JPS60109618A - Clutch for automatic transmission of automobile - Google Patents

Abstract

PURPOSE:To reduce the axial length of a clutch, by making the inner and outer clutch drums of an inner and an outer clutch sections from metal plates and sequentially disposing the inner and the outer clutch sections in the radial direction of an input shaft. CONSTITUTION:Clutch drums 21a, 24a are made of metal plates, and fitted at the inner circumferential edges on the peripheral surface of a cylindrical inner clutch member 30 so that the drum 21a is located inside the other drum 24a. The radially extending disc-like portion of the clutch drum 24a is provided with a protrusion 24h extending toward the other clutch drum 21a and annularly and uniformly in the circumferential direction of the drum 24a to uniformly decrease the cross-sectional area of an oil passage 29 between both the drums. Since the strength of the clutch drums is heightened, their thickness can be reduced to diminish the axial length of a clutch.

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a clutch device for a private WJ transmission for an automobile.

(Prior art) In front-engine automobiles, it is advantageous to use an engine ve-device, and in line with this, the automatic transmission is also arranged so that its central axis is in the width direction of the vehicle. is preferred.

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, in Japanese Patent Application Laid-Open No. Sho Sku/g'1g, a Lavignon-type granular gear unit is used, and clutch devices and brake devices are arranged in layers in the radial direction, thereby reducing the length of the automatic transmission in the axle direction. A shortened automatic transmission has been proposed. However, in conventional automatic transmissions, including the automatic transmission @ described in this patent publication, w
! The clutch drum of the clutch device used in the transmission is made of cast metal and has thick walls, making it impossible to shorten the shaft length and make the structure compact. However, it had the disadvantage of being heavy.

(Object of the Invention) Therefore, it is an object of the present invention to provide a clutch device tube for an automatic transmission for automobiles, which can shorten the shaft length without reducing Th and reduce the weight. be.

(Structure of the Invention) The clutch device of the automobile 111f clutch device of 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 the input shaft. The clutch device has inner and outer clutch drums each made of sheet metal, the inner clutch drum having a radially extending first portion and an axially extending portion 11 extending from the outer end of the first portion. The outer clutch drum is comprised of two parts, a first part extending radially along the first s of the inner clutch drum, and a second part extending radially outward of the second part of the inner clutch drum. and a second fa portion extending in the axial direction from the outer end of the i/lti portion of the outer clutch drum, the first fa portion of the inner clutch drum and the i/lti portion of the outer clutch drum. The invention is characterized in that a gap is provided between m minutes to form an oil passage noise for operating oil of the outer clutch device.

(Effects of the Invention) In the clutch device for an automatic transmission for a self-contained vehicle 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. Therefore, it is possible to reduce the thickness of the clutch drum while improving its strength, 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, since the clutch drum is made of sheet metal, a gap has not been provided between the inner and outer clutch drums for the first s.
Since this is a passage for the operating oil of the all-outer clutch device, *) there is no need to provide a special IU, and therefore the structure of the clutch device and the automatic gearbox can be made into a single structure. At the same time, the weight can be completely reduced.

(1! Example) Hereinafter, one example of the 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 illustrating an automatic transmission system for an automobile in which a clutch device using a hydraulic force according to the present invention is incorporated.

In this diagram, the symbol l indicates the crankshaft of the engine (not shown), which is the input -11, and this crankshaft l
A torque converter 2 and a multi-speed gear unit 1 (+) are installed next to the engine from the engine side.The torque converter 2 is equipped with a cylinder f8, a turbine 4, and a stator 5. f8 is rotated by the crankshaft l.The stator 5 rotates on a fixed shaft 7 integrated with the case 11 of the multi-speed gearbox fl!1llo through a one-way clutch 6. The directional clutch 6 allows the stator 6 to rotate in the same direction as the bolt f8, but does not allow rotation in the reverse direction.

The multi-speed transmission gear system 10 has a base end fixed to the crankshaft l, a distal end extending through the center of the multi-speed gear system, and drives an oil pong 11' disposed on the side wall of the device. A corpse? It has a solid shaft 12 connected to a ring. On the outside of this solid shaft 12, a base end is connected to the turbine 4 of the torque converter 2, a distal end extends to the side wall of the multi-speed gear unit 10, and a rotatable shaft is rotatably supported by the side wall. A turbine shaft 1B is provided. On this turbine shaft 18, a Rapigno-type delanet gear unit 14 is provided, and this granite gear unit 14 is arranged on a small-diameter sun gear 15, and on the side of this small-diameter sun gear 15 far from the engine. It consists of a large-diameter sun gear 16, a long pinion gear 17, a short pinion gear 18, and a ring ear 19. The side force on the side far from the engine of this grain gear unit) 14 is connected to the first and second clutch devices 2 (
1 and 21 are arranged in parallel.

The first clutch device 20 connects and connects the power transmission pipe between the small diameter sun gear 15 and the turbine shirt 1B via the first one-way clutch 22. - The second clutch device 21 is in parallel with the first clutch device 1f20 and connects and disconnects power transmission between the small diameter sun gear 15 and the turbine shaft 1B. A first brake device 28 is electrically connected radially outward of the second clutch device 21 . This hunger
Brake equipment #28 is a band brake, and has a brake drum 288 connected to the large diameter sun gear 16 and a brake band 28b hooked around the brake drum. A third clutch device #N24 is arranged radially outward of the first clutch device 2() and on the side of the first brake device 28. The clutch device 24 is the first brake device 28
The power transmission between the large-diameter sun gear 16 and the turbine shaft 1B is performed on and off through the brake drums 2, 8a and 8a.

Radially outward of the planetary gear unit 14,
Power is distributed between the carrier 146 of the planetary gear unit 14 and the second brake device 25 that engages and disengages from the multi-stage transmission vehicle system *1 (+ case lOa). , a second one-way clutch device ff1 is disengaged from the carrier 14a and the case Ioa in parallel with the second brake device #25.
2fl is placed. (Kuranetari Gya Units above)
A fourth clutch device 27 that connects and connects the power transmission pipe between the carrier 14a of the planetary gear unit and the turbine shaft 18 is disposed on the side of the gear 14 on the engine side. An output gear 28 connected to the ring gear 19 is arranged on the side of the fourth clutch device 27 on the engine side. In addition, the reference numeral 29 in the drawing designates a lock clutch t which is directly connected to the turbine shaft 18 and the crankshaft lTh 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 pipe will be explained.

This second clutch device (fillj) is connected to the above-mentioned turbine shirt (1B) along a groove line, and includes a clutch drum 218 having a substantially U-shaped cross section. A clutch hub 21C is disposed inside this clutch drum 21a. This clutch 8'7'ile is used for small diameter sun gear 1.
It is integrally supported by a support portion 21d which is connected to the sedge line at the bottom of the support portion 21d. The clutch drum 21a and the clutch hub 21cKir are gas-line connected to the clutch grating 21e and the clutch disc 21b, which are arranged mutually. A piston 21f having a substantially U-shaped cross section is fitted into the clutch drum 21a in a shape corresponding to the contour of the inner wall of the clutch drum 21a. Between this piston 21f and support body Bla,
A hydraulic oil chamber Big is formed, and this hydraulic oil chamber 21g
By controlling the supply of hydraulic oil to the clutch grate 216 and the clutch disc 21b,
Alternatively, it is designed to be released to engage and disengage the second clutch device [21]. As is clear from the figure, the base part of the support part 21d of the clutch hub 21C constitutes the inner part of the first one-way clutch 22.

First clutch device 20 The piston 21f of the second clutch device 21 also serves as the clutch drum 20a of the first clutch device 20. Inside the clutch drum 2()8, a clutch hub 20c is provided. is arranged, and this clutch hub 2 (l
The base of the clutch drum 20a and the clutch hub 20cu are integrally supported by a support portion 20d that forms the outer race of the one-way clutch 22.
0c and the clutch disc 20b are gas line coupled. A piston QO1 is fitted inside the clutch disc 20a, and a hydraulic oil chamber 2 (lg) is formed between the piston 90f and the clutch drum 201B. By controlling the supply of
The first clutch device zO is engaged or disengaged by pushing or releasing the clutch disk 20b and the first clutch device zO.

In addition, in 20h in the figure, the bush l and the second clutch device 2
(+, 214) Piste 720 f% 21 f Noah 16
This shows the return sgering of .

Third clutch device f11B4 This third clutch device 24i11. A substantially U-shaped clutch drum B that is integrated with the clutch drum 21 mentioned above.
4a'? We are prepared. A clutch hoop 240 is disposed inside and facing the clutch drum 24m, and this clutch hoop 24Ctj is formed by an extension of the brake drum 28!1 of the first brake equipment N28. Clutch drum 24a and clutch hub 2
40 are alternately arranged clutch telegraphs)
2i4d+! : Connected to the clutch disc 24b by gas lines. Inside the clutch drum 24a,
A piston 246 is fitted, and this piston 24e
Between the clutch drum 24M and the clutch drum 24M is the oil chamber 2.
4 spaces are formed. By controlling the supply of hydraulic oil to the hydraulic oil chamber 24a, the clutch grate 24d and the clutch disc 24b are pressed and released, thereby engaging and disengaging the third latch device 20. It is now possible to do this.

This third clutch device ff114fi, piston 24@
Diaphragm tie return spring for 24
It is equipped with g. Note that this is because the diaphragm tie is thin and does not require a large space in order to use the return steering ring of the diaphragm tie in this third clutch device w24.

The fourth clutch device 27 is connected to the turbine shaft 18 in a straight line manner and includes a clutch drum 2qa having a substantially square cross-sectional shape. A clutch hub 21 is disposed inside this clutch drum 27M, and this clutch nod 127C is supported by a carrier 14a of a grain gear unit 14. The clutch drum 27a and the clutch hub 27C are gas line coupled to alternately arranged clutch plates 27d and clutch discs 27b, respectively. Inside the clutch drum 27a, there is a piston 2 formed by sheet metal processing. e is fitted. A hydraulic oil chamber 27f is formed between the piston 2M and the clutch drum 2'7a.
By controlling the supply of hydraulic oil to the hydraulic oil chamber 27f, the clutch grating 27d and the clutch disc 2? The fourth clutch device 27 is engaged and disengaged by pressing or releasing b. This fourth clutch device is similar to the third clutch device 24 described above, and the return gear ring 2 of the diaphragm tie is
Equipped with 7gt.

First brake device 28 ′ Brake drum 28a of this first brake device 28, support portion 28C integrally supported by large diameter nanja 16
Supported by Therefore, when the first brake device 28 operates, the large diameter sun gear 16 is fixed.

1st: J) 7 Ray*Installation fifB5 This second brake device firg5Fi is a differential brake, and its brake drum 258 is supported by a support portion 25b that is integrally fixed to the carrier 14a of the grain gear unit 14. has been done. Therefore,
When the second brake device 28 is actuated, the carrier 14a stands fixedly.

DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, the clutch equipment of an automatic GR/speed gear according to the present invention will be explained in detail.

Figure 3 is a partially enlarged view of Figure 2, showing the second Clara? The cross-sectional shapes of the clutch drum 21a of the device f121 and the clutch drum 24a of the third clutch device 24 are shown.

Clutch drum 21a.

248 are both made of sheet metal and have a cylindrical shape i with a U-shaped cross section, and the diameter of the clutch drum 218 is smaller than the diameter of the clutch drum g+a. Each of the clutch drums 21fi and 246 has its inner peripheral edge attached to the outer peripheral end of the cylindrical clutch inner 80, and the clutch drum 21a is arranged so as to be included in the clutch drum 24a. A gap is formed over the entire range between the clutch drums 21a and 24a, which are the input shafts of the second and third clutch devices 21 and 24, and are opposed to each other in the turbine shaft 1B direction. Clutch equipment f124T
An oil passage 29 for operation is formed. As can be seen from FIG. 3, the disk portion KF! of the clutch drum 24a extends in the #radial direction! A protrusion 24h that protrudes toward the clutch drum 218 is provided. This protrusion 114hH
As can be seen from FIG. 9 showing the planar shape of the clutch tram 248 and the sectional view taken along the line v-■ in FIG.
4M is uniformly formed in an annular shape in the circumferential direction, and the passage surface 'lJI of the oil passage 11f19 between the clutch drums 21a and 248 is uniformly narrowed. If the passage area of the oil passage 29 is narrowed in this manner, the third clutch device ff&24 is prevented from operating at an undesired time due to the centripetal force of the hydraulic oil generated by the rotation of the clutch drums 21a and 24a. The effect of 'f? This is preferable because it allows you to do many things. In addition, the clutch drum 21a
If the volume of the oil passage formed between and 24a is reduced, it is also possible to obtain the effect that the load on the engine is reduced. The inner peripheral part of the clutch inner 80 is spline connected to the outer peripheral part of the turbine shaft 18, and as the turbine shaft 18 rotates, the clutch inner 8o and the clutch drum 21a% 248 rotate integrally. Furthermore, a clutch plate 21d is provided inside the tip of the latch drum 21a, a first clutch device fjI2o is provided inside the clutch drum 21a, and a clutch grate 24d is provided inside the tip of the clutch drum 24a. This is as described above, and by controlling the injection of hydraulic oil through the oil passage 29, the entire operation of the third clutch device fltQ+ is controlled.

[Brief explanation of drawings]

FIG. 1 shows a clutch system f of an automatic transmission for an automobile according to the present invention.
FIG. 2 is an axial cross-sectional view schematically showing the structure of the automatic transmission shown in FIG. A partially enlarged view, i+, is a plan view showing the planar shape of the outer clutch drum, and FIG. 5 is a sectional view taken along line IV-IV in FIG. 9. l...Crankshaft, 2...Torque converter, 1
(+... Multi-speed painting device, 12... Solid shaft %1B
...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, 22...First one-way clutch device, 2B-...First brake device ff1f
, 24-...g three clutch devices, 24a...clutch drum, 24.h...protrusion, 25...second brake locking, z6...second one-way clutch, 2
7... Fourth clutch device, 28... Output gear, 29... Oil passage, 80... Clutch inner.

Claims (1)

[Claims] Inner and outer clutch devices Vt are arranged in sequence in the radial direction with respect to the input shaft, and these inner and outer clutch devices have inner and outer clutch drums made of sheet metal, respectively. , the inner clutch drum comprises a first portion extending radially and a second portion extending axially from an outer end of the first portion; a first portion extending radially along the i/portion and radially outwardly of the second portion of the inner clutch drum and axially from the outer end of the first s portion of the outer clutch drum. an extending second portion, and an oil passage for operating oil of the outer clutch device is formed between the first portion of the inner clutch drum and the island 1 portion of the outer clutch drum. A clutch device for an automatic military KJrK machine, which is characterized by having a gap for the purpose of the automatic military use.