JPH02275152A - Clutch system of automatic transmission - Google Patents

Abstract

PURPOSE:To utilize the inner space of a case and to realize a compact size by installing two clutch drums to one common cylinder member, and superposing clutches furnished in the two drums in the radius direction. CONSTITUTION:This automatic transmission furnishes an oil pump cover 250 held by a housing of a starting device 2 and a housing case 300 of an epicyclic gear device, a cylindrical holder 252 at the center of the case side of the cover 250, an oil way member 254 pressed in at the outer circumference of the holder 252, and a cylinder member 460 held rotatable at the front and the rear ends at the outer circumference of the member 254. While two clutch drums 440 and 470 are fixed in series along the axial direction of the cylinder member 460 at the outer circumference of the cylinder member 460, a clutch 14 housed in one side clutch drum 470 is provided at the outer side in the radius direction to another clutch 1 2 housed in the other side clutch drum 440.

Description

[Detailed Description of the Invention] [Industrial Application Field] The present invention is a white! l')
This invention relates to a clutch device for a J transmission.

[Conventional technology]

An automatic transmission is equipped with a starting device and a plurality of rows of epicyclic gears, and has a path for transmitting input from the starting device to the elements that make up the planetary gear train, and a path that fixes the elements of the planetary gear train to receive reaction forces. Route and M! By selectively switching rJ and the path for extracting output from the elements of the gear train using frictional engagement elements, gear stages with different gear ratios are configured and gear stage switching is achieved.

In an automatic transmission with multiple gears, it is desirable to have many frictional engagement elements in order to smoothly configure and change gears. Among the frictional engagement elements, clutches are particularly important. Generally, it has a structure in which a clutch plate and a hydraulic screw 1, which is a servo device, are housed in a freely rotatable drum. Therefore, when a large number of clutches are installed, a problem arises in that space is required in the axial and radial directions, and it is difficult to allocate sufficient space for a supporting device for the rotating clutch drum.

[Problem to be solved by the invention]

The present invention has two clutch devices for radially overlapping and capturing two clutch devices for forming and changing gear stages of an automatic transmission.
By supporting the inner cylinder common to each clutch at two points, installation space is saved and the clutch has a strong support structure.

The present invention provides a clutch device that also improves the supply of servo oil pressure.

[Means to solve the problem]

In order to solve the above problems, the present invention has developed a single starting device (two
) and a case (300) that accommodates a planetary gear set. Support part (252)
- an oil passage member (254) press-fitted by the outer periphery of the support part (252), and a cylinder member (460) whose front and rear ends are rotatably supported by the outer periphery of the oil passage member (254); Two clutch drums (440, 470) are fixed in series to the outer circumference of the member (460) along the axial direction of the cylinder member (8460), and a clutch (14) is accommodated in one clutch drum (470). Clutch (12) accommodated in the other clutch drum (440)
It has a configuration in which it is disposed radially outward with respect to.

[Effect]

By having the above means, two clutch drums (
440, 470) are firmly supported, and the clutches (14) housed in one clutch drum (470) are housed in the other clutch drum (440).
12), space can be used effectively as it can be placed overlapping in the radial direction. Although the above symbols in parentheses are in contrast to the drawings, they do not limit the configuration in any way. isn't it.

[Example] Hereinafter, the present invention will be explained in detail based on the drawings.

FIG. 1 is a sectional view of an automatic transmission implementing the present invention, and FIG.
The figure shows a skeleton, and first, an overview of the whole will be explained with reference to FIG.

The automatic transmission 1 includes a starting device 2 and a transmission 3 having a planetary gear device, but the starting device 2 includes, in addition to the torque converter shown in this embodiment, a fluid coupling and a t! Appropriate means such as a TM clutch, a multi-plate clutch, a centrifugal clutch, etc. can be selected.

The starting device 2 includes a rear cover 204 connected to the rear part of a front cover 202 that rotates under the drive of an engine.
．． A turbine runner 208 has a pump impeller 206 formed on the inner peripheral wall surface of the rear cover 204 and is disposed opposite to the pump impeller 206.
The turbine shell 210 is connected at its inner peripheral portion to an input shaft 240 which is an output member of the starting device 2 and an input member of the transmission 3. pump impeller 206
A stator 214 is disposed between the turbine runner 208 and the one-sided clutch 21
6, and the inner race of the one-way clutch 216 is connected to the support cylinder 230 which is a fixed member.
attached to the outer periphery of the A lock-up clutch 220 that directly connects the front cover 202 and the turbine shell 210 is disposed between the front cover 202 and the turbine shell 210.

The planetary gear train of the transmission 3 includes a basic planetary gear train 4a and an auxiliary planetary gear train 4b. The basic planetary gear train 4a is the first
and second simple planetary gear set 110, 12
0, the first simple planetary gear set 110
This is a Simpson-shaped planetary gear train that connects the carrier 113 of the second simple planetary gear set 120 and the ring gear 125 of the second simple planetary gear set 120. The auxiliary planetary gear train 4b includes one row of simple planetary gear sets 130, and includes a sun gear 13.
1 is fixed and the input of the ring gear 135 is connected to the carrier 133.
It has the function of a so-called split-type speed reducer that provides input to the sun gear and ring gear, and outputs to the carrier.

This automatic transmission has five clutches as frictional engagement elements,
Equipped with 3 brakes and 3 one-way clutches,
The coupling relationship between the frictional engagement element and each element of the ti star gear train is as follows.

The input shaft 240 of the transmission 3 is connected to the drum of the first clutch 11, and the hub of the first clutch 11 is connected to the first simple planetary gear set 1 via the first intermediate shaft 610.
10 ring gear 115. first clutch 1
The drum of the second clutch 12 also serves as the hub of the second clutch 12, and the drum of the second clutch 12 connects to the sun gear 1 of the first simple planetary gear set 110 via the second intermediate shaft 620.
Connect to 11. The drum of the second clutch 12 is also connected to the drum of the fourth clutch 14, and the drum of the fourth clutch 14
The hub of is connected to the carrier 123 of the second simple planetary gear set 120 via a third intermediate shaft 630. The drum of the fourth clutch 14 is connected to the outer race of the first one-way clutch 31 together with the third clutch 13 . The drum of the third clutch 13 and the inner race of the first one-way clutch 31 are connected to the sun gear 121 of the second simple planetary gear set 120 via a fourth intermediate shaft 640. A second brake 22 is disposed on the outer periphery of the drum of the third clutch 13.

The carrier 113 of the first simple planetary gear set 110 is connected to the ring gear 125 of the second simple planetary gear set 120, and the third simple planetary gear set 130 constitutes the auxiliary planetary gear train 4b via the first connecting member 150. ring gear 135
Become one with.

The carrier 123 of the second simple planetary gear set 120 is connected to the hubs of the second one-way clutch 32 and the fifth clutch 15 via a second connecting member 160. The outer race of the second one-way clutch 32 also serves as the inner race of the third one-way clutch 33 disposed on its outer periphery, and this race is integrated with the drum of the fifth clutch 15 to form the third simple planetary gear. Connected to sun gear 131 of set 130. The first brake 21 is disposed on the outer periphery of the fifth clutch 15, and the outer race of the third one-way clutch 33 is fixed to the inner wall of the transmission case.

The carrier 133 of the third simple planetary gear set 130 is connected to the output shaft 800.

FIG. 1 is a sectional view showing a specific structure of the automatic transmission having the skeleton explained in FIG.

The starting device 2 constituting the automatic transmission 1 is a fluid transmission device, and is housed inside a housing 200 that opens toward the engine side (hereinafter, the engine side will be referred to as the "front side"). A carrier cover 204 is integrally attached to the rear of the front cover 202, which rotates in response to the engine's iAM #I. A pump impeller 206 is formed on the inner peripheral wall surface of the rear cover 204, and a turbine runner 208 disposed opposite to the pump impeller 206 is connected to the turbine shell 21.
It is held at 0. The turbine shell 210 is connected at its inner peripheral portion to an input shaft 240 which is an output member of the starting device 2 and an input member of the transmission 3 via a connecting member 211 . A stator 214 is disposed between the pump impeller 206 and the turbine runner 208, and the inner peripheral portion of the stator 214 is connected to an outer race 215 of a one-way clutch 216, and an inner race 217 of the one-way clutch 216 is connected to a support cylinder. It is attached to the outer circumference of the front end of 230. A lock-up clutch 220 having a lock-up piston 222 is disposed between the front cover 202 and the turbine shell 210.

A cylindrical case 300 that houses the components of the transmission 3 is connected to the rear of the housing 200, and an oil pump cover 250 and a partition plate 270 are connected to the joint between the housing 200 and the transmission case 300. Attach the oil pump housing 260. An internal gear pump consisting of an external gear 262 and an internal gear 264 is accommodated within the oil pump housing 260, and the inner peripheral portion of the external gear 262 is connected to a shaft 266 that is integral with the carrier cover 204.

The center of the oil pump cover 250 forms a cylindrical support portion 252 that protrudes rearward, and this support portion 25
The rear outer circumference of the support tube 230 is press-fitted and fixed to the inner circumference of the support tube 230.

The support tube 230 supports the input shaft at two fulcrums on its inner circumference, and the rear end of the input shaft forms a radially expanding flange. The outer peripheral part of the flange part is the first clutch drum 41
Concatenated to 0. The first clutch 11 is housed inside the first clutch drum 410, and the first clutch 11
A piston 420 is provided to operate the .

The rear side of the first clutch drum 410 opens rearward, and the clutch hub 430 is fixed to the front side of the drum 410, and the second clutch 12 is connected between the clutch hub 430 and the second clutch drum 440 disposed opposite to each other. A piston 450 is housed therein. The inner peripheral side of the second clutch drum 440 is a cylinder member 46
This cylinder member 460 is rotatably supported by the support portion 252 of the oil pump cover 250. A fourth clutch drum 470 that accommodates the fourth clutch 14 and a piston 480 is connected to the front end of the cylinder member 460 .

The fourth clutch drum 470 is connected to the outer race 540 of the first one-way clutch 31 via a connecting member 49O. The hub 500 of the fourth clutch 14 is connected to the third intermediate shaft 630. The third clutch 13 is provided between the outer race 540 and a third clutch drum 520 disposed on the outer peripheral side thereof, and the piston 530 is housed in the clutch drum 520. A band-type second brake 22 is provided on the outer periphery of the third clutch drum 520, and the inner cylinder side of the clutch drum 520 is integrated with the inner race 510 of the first one-way clutch 31.

The inner circumference of the rear end of the input shaft 240 is connected to the first
supports the outer periphery of the distal end of the intermediate shaft 610.

The outer peripheral portion of the rear end of the first intermediate shaft 610 is supported by the inner peripheral portion of the tip end of the output shaft 800 via a bearing. Since the input shaft 240 and the output shaft 800 are firmly supported by the transmission case 300, the support rigidity of the first intermediate shaft 610 supported by these shafts is also increased.

The outer circumference of the first intermediate shaft 610 is a cylindrical second intermediate shaft 6.
20 is supported at two points, and the outer peripheral portion of the second intermediate shaft 620 supports a cylindrical third intermediate shaft 630 at two points. A fourth intermediate shaft 640 arranged concentrically on the outer peripheral side of the third intermediate shaft 630
is supported by the inner periphery of a central support member 310 attached to the center inside the transmission case 300. The central part of the central support member 310 is formed into a cylindrical part that protrudes forward and rearward of the case. The inner periphery of the inner cylinder of the clutch drum 520 is rotatably supported.

The front end of the first intermediate shaft 610 is connected to the hub 405 of the first clutch 11, and the front end of the second intermediate shaft 620 is connected to the hub 405 of the first clutch 11.
The clutch drum 440 of the clutch 12 is connected to the clutch drum 440 of the clutch 12. The front end of the third intermediate shaft 630 is connected to the hub 500 of the fourth clutch 14, and the front end of the fourth intermediate shaft is connected to the drum 520 of the third clutch 13 and the first one-way clutch 3 integral with the drum 520 of the third clutch 13.
1 inner race 510. The intermediate shaft having a quadruple structure extends rearward through the central support member 310, and
The outer periphery of the rear end of the intermediate shaft 610 is supported by the inner periphery of the tip of the output shaft 800. A rear wall 330 is formed at the rear of the transmission case 300, and a rear support member 350 is inserted into and fixed to the inner circumference of the rear wall 330. The rear support member 350 includes a cylindrical portion that protrudes toward the front inside the transmission case 300, and the outer diameter of the cylindrical portion is formed into a plurality of stepped portions whose outer diameters gradually become smaller toward the front. . Support member 3
The front inner circumferential portion of the cylindrical portion 50 supports the front outer circumferential portion of the output shaft 800 .

A spigot engagement portion 36 at the rear end of the case 300 of the transmission.
The inner periphery of the rear end of the rear case 370 that is concentrically fitted with the rear case 370 supports the rear outer periphery of the output shaft 800 via a bearing. Therefore, the output shaft 800 is reliably supported by the two supporting points, and the first intermediate shaft 610 is reliably supported at its front and rear ends by the input shaft 240 and the output shaft 800, as described above.

As explained in the skeleton of FIG. 2, three rows of simple planetary gear sets are arranged on the outer periphery of the connecting portion between the intermediate shafts 610, 620, 630, 640 and the output shaft 800, which have a four-layer structure. 1st. arranged in the third order.

The ring gear 115 of the first simple planetary gear set 110 is attached to the rear end of the first intermediate shaft 610 via a connecting member 615. The sun gear 111 of the first simple planetary gear set 110 is attached to the rear end of the second intermediate shaft 620, and the carrier shaft 113 of the binion is connected to the ring gear 125 of the second simple planetary gear set 120. One end of the carrier shaft 123 of the second simple planetary gear set 120 is connected to the third
The other end is connected to the intermediate shaft 630 of the second connecting member 16.
Inner race 7 of second one-way clutch 32 through 0
Connect to 00.

A sun gear 121 of the second simple planetary gear set 120 is formed at the rear end of the fourth intermediate shaft 640. Ring gear 12 of second simple planetary gear cell 1~
5 is integrated with the ring gear 135 of the third simple planetary gear set 130 via the first connecting member 150.

A multi-plate third brake 23 is disposed on the outer periphery of the second coupling member 160 disposed outside the first coupling member 150, and a piston 550 is inserted into the rear wall surface of the central support member 310. to be accommodated.

A sprag and an outer race 710 are arranged on the outer circumferential side of the inner race 700 that is coupled to the second connecting member 160.
A one-way clutch 32 is configured.

Another sprag and an outer race 720 are further disposed on the outer peripheral side of the outer race 710 to constitute the third one-way clutch 33. That is, the race 710 is a member that serves both as an outer race and an inner race, and is interposed between the two one-way clutches 32 and 33, so it is referred to as a middle race 710 in this specification. inner lace 70
0 is integrated with the clutch hub 730, and the middle race 7
10 is connected to the fifth clutch drum 740. The fifth clutch 15 and piston 750 are housed in the fifth clutch drum 740.

The outer periphery of the outer race 720 of the third one-way clutch 33 is spline engaged with the inner periphery of the case 300, and the band-type first brake 21 is disposed on the outer periphery of the fifth clutch drum 740. Fifth clutch driver 7, 740
The shaft member 760, which is integrated with the inner cylinder, has its inner circumference supported by the outer circumference of the rear support member 2350, and the third simple planetary gear set 1331 is attached to its tip.

The shaft 13:3 of the carrier supporting the pinion of the third simple planetary gear cell l-, 130 is the output shaft 80.
It is supported by a connecting part formed at the front end of the 0.

On the outer periphery of the rear case 7370 of this output/f'llll 800 are a parking gear F3'0 and a speaker 1.
A meter drive gear 8330 is attached, and a pawl 820 that connects to the parking gear 810 is attached to the outside of the parking gear 810. Set up The connecting portion (38F'10) is fixed to the rear end of the output 1/IIl with a nut 855.

Transmission case; inside of 300 and rear case 370.
Rotation sensors 305 and 306 are provided in the V section to obtain information for controlling the frictional engagement elements by providing the number of rotations j/' of the rotating member.

A hydraulic control device (not shown) is attached to the bottom of the transmission case 300 and covered with a cover 309 that also serves as an oil pan.

As described above, the automatic transmission of the present invention includes five clutches and three brakes as frictional engagement elements.

Three one-way clutches are provided to achieve five forward speeds and one reverse speed, and Table 1 shows the engagement state of each of the 19 friction engagement elements at each gear stage.

In Table 1, the O mark indicates that the frictional engagement element engages,
The (0) mark indicates engagement during engine braking.

Note that the 4A gear has the same gear ratio as the 4th gear, and is a gear that appears immediately before shifting to the 5th gear.

The present invention relates to a clutch device for an automatic transmission having the above structure, and the specific structure thereof will be explained below with reference to FIG. 3.

Between the housing 200 of the starting device and the case 300 of the transmission, the center of the oil pump cover 250 forms a cylindrical support portion 252 that projects rearward. The outer circumferential portion of the rear end of the support tube 230 is press-fitted into the inner circumferential portion of the supporting portion 252 .

The rear outer peripheral portion of the input shaft 240 is supported by a radial bearing 241 disposed between the input shaft 240 and the support portion 252, and the rear end portion of the input shaft forms a flange portion 242 that expands in the radial direction. The outer peripheral portion of the flange portion 242 is connected to a first clutch drum 410 that accommodates the first clutch 11, and a piston 420 for operating the first clutch 11 is disposed therein.

The rear side of the first clutch drum 410 opens rearward, and the clutch hub 430 is fixed to the front surface of the front wall 411 of the clutch drum 410. A second clutch drum 440 that accommodates the second clutch 12 is disposed on the outer peripheral side of the clutch hub 430, and a piston 450 that operates the second clutch 12 is inserted therein. The inner circumferential portion of the front wall 441 of the clutch drum 440 is fixed to the center portion of the cylinder member 460. The cylinder member 460 has a stepped cylindrical shape and has approximately the same length as the support portion 252 of the oil pump cover 250.

A cylindrical oil passage member 254 is press-fitted and fixed to the outer periphery of the support portion 252 of the oil pump cover 250.

The oil pump cover 250 is generally made of a material such as an aluminum alloy, but this oil passage member is made of, for example, iron. Then, precision can be improved by cutting. The oil passage member 254 rotatably supports the front and rear ends of the inner circumference of the cylinder member 460 by radial bearings 255a and 255b disposed at the front and rear ends of the outer circumference. That is, the cylinder member 460 is connected to the oil passage member 254 which is a fixed member.
It is definitely supported at two points. This cylinder member 46
0 is also a machined part to ensure high accuracy. Small diameter portion 46 formed in the latter half of the outer circumferential side of the cylinder member 460
2 is an inner cylinder of a piston 450 that operates the second clutch 12.

A clutch drum accommodating the fourth clutch 14, generally designated by the reference numeral 470, is attached to the first half of the outer peripheral side of the cylinder member 460. The clutch drum 470 consists of two drums: a drum 472 disposed on the inside and a drum 474 disposed on the outside.
The cylinder member 472 has a structure in which two drums are integrally overlapped, and the inner side of the inner drum 472 is supported by the outer circumference of the cylinder member 460, and the two are engaged with each other by a spline 463.

A piston 480 is inserted into the inner drum 472, and the fourth clutch 14 is disposed on the inner peripheral side of the outer drum 474. The inner circumferential portion of a suppressing member 482 is fixed to the outer circumferential portion of the piston 480, and the fourth clutch 14 is operated to suppress by the outer circumferential portion of the suppressing member 482.

With the above configuration, the clutch drum 440 that accommodates the second clutch 12 and the clutch drum 470 that accommodates the fourth clutch 14 are attached to the common cylinder member 460 and rotate together.

As explained in FIGS. 1 and 2, in the automatic transmission of the present invention, the clutch drum 440 of the second clutch 12 and the clutch drum 470 of the fourth clutch 14 are connected to form a power transmission path. , the above-described configuration can be adopted.

The fourth clutch 14 is engaged during the first to second forward speeds, receives a reaction force, and transmits power at a high speed stage above the third speed, and has a relatively small torque capacity. Therefore, by utilizing this characteristic, the fourth clutch 14 is connected to the second clutch 1.
2 are arranged in a stepped manner in the outer diameter direction. In addition, the piston 480 that operates the clutch 14 with a small torque capacity is
Since the effective area is also relatively small, the piston has a small diameter and is inserted into the clutch drum 472 which is disposed inside the clutch drum having a double structure. clutch drum 47
Since the piston 48 rotates at a high speed of 3rd gear or higher, it is easily affected by centrifugal oil pressure generated by centrifugal force.
By forming 0 with a small diameter, the influence of centrifugal oil pressure can be eliminated as much as possible.

Hydraulic pressure is supplied to the piston 450 that operates the second clutch 12 via a first oil passage 256 formed in the oil passage member 254 and an oil passage 465 formed in the cylinder member 460,
The screw that operates the fourth clutch 14! Servo oil pressure is supplied to the hexagon 480 via a second oil passage 257 formed in the oil passage member 254 and an oil passage 46G formed in the cylinder member 460 communicating with this oil passage.

Since it is disposed close to the outer periphery of the oil passage member 254 and adjacent to it in the same plane, and because it slides between it and the cylinder member 460, it is necessary to reliably seal against leakage of servo oil pressure. For this purpose, seal rings are fitted on both sides of each oil passage 256, 257, but if vibration occurs in the sliding part for one revolution, the seal rings will rapidly deteriorate, causing clutch malfunction due to servo oil pressure leakage. It becomes a prisoner of problems such as dragging.

In the present invention, since the iron oil passage member 254 and the upper cylinder member 460, which are press-fitted into the oil pump cover 250 that is firmly fixed to the transmission case, are reliably supported at two points, rotational vibration is reliably prevented, and the seal ring can improve durability.

〔Effect of the invention〕

As described above, the present invention is a clutch device installed in an automatic transmission, in which two clutch drums are attached to a common cylinder member, and the front and rear ends of the inner circumferential side of the cylinder member are connected by bearings. Since it is point supported, reliable support can be achieved.

Servo hydraulic pressure is supplied into the clutch drum through the cylinder member, but since the supporting rigidity is low, there is little vibration at the vibrating part, and deterioration of the seal ring fitted in the seal part can be prevented. Therefore, problems caused by leakage of servo oil pressure can be avoided.

Furthermore, since the clutches disposed within the two clutch drums are arranged to overlap in the radial direction, it is possible to construct a compact automatic transmission by effectively utilizing the internal space of the automatic transmission case.

[Brief explanation of drawings]

FIG. 1 is a cross-sectional view of an automatic transmission embodying the present invention, FIG. 2 is an explanatory diagram showing an overview of the automatic transmission embodying the present invention, and FIG. 3 is a partial cross-sectional view of essential parts. 1... Automatic transmission, 2... Starting device. 12...Second clutch, 14...Fourth clutch. 250...Oil pump cover 252...
...Support part, 254 ... Oil passage member, 300 ... Case, 440.470 ... Clutch drum, 460 ...
...Cylinder member. Patent applicant: Aisin AW Co., Ltd. Agent: Masaaki Suzuki (2 others) - 3'.

Claims (1)

[Claims] (1) In an automatic transmission equipped with a starting device and a planetary gear device, an oil pump cover that is clamped and fixed between a housing that accommodates the starting device and a case that accommodates the planetary gear device, and a center portion of the oil pump cover on the case side. a cylindrical support part formed in the outer circumference of the cylinder member; Two clutch drums are fixed in series along the axial direction of the cylinder member, and the clutch housed in one clutch drum is arranged radially outward from the clutch housed in the other clutch drum. A clutch device for an automatic transmission featuring: