JPH0158788B2 - - Google Patents

Description

[Detailed description of the invention]

(Industrial Application Field) The present invention relates to a clutch device for an automatic transmission for an automobile. (Prior art) In front-engine, front-drive automobiles, it is advantageous to place the engine horizontally, and it is also advantageous to arrange the automatic transmission so that its central axis extends in the width direction of the vehicle. preferable.
However, since there is a limit to the width of a vehicle, it is desirable that the axial length of the automatic transmission be as short as possible.
Therefore, Japanese Patent Application Laid-Open No. 57-1848 discloses an automatic transmission that uses a Ravignion type planetary gear unit, and also has a clutch device and a brake device arranged in layers in the radial direction, thereby shortening the axial length of the automatic transmission. machine is proposed. However, in conventional automatic transmissions including the automatic transmission described in this patent publication, the clutch drum of the clutch device used in the transmission is thick because it is made of cast iron. It was not possible to shorten the shaft length and make the structure more compact as desired, and it also had the drawbacks of being heavy. (Object of the Invention) Therefore, an object of the present invention is to provide a clutch device for an automatic transmission for an automobile that can shorten the shaft length without reducing strength and reduce the weight. be. (Structure of the Invention) A clutch device for an automatic transmission for an automobile according to the present invention includes two clutch devices, an inner and an outer clutch device, which are sequentially arranged in the radial direction with respect to an input shaft. The clutch device has inner and outer clutch drums, each made of sheet metal, connected to a common clutch hub portion, the inner clutch drum having a radially extending first portion and an outer end of the first portion. a second portion extending axially along the first portion of the inner clutch drum, the outer clutch drum comprising a first portion extending radially along the first portion of the inner clutch drum; a second portion radially outwardly of the portion and extending axially from the outer end of the first portion of the outer clutch drum in the same direction as the second portion of the inner clutch drum; A gap is provided between the first portion of the clutch drum and the first portion of the outer clutch drum to form an oil passage for operating oil of the outer clutch device. The passage is characterized in that the area of the passage is limited by welding at a plurality of locations in the circumferential direction of the two first parts. (Effects of the Invention) In the clutch device of the automatic transmission for automobiles having the above structure, both the inner and outer clutch drums of the inner and outer clutch devices arranged sequentially in the radial direction of the input shaft are made of sheet metal. As a result, it is possible to reduce the thickness of the clutch drum without reducing its strength, but rather improving it, which reduces the axial length of the clutch device and, by extension, the automatic transmission into which this clutch device is incorporated. The axial length of the machine can be reduced. Furthermore, the clutch drum is made of sheet metal, and a gap is provided between the first portions of the inner and outer clutch drums to serve as a passage for the operating oil of the outer clutch device. Therefore, it is not necessary to specially provide the passage, and therefore the structure of the clutch device and automatic transmission can be made compact and the weight can be reduced. Furthermore, since the passage of the operating oil is restricted by the welded joints in the circumferential direction of the two first parts, the operating oil is supplied to the outer clutch device by centrifugal force when unnecessary, and the outer clutch device is closed. This prevents the device from operating. (Embodiment) Hereinafter, one embodiment of a clutch device for an automatic transmission for an automobile according to the present invention will be described with reference to the drawings. FIG. 1 is a schematic diagram showing an automatic transmission for an automobile incorporating a clutch device according to an embodiment of the present invention. In FIG. 1, reference numeral 1 indicates a crankshaft of an engine (not shown) which is an input shaft, and a torque converter 2 and a multi-speed gearing device 10 are arranged coaxially with this crankshaft 1 in order from the engine side. . The torque converter 2 includes a pump 3, a turbine 4, and a stator 5,
The pump 3 is fixed to the crankshaft 1. The stator 5 is connected to a fixed shaft 7 integrally connected to the case 11 of the multi-speed gearing device 10 via a one-way clutch 6.
rotate on top. The one-way clutch 6 allows the stator 5 to rotate in the same direction as the pump 3, but does not allow it to rotate in the opposite direction. The multi-speed gear device 10 has a base end fixed to the crankshaft 1 and a distal end extending through the center of the multi-speed gear device to drive an oil pump P disposed on the side wall of the device. It has a central shaft 12 connected to the pump. On the outside of this central shaft 12, a hollow turbine whose base end is connected to the turbine 4 of the torque converter 2, whose distal end extends to the side wall of the multi-speed gear unit 10, and is rotatably supported by the side wall. A shaft 13 is provided. A Ravigneau type planetary gear unit 14 is provided on the turbine shaft 13, and this planetary gear unit 14 is connected to a small diameter sun gear 15, and a large diameter sun gear 1 disposed on the side of the small diameter sun gear 15 far from the engine.
6, a long pinion gear 17, a short pinion gear 18, and a ring gear 19.
First and second clutch devices 20 and 21 are arranged in parallel on the side of the planetary gear unit 14 that is far from the engine. The first clutch device 20 connects and disconnects power transmission between the small diameter sun gear 15 and the turbine shaft 13 via the first one-way clutch 22. On the other hand, the second clutch device 21 is connected in parallel with the first clutch device 20 to connect and disconnect power transmission between the small diameter sun gear 15 and the turbine shaft 13. A first brake device 2 is disposed radially outwardly of the second clutch device 21.
3 is placed. This first brake device 2
3 is a band brake, which includes a brake drum 23a connected to the large-diameter ungear 16 and a brake band 23b hung on the brake drum.
has. radially outward of the first clutch device 20 and the first brake device 2
A third clutch device 24 is disposed on the side of the first brake device 23, and this third clutch device 24 is connected to the brake drum 23a of the first brake device 23.
The power transmission between the large-diameter sun gear 16 and the turbine shaft 13 is switched on and off through the . A carrier 14a of the planetary gear unit 14 and a case 10a of the multi-speed gear device 10 are arranged radially outwardly of the planetary gear unit 14.
A second brake device 25 is arranged to engage and disengage the. The first and second brake devices 23
and 25, a second one-way clutch device 26 is disposed in parallel with the second brake device 25 for engaging and disengaging the carrier 14a and the case 10a. On the engine side side of the planetary gear unit 14, a carrier 14a of the planetary gear unit and the turbine shaft 13 are arranged.
a fourth clutch device 2 for intermittent power transmission between
7 is placed. This fourth clutch device 2
An output gear 28 connected to a ring gear 19 is arranged on the side of the engine 7 on the engine side. In addition, the reference numeral 29 in the figure indicates the turbine shaft 1.
3 shows a lock-up clutch for directly connecting the crankshaft 1 to the crankshaft 1 without going through the torque converter 2. Next, with reference to FIG. 2, the structure of each of the above-mentioned devices constituting the automatic transmission will be explained. Second Clutch Device 21 This second clutch device 21 is spline-coupled to the turbine shaft 13 and includes a clutch drum 21a having a substantially U-shaped cross section. , a clutch hub 21c is disposed, and this clutch hub 21c is integrally supported by a support portion 21d splined to the small diameter sun gear 15. The clutch drum 21a and clutch hub 21c are connected to alternately arranged clutch plates 21e and clutch discs 21b by gas splines, respectively. clutch drum 21a
Fitted inside the clutch drum 21a is a piston 21f having a shape corresponding to the contour of the inner wall of the clutch drum 21a and having a substantially U-shaped cross section. This piston 2
A hydraulic oil chamber 21g is formed between 1f and the drum 21a, and by controlling the supply of hydraulic oil to this hydraulic oil chamber 21g, the clutch plate 21a and the clutch disk 21b are pushed.
Alternatively, the second clutch device 21 can be engaged and disengaged by releasing the clutch. In addition, as is clear from the figure, the support portion 2 of the clutch hub 21c
The base portion 1d constitutes the inner race of the first one-way clutch 22. First clutch device 20 Piston 21f of the second clutch device 21
also serves as the clutch drum 20a of the first clutch device 20. A clutch hub 20c is disposed inside the clutch drum 20a, and the clutch hub 20c has a support portion 2 that forms the outer race of the one-way clutch 22 at its base.
It is integrally supported by 0d. The clutch drum 20a and clutch hub 20c are spline-coupled with alternately arranged clutch plates 21e and clutch discs 21b, respectively. A piston 20f is fitted inside the clutch disk 20a.
A hydraulic oil chamber 20 is provided between f and the clutch drum 20a.
g is formed. By controlling the supply of hydraulic oil to the hydraulic oil chamber 20g, the clutch plate 21e and the clutch disk 21b are pushed or released, and the first clutch device 2
0 engagement and disengagement. In the figure, reference numeral 20b indicates a return spring for the pistons 20f, 21f of the first and second clutch devices 20, 21. Third Clutch Device 24 The third clutch device 24 includes a substantially U-shaped clutch drum 24a that is integral with the clutch drum 21a. A clutch hub 24c is disposed inside the clutch drum 24a, facing the clutch drum 24a.
4c is formed by an extension of the brake drum 23a of the first brake device 23. The clutch drum 24a and the clutch hub 24c are spline-coupled with alternately arranged clutch plates 21d and clutch disks 21b. A piston 24e is fitted inside the clutch drum 24a.
A hydraulic oil chamber 24 is located between the clutch drum 24a and the clutch drum 24a.
f is formed. By controlling the supply of hydraulic oil to the hydraulic oil chamber 24f, the clutch plate 24d and the clutch disk 21b are pressed or released, and the third clutch device 24 is engaged or disengaged. It's becoming like that. This third clutch device 24 is equipped with a diaphragm-type return spring 24g for the piston 24e. The reason why a diaphragm type return spring is used in this third clutch device 24 is that this diaphragm type is thin and does not require a large space. Fourth clutch device 27 This fourth clutch device 27 is spline-coupled to the turbine shaft 13 and has a supported clutch drum 27a having a substantially U-shaped cross section.
It is equipped with A clutch hub 27c is disposed inside the clutch drum 27a, and the clutch hub 27c is supported by the carrier 14a of the planetary gear unit 14. The clutch drum 27a and the clutch hub 27c
are connected by gas spline to clutch plates 27d and clutch discs 27b, which are arranged alternately, respectively. A piston 27e formed by sheet metal processing is fitted inside the clutch drum 27a. A hydraulic oil chamber 27f is formed between the piston 27e and the clutch drum 27a, and by controlling the supply of hydraulic oil to the hydraulic oil chamber 27f, the clutch plate 27d
The fourth clutch device 27 is engaged and disengaged by pressing or releasing the clutch disk 27b. This fourth clutch is also provided with a diaphragm type return spring 27g, similar to the third clutch device 24 described above. First Brake Device 23 The brake drum 23a of the first brake device 23 is supported by a support portion 23c that is integrally supported by the large diameter sun gear 16. Therefore, when this first brake device 23 operates,
The large diameter sun gear 16 is fixed. Second brake device 25 This second brake device 25 is a disc type brake, and its brake drum 25a
is the carrier 14a of the planetary gear unit 14.
It is supported by a support portion 25b that is integrally fixed to the support portion 25b. Therefore, this second brake device 2
3 is activated, the carrier 14a is fixed. Below, Figure 3 is a partially enlarged view of Figure 2, and Figure 4 shows the clutch disc of the third brake device.
The clutch device for an automatic transmission according to the present invention will be explained with reference to FIGS. FIG. 3 shows an enlarged cross-section of the clutch drum 21a of the second clutch device 21 and the clutch drum 24a of the third clutch device 24. As shown, a clutch drum 21a of a second clutch device 21, which is an inner clutch device, and a third clutch device 24, which is an outer clutch device.
The clutch drum 24a is formed from a metal plate and has a U-shaped cross section. The clutch drum 21a is included in a clutch drum 24a having a larger diameter, and its end portion is connected and attached to a common clutch hub portion 20k. In the cross section shown in FIG. 3, the turbine shaft 1, which is the input shaft,
Portions where the clutch drums 21a and 24a face each other in three directions are joined by welding. FIG. 4 is a plan view of the clutch drum 24a of the third clutch device 24, FIG. 5 is a cross-sectional view taken along the line "--" in FIG. 4, and FIG. 6 is a cross-sectional view taken "--" shown in FIG. As shown in these figures, the outer peripheral edge of the clutch drum 24a is provided with the clutch drum 24a.
Almost trapezoidal protrusions 24b slightly protruding in the direction of 1a are arranged at intervals of 90 degrees in the circumferential direction,
This protruding portion is welded to the clutch drum 21a, and an oil passage 24j is formed in the other portion. This oil passage 24j is
It is desirable to provide protrusions 24i between the trapezoidal protrusions for the purpose of narrowing the passage, since the narrower the passage, the less malfunctions caused by centrifugal force occur and the amount of oil required is small. As explained in detail above, in the clutch device of the automatic transmission for automobiles of the present invention, one clutch device is located radially inward of the input shaft with respect to the other clutch device, and the clutch device is located outwardly. An oil passage for operating the clutch device is secured, and the area of the oil passage can be reduced by welding parts of the clutch drums of the inner and outer clutch devices to each other. , centrifugal force is prevented from actuating the outer clutch device. Furthermore, since the volume of the oil passage formed between the inner and outer clutch drums is reduced, the amount of oil that operates the outer clutch device is reduced, and the load on the engine is reduced. Furthermore, since the clutch drum is formed from a metal plate, the clutch drum can be made thinner and the axial length of the automatic transmission can be shortened, making it possible to install it in smaller vehicles. Become. It is also possible to reduce weight and improve the rigidity and strength of the clutch drum.

[Brief explanation of drawings]

FIG. 1 is a schematic diagram showing an automatic transmission using the clutch device of the automatic transmission for automobiles according to the present invention, and FIG. 2 is a detailed diagram showing the structure of the automatic transmission shown in FIG. 1. An axial sectional view, FIG. 3 is a partially enlarged view of FIG. 2, FIG. 4 is a plan view of the clutch drum of the third clutch device, and FIGS.
They are - and - sectional views of the figure, respectively. 1...Crankshaft, 2...Torque converter,
10... Multi-speed gear device, 12... Central shaft, 1
3...Turbine shaft, 14...Planetary gear unit, 15...Small diameter sun gear, 16...Large diameter sun gear, 17...Long pinion gear, 18
...Short pinion gear, 19...Ring gear, 20...First clutch device, 20a...Clutch drum, 21...Second clutch device, 2
2...First one-way clutch device, 23...
First brake device, 24...Third clutch device, 24a...Clutch drum, 25...Second brake device, 26...Second one-way clutch, 27...Fourth clutch device, 28... ...Output gear.

Claims (1)

[Claims] 1 Two clutch devices, an inner and an outer clutch device, arranged in sequence in the radial direction with respect to the input shaft, the inner and outer clutch devices each having a sheet metal inner clutch connected to a common clutch hub portion. and an outer clutch drum, the inner clutch drum having a first radially extending portion and a second portion extending axially from an outer end of the first portion; a first portion extending radially along the first portion of the inner clutch drum, and radially outwardly of the second portion of the inner clutch drum and extending radially along the first portion of the outer clutch drum. a second portion extending from an outer end of the first portion in the same direction as the second portion of the inner clutch drum;
A space is provided between the first part of the outer clutch drum and the first part of the outer clutch drum to form an oil passage for operating oil of the outer clutch device. A clutch device for an automatic transmission for an automobile, characterized in that a passage area is limited by welding at a plurality of circumferential locations of a first portion.