JPH02275169A - One-way clutch of automatic transmission - Google Patents

Abstract

PURPOSE:To realize the reduction of weight and the utilization of the space by superposing one-way clutches provided at the rear part of the case of an automatic transmission in two layers in the radius direction, and providing two sets of one-way clutches between three races. CONSTITUTION:A sprag or the like is inserted between an inner race 700 and a middle race 710 to compose the second one-way clutch 32. And an outer race 720 is provided at the outer periphery of the middle race 710, a sprag or the like is inserted between the outer race and the middle race, and the third one-way clutch 33 is composed. Since the inner, the middle, and the outer races 700, 710, and 720 are provided from the inner bore side to the outer bore side in a multiple layers, and two one-way clutches are provided between the three races, one race can be omitted. And since two one-way clutches are provided in the radius direction in two layers, the axial direction can be shortened. And since the diameter size of the outer race to be the fixing member can be made larger, a large capacity of one-way clutch can be composed without expanding the width size of the outer race.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a one-way clutch for an automatic transmission equipped with a starting device and a planetary gear device.

[Prior Art] An automatic transmission is equipped with a starting device and a plurality of rows of planetary gears, and has a path for transmitting input from the starting device to the elements constituting the planetary gear train, and a path through which the elements of the planetary gear train are fixed. By selectively switching the path for receiving reaction force and the path for extracting output from the elements of the planetary gear train using frictional engagement elements, gear stages with different gear ratios are configured and gear stage switching is achieved.

For example, 5AE84130, which is an automobile-related technical document.
4, similarly to the automatic transmission of the present invention, a basic planetary gear train having a double-row planetary gear train and an auxiliary planetary gear train having a single-row planetary gear train are combined to provide four forward speeds and one reverse speed. An automatic transmission is disclosed that has several gear stages. This automatic transmission has two clutches and three brakes as frictional engagement elements.
use one directional clutch. One-way clutch]
It is engaged in the gear and reverse gears, but in the first gear it is interposed in the path that receives the reaction force, and in the reverse gear it is interposed in the path that transmits the power.

In order to smoothly configure and change gears, it is desirable to be equipped with many frictional engagement elements.In particular, one-way clutches are designed to automatically engage and disengage depending on the direction of rotation, and torsionally Since it has a shock absorbing effect, it achieves smooth switching.

In the automatic transmission described above, the characteristics of this one-way clutch can be used only when switching from first speed to second speed.

If a one-way clutch is added to use the one-way clutch to change more gears, the space for disposing the negative-direction clutch increases, which is a factor that goes against the desire to make the automatic transmission more compact.

[Problems to be Solved by the Invention] The present invention provides a device that can arrange two one-way clutches in the axial space of one by stacking the one-way clutches in the radial direction. It is.

[Means for Solving the Problems] In order to solve the problems described above, one aspect of the present invention is to provide a rear wall portion (330) of a case (300) that accommodates a planetary gear device.
) a stepped cylindrical rear support member (350) fixed to the
The outer periphery of the rear support member (350) is connected to the inner cylinder (7).
42) and a drum (740) that supports a shaft member (760), and a small diameter cylindrical inner race (700) that supports the outer circumference of the shaft member (760) via a bush (764). , a cylindrical middle lace (710) with a larger diameter than the inner lace arranged on the outer periphery of the inner lace (700), and a cylindrical outer lace (710) with a larger diameter than the middle lace arranged on the outer periphery of the middle lace ( 720), a one-way clutch (32) inserted between the inner race (700) and the middle race (710), and a middle race (720).
The basic configuration is that two one-way clutches (33) are inserted between the clutch 10) and the outer race (720) and are stacked in two layers in the radial direction.

The one-way clutch (32) disposed between the inner race (700) and the middle race (710) serves as a means for lubricating the one-way clutch.
lubricating oil is supplied from the rear support member (350) through radial oil holes (700a) provided in the middle race (
The one-way clutch (33) disposed between the outer race (710) and the outer race (720) is connected to the case (300) through a radial oil hole (720a) provided in the outer race (720).
It has a structure in which lubricating oil is supplied directly from the

Furthermore, in order to facilitate the assembly of the one-way clutch,
The inner race (700) is attached to the spline (7) on the hub (730) of the clutch (15) housed in the drum (740).
32) is engaged, and the middle race (710) is engaged with the drum (74).
spline (747) on the outer cylinder (746) of
) and the outer race (720) is engaged with the case (300).
It has a configuration in which a spline (722) is engaged with the spline (722).

[Operation] By providing the above means, the one-way clutches (32, 33) arranged in two layers in the radial direction act as one-way clutches in series or in parallel depending on the gear position. The inner race (700) has a rear support member (
Case (350) to outer lace (720)
Force lubrication from 00). 3 more races (700
, 710° 720) to a spline (732, 747, 7
22) to facilitate the assembly work.

Note that the above-mentioned symbols in parentheses are used to contrast with the drawings, but do not limit the configuration in any way.

[Example] The present invention will be described in detail below based on one drawing.

Figure 1 is a sectional view of an automatic transmission implementing the present invention;
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, an electromagnetic clutch,
Appropriate means such as a multi-plate clutch, a centrifugal clutch, etc. can be selected.

The starting device 2 includes a rear cover 204.
A turbine runner 208, which has a pump impeller 206 formed on the inner circumferential wall surface of the rear cover 204 and is disposed opposite to the pump impeller 206, is held by a turbine shell 210, and the turbine shell 210 has an inner circumferential portion thereof that is connected to a starting device. 2 and is connected to an input shaft 240 that is an input member of the transmission 3. A stator 214 is disposed between the pump impeller 206 and the turbine runner 208, and the inner circumference of the stator 214 is connected to a one-way clutch 216.
The inner race of the one-way clutch 216 is attached to the outer periphery of a support tube 230, which is a fixed member. 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 friction engagement element and each element of the planetary 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 cross-sectional view showing the specific structure of the automatic transmission having the skeleton explained in FIG. , the engine side is referred to as the "front side"). A carrier cover 204 is integrally attached to the rear of the front cover 202, which rotates under the drive of the engine. A pump impeller 206 is formed on the inner peripheral wall surface of the rear cover 204, and a turbine runner 2 is disposed opposite to the pump impeller 206.
08 is held in the turbine shell 210. 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 . pump impeller 206
A stator 214 is disposed between the turbine runner 208 and the one-way clutch 21 .
The inner race 217 of the one-way clutch 216 is attached to the outer circumference of the front end of the support tube 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, which is integral with the oil pump cover 250, 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 490. 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 5] Connect to 0. 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 360 is provided at the rear end of the transmission case 300.
The inner periphery of the rear end of the rear case 370, which is fitted concentrically through 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 125 of the second simple planetary gear set
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 on the outside of the first coupling member 150 , and a screw 1 - 550 is attached to the rear side of the central support member 310 . be housed within the wall of the

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 10 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 surface of the case 300, and the band-type first brake 21 is disposed on the outer periphery of the fifth clutch drum 740. The shaft member 760, which is integrated with the inner cylinder integrated with the fifth clutch drum 740, has its inner circumference supported by the outer circumference of the rear support member 350, and has the third simple planetary gear set 1 attached to its tip.
Attach No. 30 sun gear 131.

The shaft 133 of the carrier that supports the pinion of the third simple planetary gear set 130 is supported by a connecting portion formed at the front end of the output shaft 800.

The outer periphery of the output shaft 800 inside the rear case 370 includes
A parking gear 810 and a speedometer drive gear 830 are attached, and the parking gear 810
A pawl 820 coupled to the gear 810 is disposed on the outside of the gear 810 .

A connecting member 850 is fixed to the rear end of the output shaft with a nut 855.

Rotation sensors 305 and 3 for detecting the rotation speed of rotating members are installed in the main parts inside the transmission case 300 and rear case 370.
06 to obtain information for controlling the frictional engagement elements.

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 has five clutches, three brakes, and three one-way clutches as frictional engagement elements to achieve five forward speeds and one reverse speed. 1
The table shows the engagement state of each frictional engagement element 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 two-layer one-way clutch for an automatic transmission having the above-described structure, and the specific structure thereof will be explained below with reference to FIG. 3.

The rear support member 350 is fixed to the inner periphery of the rear wall 330 of the transmission case 300 by spigot engagement, and has a cylindrical shape that protrudes into the case. Supports 800. The outer circumference of the rear support member 350 supports an inner cylinder 742 of a clutch drum 740 that accommodates the fifth clutch 15 via a bearing. The front part of the inner cylinder 742 forms a cylindrical shaft member 760, and the sun gear 131 of the third simple planetary gear set is connected to the inner peripheral part of the front end via a spline 763.

A band-type first brake 21 is disposed on the outer periphery of the outer cylinder 746 of the clutch drum 740. The fifth clutch 15 has a piston 75 inserted into the drum 740.
0, but the hub 730 of the fifth clutch 15
The front portion extends inward in the radial direction and is connected to the inner race 700 via a spline 732 formed on the outer periphery of the front end.

The inner race 700 is connected to the basic planetary gear train by the second connection member 160, and the inner circumference of the inner race 700 is provided with a sleeve 764, and the shaft member 760 is integrated with the inner cylinder 742 of the clutch drum 740. Supported by the outer periphery.

A middle race 71 is attached to a spline 747 formed on the inner periphery of the front end of the outer cylinder 746 of the clutch drum 740.
A sprag or the like is inserted between the inner race 700 and the middle race 710, which are engaged with the splines of the member 712 connected to the second one-way clutch 32. An outer lace 720 is arranged on the outer peripheral side of the middle lace 32,
A sprag or the like is inserted between the middle races to constitute the third one-way clutch 33. The outer periphery of the outer race 720 forms a spline 722 and is engaged with and fixed to the inner periphery of the transmission case 300.

The one-way clutch of the present invention has three races, an inner race 700, a middle race 710, and an outer race 720, arranged in multiple layers from the inner diameter part to the outer diameter part, as shown below. Since two one-way clutches are provided between them, one race can be omitted. Since the two one-way clutches are arranged doubly in the radial direction, the axial direction can be shortened, and the diameter of the outer race that serves as the fixing member can be increased, so the width of the outer race can be increased. A large-capacity one-way clutch can be constructed without the need for

These two one-way clutches 32 and 33 are arranged between the auxiliary planetary gear train and the fifth clutch 15 that operates this, the inner race 700 is connected to the basic planetary gear train, and the middle race 710 is connected to the fifth clutch 15 that operates the auxiliary planetary gear train. It is directly connected to the drum 740 of the clutch 15 of No. 5, and also connected to the inner cylinder 700 via the clutch 15. A shaft member 760 integral with the inner cylinder 742 of the clutch drum 740 is directly connected to the sun gear 131 of the auxiliary planetary gear train.

As shown in Table 1, the two one-way clutches 32 and 33 operate in the following manner at each gear stage.

That is, in the first gear, the inner race 700 stands still together with the connecting member 160 and receives a reaction force.

Therefore, the second one-way clutch 32 located on the inside is in a locked state, and when receiving torque, the second one-way clutch 32 receives a torque approximately 1.2 times the input torque.

At the same time, the sun gear 131 of the auxiliary planetary gear train is stationary and receives a reaction force, but this torque is transmitted to the middle race 710 via the drum 740, locks the third one-way clutch 33 located on the outside, and locks the outer race 720. Torque can be received by

The third one-way clutch 33 is the second one-way clutch 32
The torque transmitted from the sun gear 131 and the torque transmitted from the sun gear 131 are combined, and the torque is approximately 2.2 times the input torque.

Therefore, although it is necessary to increase the torque capacity of the third one-way clutch 33, it is extremely convenient because the radial dimension can be increased. especially.

Since the first speed is the lowest forward speed and the transmitted torque is large, the above characteristics work extremely advantageously.

When the one-way clutch is in a locked state, the sprags or the like are elastically deformed, so that the one-way clutch has a shock absorbing effect. In the present invention, since two one-way clutches are used in series, shocks are absorbed and smooth gear shifting is achieved.

In the second gear, the two one-way clutches 31 and 32 are utilized in the same way as in the first gear.

In the third gear, only the third one-way clutch 33 located on the outside is engaged and the sun gear 131 of the auxiliary planetary gear train is engaged.
receives a reaction force.

In the reverse gear, the second one-way clutch 32 engages during reverse drive to transfer the reaction force of the sun gear 131 to the second
When the engine brake is applied, the third one-way clutch 33 is engaged and the sun gear 13 is
receives a reaction force of 1.

As described above, in the present invention, two one-way clutches arranged in two layers in the radial direction are used in four different gears, so the one-way clutch can participate in switching between each gear. Smooth operation can be achieved.

When a one-way clutch has a two-layer structure, lubrication becomes difficult, and especially when the diameter of the race becomes large, it becomes difficult to supply lubricating oil from the shaft center.

Therefore, in the present invention, lubricating oil is supplied to the inner race 700 from the rear support member 350 and to the outer race 720 from the case 300.

That is, an oil passage 352 for lubricating oil is provided in the rear support member 350, and a radial oil hole 352a is provided in the front end thereof. A shaft member 760 that is integral with the inner cylinder 742 of the clutch drum 740 is also formed with a radial oil hole 760a that faces the oil hole 352a. Since the outer circumference of the shaft member 760 that is integral with the inner cylinder 742 supports the inner race 700 via the bushing 764, the bushing 764 is also provided with an annular oil passage and a radial oil hole 764a. nl+g and the radial oil hole 700a are communicated with each other.

With the above configuration, the second one-way clutch 32 can be reliably lubricated.

Outer race 720 has spline 722 on case 300
Therefore, the third one-way clutch 33 is forcibly lubricated via the oil passage 325 provided in the case 300 and the oil passage 720 provided in the outer race 720. Note that a pipe 326 is inserted into the oil passage 325, and the oil hole 720a opening at the peak of the spline 722 is sealed with the tip of a rubber cylinder 327 attached to the tip of the pipe 326 to prevent leakage of lubricating oil. Achieve reliable lubrication.

The two-layer one-way clutch of the present invention is arranged between an auxiliary planetary gear train and a servo device that controls it, and although it has a complicated structure, it is constructed so that it can be easily assembled.

That is, the case 3 to which the rear support member 350 etc. are attached in advance
00 upright with the rear wall 330 side down, and first attach the clutch drum 740.

Next, the fifth clutch 15 and hub 730 are inserted.

Connect the middle race 710 to the spline 7 to the outer cylinder 74G of the clutch drum 740 using the connecting member 712.
47. The outer race 720 is fixed to the inner peripheral wall of the case 300 by a spline 722. Third
The second one-way clutch 33 is inserted between the outer race 720 and the middle race 710, and the second one-way clutch 32 is assembled together with the inner race 700. Finally sun gear 1
31 to the clutch drum 74 using spline 763
The assembly is completed by engaging the shaft member 760 integral with the inner cylinder 742 of No. 0.

With the above configuration, the diameter of the sun gear 131 can be freely selected, so the gear ratio of the auxiliary planetary gear train acting as a reduction gear can be changed depending on the purpose.

〔Effect of the invention〕

As described above, the present invention has a structure in which the one-way clutches disposed at the rear part of the automatic transmission case are overlapped in 2WJ in the radial direction, so that the space in the axial direction can be reduced.

Since the two one-way clutches are disposed between the three races, the center race also serves as the inner race of the one-way clutch disposed on the outside and the outer race of the one-way clutch disposed on the inside. Therefore, one lace can be saved, thereby achieving weight reduction and effective use of space.

One-way clutches require sufficient lubrication, but one-way clutches installed on the inside engage through a member that supports the inner race, and one-way clutches installed on the outside engage the outer race of the transmission case. Reliable lubrication is achieved as forced lubrication is applied from each side.

Further, since the three races each engage with the mating member through splines, the assembly is easy to assemble.

[Brief explanation of drawings]

FIG. 1 is a sectional view of an automatic transmission embodying the present invention, and FIG. 2 is an explanatory diagram showing an outline of the automatic transmission embodying the present invention. FIG. 3 is a partial sectional view of the main part. 1... automatic transmission, 2... starting device, 32.33... one-way clutch, 300...
...Case, 350...Rear support member, 700...Inner lace, 710...Middle lace, 720...Outer lace, 740... ... Drum, 742 ... Inner cylinder, 746 ... Outer cylinder, 760 ... Shaft member, 764 ... Bush.

Claims (3)

[Claims] (1) In an automatic transmission equipped with a starting device and a planetary gear device, the rear support member is a stepped cylindrical portion that is fixed to the rear wall of the case that houses the planetary gear device, and the outer periphery of the rear support member is an inner cylinder. and a drum integrally supporting the shaft member, a small-diameter cylindrical inner race supported by the outer periphery of the shaft member via the support member, and a drum with a larger diameter than the inner race disposed on the outer periphery of the inner race. It has a cylindrical middle race and a cylindrical outer race with a larger diameter than the middle race arranged around the outer periphery of the middle race, and a one-way clutch inserted between the inner race and the middle race, and between the middle race and the outer race. A one-way clutch for an automatic transmission, characterized in that the one-way clutch is stacked in two layers in the radial direction. (2) In the one-way clutch according to claim 1, the one-way clutch disposed between the inner race and the middle race is supplied with lubricating oil from the rear support member through a radial oil hole provided in the inner race. A one-way clutch for an automatic transmission, characterized in that the one-way clutch disposed between the middle race and the outer race is supplied with lubricating oil directly from the case through radial oil holes provided in the outer race. (3) In the one-way clutch according to claim 1, the inner race is spline engaged with the hub of the clutch housed in the drum, the middle race is spline engaged with the outer cylinder of the drum, and the outer race is spline engaged with the case. A one-way clutch for an automatic transmission characterized by comprising: