 that covers the opening of
1 is fastened, a pump cover 52 is fastened to the underdrive device side of the cover 51, and an oil pump 9, which is a hydraulic pressure source, is installed in the middle.
Hydraulic pressure for operating each clutch device and brake device and hydraulic oil for a hydraulic torque converter are supplied via a hydraulic control device 3. The intermediate support wall 60 has a center hole 64 and a center hole 6
4, a central cylindrical portion 61 integrally formed around the intermediate support wall 60, and a peripheral cylindrical portion 62 formed at the peripheral edge of the intermediate support wall 60.
It has An annular cylinder 63 constituting a hydraulic servo of the brake 37 is formed on the underdrive device 12 side of the intermediate support wall 60, and an outer periphery 61a of the central cylindrical portion 61 on the overdrive side is connected to the hydraulic servo drum 82 of the clutch 48. It constitutes a bearing. An eccentric notch 65 is formed in the center hole 64, and a sleeve 66 constituting a metal bearing is fitted therein, and an oil chamber is formed between the eccentric notch 65 and the sleeve 66. Inside the intermediate support wall 60 is a radius connecting the output hydraulic pressure port 101 of the hydraulic pressure output from the hydraulic control device 3 formed on the lower wall of the transmission case 10 and the eccentric notch 65 of the center hole 64. Further, the eccentric notch 65 communicates with the hydraulic servo 48A via a radial oil passage 68 provided in the central cylindrical part 61. The hydraulic oil supplied through the output hydraulic port 101 is supplied to the oil passage 67,
Hydraulic servo 4 via eccentric notch 65 and oil passage 68
8A is supplied and discharged. Further, within the supporting wall 60, an oil passage 1 is provided from the hydraulic control device 3 through the transmission case.
An oil passage 69 for supplying and discharging hydraulic oil to and from the hydraulic servo 37A is formed through the hydraulic servo 37A. The oil passage 69
is connected to an oil passage 102 formed in the transmission case 10, extends radially within the intermediate support wall 60, is connected to a cast hole extending axially within the intermediate support wall 60, and is connected to the hydraulic servo 37A. It leads to the oil room. The cross section of the cast hole is large, and the pressure applied to the hydraulic servo 37A is static pressure, so that the piston of the hydraulic servo 37A can move smoothly. In addition, the underdrive device 1 of the center hole 64
A stepped portion having a larger diameter than the center hole 64 is formed on the second side. In the center hole 64 other than the stepped portion,
The sleeve 66 is fitted. In the piston of the brake 37, the friction plate pressing portion on the outer periphery protrudes from the cylinder sliding portion (return spring arrangement portion) on the inner periphery.
That is, the piston has a smaller axial dimension on the inner peripheral edge side. As mentioned above, the pressure oil supplied through the oil passage 69 and the cast hole applies static pressure to the piston, so that the piston can slide stably in the cylinder 63 even if the axial dimension on the inner peripheral edge side is small. Can perform dynamic movements. Furthermore, since the ring gear 32 of the second planetary gear device 16 is spline-fitted to the output shaft 40 within the stepped portion, the central cylindrical portion 61 and a portion of the spline-fitting portion overlap in the axial direction. is arranged,
The axial dimension can be reduced. As shown in FIG. 5, the intermediate support wall 60 is fixed to the transmission case 10 with bolts, and its movement in the circumferential direction is restricted. Further, the movement in the axial direction is restricted by the clips 121 and 122 as described above.
Furthermore, since the structure for fixing the intermediate support wall 60 is simplified, a sufficient space for the oil passage can be taken inside the intermediate support wall 60, and the structure of the pressure oil supply oil passage is simplified. Therefore, the transmission can be operated smoothly.

[Brief explanation of the drawing]

FIG. 1 is a sectional view of a gear transmission of an automatic transmission showing an embodiment of the present invention, FIG. 2 is a right side view of an intermediate support wall, FIG. 3 is a sectional view taken along line DD in FIG. The figure is a sectional view taken along the line AA in FIG. 2, and FIG. 5 is a sectional view taken along the line BB in FIG. 4. 1... Torque converter, 2... Gear transmission, 3... Hydraulic control device, 9... Oil pump,
10... Transmission case, 12... Underdrive device, 13... Overdrive device, 32... Ring gear, 37... Brake,
40... Intermediate shaft, 60... Intermediate support wall, 61... Center cylindrical part, 61a... Outer peripheral part, 62... Peripheral cylindrical part, 63... Annular cylinder, 64... Center hole, 6
5...Eccentric notch, 66...Sleeve, 67,6
9, 101, 102...Oil path, 82...Drum.

Claims (1)

[Scope of Claims] 1. An intermediate support wall formed radially inward from the transmission case, a center hole formed in the intermediate support wall, and a central cylindrical shape formed around the periphery of the center hole. a peripheral cylindrical part formed on the peripheral edge of the intermediate support wall; an annular cylinder formed on one surface of the intermediate support wall facing the first transmission and forming a hydraulic servo of the brake; a clutch drum supported by the outer circumferential portion of the central cylindrical portion on the other surface of the intermediate support wall facing the transmission; and a stepped portion having a large diameter formed on the first transmission side of the center hole;
The brake piston has a sleeve that is fitted in a part other than the stepped part of the center hole, and an eccentric notch that is provided in the center hole and forms an oil chamber between the sleeve and the sleeve. The friction plate pressing portion protrudes from the cylinder sliding portion on the inner circumferential side, and the ring gear of the first transmission is located within the step portion.
It is spline-fitted to the output shaft of the transmission, and the first
Pressure oil is supplied to the brakes of the transmission through an oil path provided in the transmission case, an oil path provided radially in the intermediate support wall, and an oil path provided axially in the intermediate support wall. Further, pressure is supplied to the clutch of the second transmission through an oil passage provided in the transmission case, an oil passage provided radially in the intermediate support wall, and the eccentric notch. A gear transmission device for an automatic transmission characterized by: 2. In the brake, the cylinder sliding part on the inner circumferential side of the piston is shorter than the friction plate pressing part on the outer circumferential side, and the oil passage provided in the axial direction in the intermediate support wall has a large passage cross section. Said claim 1
A gear transmission device for an automatic transmission as described in . 3. The intermediate support wall is fixed by bolts extending in the axial direction from the transmission case into the intermediate support wall, and is also fixed to the inner wall of the transmission case by clips at both end surfaces of the peripheral cylindrical portion of the intermediate support wall. A gear transmission device for an automatic transmission according to claim 1 or 2.