JPH02125136A - Support structure for servo device of automatic transmission - Google Patents

Abstract

PURPOSE:To make a servo device compact by arranging a clutch connecting a sun gear and carriers and its piston in the drum of a band brake fixing the sun gear to a reduction gear. CONSTITUTION:A clutch 104 operated when carriers 103 and 105 are directly connected to a sun gear shaft 108 and its operating piston 116 are stored in the drum 110 of a band brake 112 operated at the time of deceleration, and the outer race 115 of a one-way clutch 113 coupled with an inner race 109 and operated at the time of deceleration is coupled with the inside of a transmission case 30. A sun gear 128 is rotatably supported on the stepped section 125c of a stepped cylindrical rear shaft support member 125 fitted to the hole 303 of the rear wall face 302 of the reduction gear case via a bearing 125h, and the boss section 125f of a base section 125a is faucet-coupled with the hole 303 of the rear wall face 302. A servo device can be made compact.

Description

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

[Conventional technology]

An automatic transmission consisting of a main transmission equipped with a starting device and a planetary gear system, and a sub-transmission equipped with a planetary gear system for deceleration, the automatic transmission being provided between a ring gear that is an input member and a carrier that is an output member. A servo device including a clutch is disclosed in, for example, Japanese Patent Laid-Open No. 141342/1983.

The servo device disclosed in the above publication includes a cylindrical sun gear shaft with a sun gear formed at the tip, a radial wall provided at the rear of the sun gear shaft, a drum provided on the outer periphery of the wall, and a cylindrical sun gear shaft provided at the rear of the sun gear shaft. It has a cylindrical inner race formed at the end, and the outer circumferential surface of the drum also serves as the brake drum of the band brake that operates during deceleration, and the inside of the drum contains a clutch and a clutch actuating piston that operate when the carrier and sun gear are directly connected. It has a structure in which the outer race of a one-way clutch that operates during deceleration is fitted into the outer peripheral surface of the inner race and engaged with the inside of the transmission case.

However, this servo device is rotatably supported on the output shaft of an auxiliary transmission arranged parallel to the main transmission.

[Problem to be solved by the invention]

The present invention relates to an automatic transmission in which a main transmission and an auxiliary transmission are connected in series, and in which a sun gear shaft constituting a servo device 7t of the auxiliary transmission is fixed to a rear part of a case of the transmission. The purpose of this support is to provide a reliable support structure with good concentricity.

[Means to solve the problem]

The present invention provides a ring gear (101) connected to an input member.
and a carrier (103,
This is a servo device for a 12i2 star gear device for reduction with ), a drum (110) provided on the outer periphery of the wall, and a cylindrical inner race (109) formed at the rear end of the sun gear N (108) (7). The drum also serves as the brake drum for the band brake (112) that is activated when the carrier is connected directly to the sun gear.
The outer race (115) of the one-way clutch (113) that operates during deceleration is fitted to the outer peripheral surface of the inner race (lO9) and is engaged with the inside of the transmission case (30). The stepped cylindrical rear shaft support member (125), which is attached to the hole (303) formed in the rear wall surface (302) of the transmission case, has a base (125a) with the maximum outer diameter.
and a multi-stage stepped portion (125b) whose outer diameter decreases sequentially from the base toward the inside of the case.

125c, 125d), and a boss portion that protrudes on the opposite side of the stepped portion across the base, and the stepped portion has a bearing (125h) fitted to the front and rear ends of its outer periphery. The inner circumferential portion of the sun gear shaft (108) of the servo device is rotatably supported through the servo device, and the boss portion is attached by engaging with a hole formed in the rear wall surface of the case with a spigot.

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

〔Example〕

Embodiments of the present invention will be described below based on the drawings.

Figure 2 shows the skeleton of an automatic transmission.

The automatic transmission 1 includes a torque converter 2 as a starting device and a transmission 3. The transmission 3 consists of a main transmission 4 and a sub-transmission 10 which are arranged concentrically, and the main transmission 4 has a forward transmission 4.
The sub-transmission 10 has a reduction ratio of 1.
Achieves two-speed shifting with a direct connection and a reduction ratio of 1 or more. The transmission 3 uses five clutches, three brakes, and three one-way clutches as frictional engagement elements.

The torque converter 2 includes a converter case 21 which is an input member connected to the crankshaft of the engine, and the converter case 21 supports a pump impeller 22. The hydraulic oil pressurized by the pump impeller 22 passes through the stator 23 supported by the case 30 of the transmission 3 via the one-way clutch 24, drives the turbine runner 27, and transmits power to the turbine output shaft 28. A lock-up clutch 26 for coupling is provided between the pump impeller 22 and the turbine output shaft 28, and the converter case 21 and the output shaft 28 are directly coupled when necessary.

The output shaft 28 of the torque converter 2 acts as an input shaft of the main transmission 4, and this input is transmitted to the clutch drum 40 of the first clutch 41.

The first clutch 41 is a forward clutch that is always activated when the vehicle is moving forward, and power is transmitted via the clutch hub 43 to an outer race 46 that is integrated with the clutch hub 43 of the first one-way clutch 45. Inner race 47 of one-way clutch 45 opens large sun gear shaft 48 and large sun gear 49 that is integrated with large sun gear shaft 48 . The first one-way clutch 45 operates between 1st and 4th speeds.

A second clutch 52 is disposed inside the drum 40 of the first clutch 41 . The second clutch 52 is a clutch that operates in the fourth and fifth speeds, and the clutch hub 53 is connected to an intermediate shaft 55, and the intermediate shaft 55 supports the carrier 54 of the planetary gear device 80.

The drum 40 of the first clutch 41 is the fifth clutch 65
drum 60. The fifth clutch 65 is a so-called coast clutch that transmits torque from the wheel side to the engine side, and its hub 67 is connected to the large sun gear shaft 4.
Combined with 8. A hub 74 of a third clutch 73 is connected to the drum 60 of the fifth clutch. The third clutch 73 is a so-called reverse clutch that operates during reverse travel, and the clutch drum 75 is connected to a small sun gear 78 via a small sun gear shaft 77. Third clutch 73
The drum 75 also serves as a brake drum for the first brake 71, and the first brake 71 is activated in the third and fifth speeds.

The planetary gear device 80 is a so-called Ravigneau-type planetary gear device that has two sun gears with different numbers of teeth and shares a carrier and a ring gear, but in the present invention, a Ravigneau-type gear train with a ring gear as an output is used. adopt.

A shaft 81 is connected to the carrier 54 which is integrally connected to the intermediate shaft 55.
and one end of the shaft 83 is attached. The shaft 81 supports a long pinion 82 and the shaft 83 supports a short pinion 84. The large sun gear 49 meshes with the long pinion 82, and the small sun gear 78 meshes with the short pinion 84, respectively.

The other ends of the shaft 81 and the shaft 83 are connected to a hub 85 of a third brake 93, and the hub 85 supports a brake disc of a friction plate type brake 93 on its outer periphery, and the brake plate is supported on the case 30 side. Ru. The third brake 93 operates during reverse travel and for engine braking in 1st and 2nd gears.

The inner peripheral portion of the hub 85 forms an outer race 91 of the second one-way clutch 90, and an inner race 92 of the one-way clutch 90 is integrally fixed to the support 35 fixed to the case 30. The second one-way clutch 90 operates in first and second speeds.

The short pinion 84 meshes with a ring gear 96 formed inside one end of a drum 95, and this drum 95 acts as an output member of the main transmission 4 and an input member of the sub-transmission 10.

That is, a ring gear 101 is provided inside the other end of the drum 95.
is integrally formed, and a shaft 105 is attached to this ring gear 101.
The pinion 102 supported by the pinion meshes with the pinion 102 . One end of the shaft 105 is supported by a carrier 103, and the carrier 103 is integrated with the output shaft 120. The other end of the shaft 105 is connected to the clutch hub of the fourth clutch 104, and the clutch drum 110 of the fourth clutch 104 is connected to the second brake 11.
Also serves as the second brake drum.

The fourth clutch 104 operates in the second to fifth speeds, and brings the sub-transmission 10 into a directly connected state. The second brake 112 is a reverse brake that operates during reverse travel and during engine braking in first gear, and employs a band type brake.

The other end of the shaft 108, which has a sun gear 106 that meshes with the pinion 102 formed at one end, forms an inner race 109 of a third one-way clutch 113.

The outer race 115 of the directional clutch 113 is attached to the case 30.
Fixed to. Drum 110 is integrally coupled to shaft 108.

FIG. 1A shows a cross section of an automatic transmission, and the automatic transmission, which is generally designated by the reference numeral 1, is composed of a torque converter 2 and a transmission 3. The torque converter 2 is installed in a case 20, and includes a drum-shaped converter case 21 connected to the crankshaft of the engine at the frontmost part (hereinafter, the side closest to the engine will be referred to as the "front side"). Converter case 21 includes engine crankshaft and pump impeller 22
The hydraulic oil pressurized by the pump impeller 22 drives the turbine runner 27 and returns to the pump impeller 22 through the stator 23 . The turbine runner 27 drives a turbine shaft 28 directly connected thereto.

The stay 23 is connected to the fixed part 3 via a one-way clutch 24.
A lock-up piston 25 is disposed between the turbine runner 27 and the drum-shaped converter case 21, and when necessary, a lock-up clutch 26 between the lock-up piston 25 and the converter case 21 is actuated to shut down the turbine. 28, which serves as an output shaft and an input shaft of the transmission, is directly connected to the converter case 21. An oil pump cover 31, a partition plate 32, and an oil pump housing 33 are arranged at the joint between the case 20 of the torque converter 2 and the case 30 housing the transmission 3.

The oil pump cover 31 consists of a face plate-like portion having an oil passage therein and a boss portion whose center portion protrudes rearward. The partition plate 32 supports the side surface of the rotating body of the oil pump 29 and defines an oil passage, etc., and forms the oil pump 29 within the oil pump housing 33 .

A rear end portion of the pump impeller 22 is coupled to a rotating body of an oil pump 29. The rotating body of the oil pump 29 is driven within the oil pump 29 to generate the necessary hydraulic pressure. The oil pump cover 31 has an oil pump 29 formed inside.
A face plate portion 311 that covers the front opening of the transmission case, and a hollow boss portion 312 that protrudes from the center of the transmission case into the inside of the case.
A hollow tubular support cylinder 34 is press-fitted into 2.

The support cylinder 34 supports the shaft 28 connected to the turbine runner 27 of the torque converter through a sleeve and a bearing inside the front and rear ends. This shaft 28 is an input shaft of the transmission 3, and the rear end of the shaft 28 is provided with a flange portion 281 that expands in the radial direction, and thrust bearings having the same diameter are interposed on both sides of the flange portion 281.

Flange 281. The outer circumference of the clutch drum 40 is connected to an inner cylinder 401 of the clutch drum 40, and a first clutch 41 is installed inside the clutch drum 40. The clutch drum 40 has a cylindrical shape with a supported front end and an open rear end, and rotates together with the input shaft 28 . Inner cylinder 40
The inner diameter side of 1 is a cylindrical oil passage member 315 that forms an oil passage and is fitted to the outer periphery of the boss portion 312 of the front support 31.
Slides and rotates against the outer circumferential surface of the

A large diameter piston 42 is provided on the outer circumference of the inner cylinder 401.
and a small diameter piston 56 is inserted in the form of a double piston. The large diameter piston 42 also serves as a cylinder for the small diameter piston 56, and is fitted inside the drum 40 in a fluid-tight manner. The large-diameter piston 42 is for operating the first clutch 41, and when the piston 42 is operated, the clutch plate is spline-engaged to the inside of the drum 40 and the clutch hub 43 is spline-engaged. Transmits power between the clutch disc and the clutch disc. A wall surface 431 extending in the axial direction is formed on the front side of the clutch hub 43, and thrust bearings are arranged on both sides of this wall surface 431. clutch hub 4
The inner diameter part of No. 3 forms the outer race 46 of the first one-way clutch 45, and the inner race 47 of the directional clutch 45 forms the rear end of the five-large sun gear shaft 48 that is integrally formed with the front end of the large sun gear shaft 48. Attach the large sun gear 49 via the serrations. The large sun gear shaft has a cylindrical shape, and the inner peripheral portions of its front and rear ends are supported by an intermediate shaft 55 using bearings.

A second clutch 52 and a small-diameter clutch piston 56 for actuating the clutch 52 are provided inside the large-diameter screw 1 42 in the radial direction. The clutch plate is spline engaged with the inner peripheral surface of the piston 42, and the clutch disk is spline engaged with a clutch hub 53 disposed inside.

The small diameter piston 56 transmits power between the large diameter piston 42 which rotates together with the drum 40 and the hub 53. The large diameter piston 42 and the small diameter piston 56 are always urged in the non-operating direction by a return spring 541 stretched between them and the inner cylinder 401.

The clutch hub 53 has a wall surface 5 extending from the rear end side to the shaft center.
31, the intermediate shaft 55 is spline-serrated connected to the vicinity of the distal end thereof. The tip of the intermediate shaft 55 is the input shaft 28
It is supported via a bearing on the inner diameter of the rear end. The rear end of the intermediate shaft 55 is supported by the front end of an output shaft, which will be described later, and a carrier 54 that extends in the radial direction is provided near the rear end of the intermediate shaft 55.

The open rear end of the drum 40 containing the first clutch 4 and the second clutch 52 is connected to the clutch drum 60 of the fifth clutch by a spline. A fifth clutch 6 is provided inside the clutch drum 6o, and includes a clutch plate splined to the inside of the clutch drum 60 and a clutch disc splined to a clutch hub 67 located inside the clutch drum.
Deploy 5. A lower end of a wall surface 671 formed from the front side of the clutch hub 67 toward the axis is coupled to the large sun gear shaft 48 . An inner cylinder 601 is formed on the inner circumferential side of the clutch drum 60, and the outer circumferential side of the inner cylinder 601 supports a piston 66 in a slidable manner. A return spring 661 is provided between the piston 66 and the inner cylinder 601.
will be established.

The inner peripheral side of the inner cylinder 601 is a stepped cylindrical member 771
It is rotatably supported. A clutch hub 74 is connected to the drum 6 on the opposite side of the clutch drum 60 from the fifth clutch 65.
0, and the clutch hub 74 supports a clutch disk constituting the third clutch 73 via a spline. Clutch play 1- of the third clutch 73
is supported by a drum 75 which also serves as an outer cylinder, and a belt-type first brake 71 is provided on the outer periphery of the drum 75. An inner cylinder 751 is formed on the inner circumference side of the drum 75, and a clutch 73 is formed on the outer circumference side of the inner cylinder 751.
A piston 76 that operates is supported in a movable manner. A return spring 761 is provided between the inner cylinder 751 and the piston 76.

The distal end of the inner cylinder 751 is spline engaged with the cylindrical member 771 and the inner periphery of the two cylindrical members 771 is connected to the front end of the small sun gear shaft 77, so that the drum 75 rotates together with the small sun gear shaft 77. The small sun gear shaft 77 is cylindrical and has a small sun gear 78 formed at its rear end. The inner peripheral portions of the front and rear ends of the small sun gear shaft 77 are supported by the large sun gear shaft 48 via bearings.

A central support member 35 is provided at the center inside the case 30. This central support member 35 has a flange portion that engages with the inner peripheral portion of the case, a stepped boss formed in the inner diameter direction of the flange portion that protrudes to the front side, and a short boss that protrudes to the rear side, and protrudes to the front side. A small-diameter ring member 36 and a large-diameter ring member 37 are respectively fitted to the outer periphery of the stepped portion of the boss.

The small diameter ring member 36 rotates and slides on the inner circumference of the cylindrical member 771 at its outer circumference, and the large diameter ring member 37 rotates and slides on the inner circumference of the inner cylinder 751 of the drum 75 at its outer circumference via a bearing. It is rotatably supported by a member 37.

Since the intermediate shaft 55 supports the large sun gear shaft 48 and the large sun gear shaft 48 supports the small sun gear shaft 77, this shaft portion has a triple shaft structure.

The rear side of the flange portion of the central support member 35 forms a cylinder, into which a piston 94 for actuating a third brake 93 is fitted. An iron sleeve 38 is press-fitted into the inner diameter of the central support member 35, and the rear end of the sleeve 38 is formed into a ring shape, into which the inner race 92 of the second one-way clutch 90 is press-fitted. A return spring 941 is interposed between the inner race 92 and the piston 94. The outer race 91 of the second one-way clutch 90 also serves as the hub of the third brake 93, and a brake disc is spline-engaged to its outer periphery. The brake plate of the third brake 93 is fitted onto the inner periphery of the case 3o with a spline.

A ring member 911 is fixed to the rear side of the seven outer races 9j of the second one-way clutch 90.
1 and the carrier 54 of the intermediate shaft 55.
1 and pinion shaft 83. A plurality of these pinion shafts 81 and 83 are provided, and the pinion shafts 81 and 83 are provided in plural numbers.
supports a long pinion 82, and a pinion shaft 83 supports a short pinion 84. The short pinion 84 meshes with the small sun gear 78 and also meshes with the ring gear 96.
The long pinion 82 meshes with the large sun gear 49.

The ring gear 96 is fixed to the front end of the drum 95,
The inner hole formed in the wall surface 951 of the drum 95 has a gap between it and the intermediate shaft, and both sides of the inner hole are supported by thrust bearings. The ring gear 96 has a ring gear 101 at its rear end on the opposite side with this wall surface 951 in between.

The ring gear 101 provides input to the auxiliary transmission, and as described above, the auxiliary transmission is a reduction gear having one set of planetary gear trains, and is of the type that takes the input of the ring gear from the carrier and outputs it. . A binion 102 that meshes with a ring gear 101 meshes with a sun gear 106, and the binion 102 is supported by a shaft 105. The front end of the shaft 105 is supported by a carrier 103 formed at the front end of an output shaft 120, and a hub 107 of a fourth clutch 104 is provided at the rear end of the shaft 105. The clutch hub 107 supports a clutch disk by a spline, and supports a clutch plate by a spline on the inner circumference of an opposing drum 112.

A second brake 112 is arranged on the outer periphery of the drum 110.

A stepped cylindrical rear shaft support member 125 that protrudes toward the front of the case 30 is attached to the rear wall of the transmission case 30, and the inner circumference of the cylindrical sun gear shaft 108 is attached to the outer periphery of the rear shaft support member 125. Support the periphery. The sun gear shaft 108 has a sun gear 106 meshing with the binion 105 at its front end, and the rear part of the sun gear shaft 108 is integrated with the drum 110. A piston 116 is fitted inside the drum 110,
A return spring 117 is provided between the piston 116 and the sun gear shaft 108.

An inner race 109 of a third one-way clutch 113 is formed on the rear side of the drum 110 of the sun gear shaft 108, and an outer race 115 of the one-way clutch 113 is spline supported inside the case 30.

A rear case 301 that supports the output shaft 120 is attached to the rear end of the case 30, and the output shaft is supported by a bearing arranged inside the rear end of the case 301 inside the front end of the rear shaft support member 125. The outer diameter portion of the rear end of the intermediate shaft 55 is supported by a bearing.

The output shaft 120 is provided with a parking gear 12G and a speedometer drive gear 131.

The parking gear 126 cooperates with a pawl 127 disposed on the fixed side to achieve a parking brake, and the drive gear 131
drives the speedometer.

A flange 129 is integrally provided on the parking gear 126, and the rotation speed of the output shaft 120 is obtained by detecting passage of the flange through a slit with a sensor 130.

At the rear end of the output shaft 120 is a connecting member 135 to the axle shaft.
is inserted and fixed to the output shaft 120 with a nut 136. A hydraulic control device (not shown) is provided at the bottom of the transmission case 30 to control the operation of the clutch and brake of the transmission. The hydraulic control device is covered with a cover 11 that also serves as an oil pan.

Next, referring to FIG. 1B, the arrangement of bearings used in supporting parts of the automatic transmission components, the arrangement of seals provided in the hydraulic circuit, etc. will be explained.

The front part of the input shaft 28 is connected to the bush 2 by a support tube 34.
At 82, the rear portion is supported by a radial bearing 283. The rear end of the input shaft 28 supports the front end of the intermediate shaft 55 with a radial bearing 551.

The rear end of the intermediate shaft 55 is output by a radial bearing 554!
It is supported by the front end of Ill 120. Output shaft 120
A radial bearing 120a is disposed between the rear shaft support member 125 and the rear case 301.

120e.

Intermediate shaft 55 supports large sun gear shaft 48 with radial bearings 552 and 553, and large sun gear shaft 48 supports small sun gear shaft 77 with radial bearings 481 and 482. A radial bearing 772 is disposed on the outer circumference of the hub 771, and a radial bearing 371 is disposed on the outer circumference of the large-diameter ring member 37.

A radial bearing 1 is also provided on the outer periphery of the rear support member 125.
25h and 125g are arranged.

Thrust bearings are installed in rotating parts that are subjected to axial thrust, and these bearings are numbered 281a in order from the front side of the transmission.
, 531a, 431a, 431b.

9 shown as 47a, 49a, 49b, 951a, 951b
Thrust bearings are installed in important parts.

These thrust bearings can be standardized in size to reduce costs.

Thrust bearings 103b and 125j are also provided between the rear shaft support member 125 and the sun gear shaft 108 supported.

Next, a check ball is provided on the piston that operates each clutch, and a hydraulic sealing means is provided.

A large-diameter piston 42 housed in a clutch drum 40 integrated with the input shaft 28 has a pair of O-rings 42p installed between it and the sliding surface of the cylinder, and a pair of oil seal rings on both sides of the oil path to the piston 42. Attach 316a. A check ball 4 is provided on the wall of the drum 40 facing the piston 42.
Attach 0g. A small-diameter piston 56 housed within the large-diameter piston 42 has a check ball 56a and is fitted with a pair of O-rings 56p. A pair of oil seal rings 317a are also installed on both sides of the oil passage to the small diameter piston 56.

The same applies to the two pistons disposed within the two clutch drums supported by the central support member 35.

Since hydraulic pressure is supplied to the piston 66 disposed on the front side from the central support member 35 via the small-diameter ring member 36 and the hub 771, oil seal rings 36a and 7 are provided on both sides of the oil passage.
71a is arranged. The piston 66 has a pair of O-rings 66
p and a check ball 66a. Since the piston 76 supplies hydraulic pressure through the large-diameter ring member 37, oil seal rings 37a are provided on both sides of the oil passage, and the piston 76 has a pair of O-rings 76p and a check ball 76a.

The piston 94 disposed on the back surface of the central support member 35 also has a pair of O-rings 94P.

An oil seal ring 125n is also attached to the oil passage to the piston 116 that supplies hydraulic pressure via the rear shaft support member 125, and the piston 116 has a pair of O-rings 116p and a check ball 116a.

In order to obtain information for speed change control, a rotation sensor 140 is installed facing the outer periphery of the drum 95 connecting the main transmission and the sub-transmission.
At the same time, a rotation sensor 145 is arranged opposite to the outer periphery of the clutch drum 4o that is integrated with the input shaft 28.

The operation of the single automatic transmission will be explained below.

This automatic transmission has five forward speeds and one reverse speed. Table 1 shows each speed and the operation of the frictional engagement elements that achieve the speed change.

Table 1 (0) shows operation during engine braking. Table 1 shows the gears in the vertical section and the friction engagement elements in the horizontal shelves. The ○ mark indicates that the friction engagement elements are operating. , (0) indicates that it operates during engine braking.

Reference numbers 41, 52, and 73104.65 indicate the first to fifth clutches, respectively, and reference numbers 71, 112.9
3 indicates the first to third brakes, respectively, and numerals 45, 90, and 113 indicate the first to third one-way clutches, respectively.

Figures 3 to 8 show the power transmission paths to each gear stage, and the thick line part is the path where the power is transmitted.
The shaded area indicates the element to be fixed.

Figure 3 shows the power transmission path at 1st speed, and shows the input shaft 28.
The power is transmitted from the first clutch 41 to the first one-way clutch 45 and moves the large sun gear shaft 48 and large sun gear 49. Since the long pinion shaft 81 with which the large sun gear 49 meshes is fixed by the action of the second one-way clutch 90, the rotation of the large sun gear 49 is decelerated and transmitted to the ring gear 96. This rotation is transmitted to ring gear 101 via drum 95. In the 1st speed, the sun gear shaft 108 of the planetary device constituting the sub-reducer is fixed by the action of the third one-way clutch 113, so the rotation input from the ring gear 101 is decelerated and transmitted to the carrier 103 and output shaft 120. Output from.

That is, in the first speed, the rotation that has been decelerated by the main transmission is further decelerated by the sub-transmission and then output.

FIG. 4 shows the power transmission path in 2nd speed, and the same path as in 1st speed is followed from the output shaft of the main transmission to the drum 95, which also serves as the human power shaft of the auxiliary transmission.

The fourth clutch 104 of the auxiliary transmission operates to maintain the auxiliary transmission in a directly coupled state, and the input from the drum 95 is transmitted to the output shaft 120 as is.

FIG. 5 shows the power transmission path at the third speed, in which the first brake 71 operates to fix the small sun gear shaft 77. The power of the large sun gear shaft 48 is decelerated from the large sun gear shaft 49 and transmitted to the ring gear. The reduction ratio at this time is small sun gear 78
, the number of teeth of the large sun gear 49 and ring gear 96. The fourth clutch 104 is operated to maintain the direct connection state of the sub-transmission, and the power of the drum 95 is directly transmitted to the output shaft.

FIG. 6 shows the power transmission path at the fourth speed, where both the first clutch 41 and the second clutch 52 operate. Therefore, the power of the input shaft 28 is transferred to the intermediate shaft 55 and the large sun gear shaft 4.
Since the planetary gear train does not move relative to each other, the intermediate shaft 55 and the large sun gear shaft 48 are directly connected to the drum 95. The auxiliary transmission is also maintained in a directly connected state, and eventually the input shaft 28 and output shaft 120 are directly connected.

FIG. 7 shows the power transmission path at the fifth speed, in which the second clutch 52 operates and the power from the input shaft 28 is transmitted to the intermediate shaft 55. The first brake 71 operates and the small sun gear shaft 7
7 is fixed, the rotation of the carrier 54 integrated with the intermediate shaft 55 is accelerated and transmitted to the drum 95. Since the direct connection state of the sub-transmission is maintained, the power of the drum 95 is directly transmitted to the output shaft 120.

The fifth speed is an overdrive in which the rotational speed of the input shaft 28 is increased and transmitted to the output shaft 120.

FIG. 8 shows the power transmission path during reverse movement, in which the third clutch 73 operates to transfer the power from the input shaft 28 to the small sun gear shaft 77.
tell to. Since the third brake 93 operates and fixes the short pinion shaft 83 that meshes with the small sun gear shaft 78,
The rotation of the small sun gear shaft 78 is reversed with deceleration and transmitted to the ring gear 96 and drum 95. Since the second brake 112 of the sub-transmission is also activated and fixes the sun gear shaft 108, the power input to the ring gear 101 is decelerated and transmitted from the carrier 103 to the output shaft 120.

Therefore, the speed change state in which the auxiliary transmission further decelerates the vehicle during reversing is shown in the speed diagram of FIG.

In the figure, reference numeral 4 indicates a main transmission equipped with a Ravigneau planetary gear mechanism, and reference numeral 10 indicates an auxiliary transmission that achieves deceleration (underdrive).

The gear ratio of each transmission is determined by appropriately selecting the number of gear teeth of the planetary gear train, but in this transmission, the sub-transmission that acts as a speed reducer is activated only during first speed and reverse. The reason for this is to avoid, as much as possible, control to engage and disengage two clutches and brakes at the same time.

FIG. 10 shows details of a servo device for a reduction gear of an automatic transmission according to the present invention and its support structure, and for the sake of explanation, only the upper half of the servo device from the center line of FIG. 1 is shown.

As described above, the reducer incorporating this servo device includes a ring gear 101 and a pinion 102 that are input members, and a carrier 103 that is integrated with a shaft 105 that supports the pinion 102.
．． Output shaft 120 integrated with carrier 103, sun gear 10
6, when the sun gear is stopped, the input rotation of the ring gear 101 is decelerated and transmitted to the output shaft 120, and when the sun gear is released and the carrier and the sun gear are integrally coupled, the input rotation of the ring gear 101 is reduced.
1, the pinion 102 and the sun gear 106 are in a directly connected state where they rotate together, and the reduction ratio is 1, and the ring gear 10
1 is directly transmitted to the output shaft 120. Therefore, the servo device has the function of rotatably supporting the sun gear,
It is necessary to provide a brake function to stop and release the sun gear, a clutch function to connect and isolate the carrier and the sun gear, and a one-way clutch function to prevent the sun gear from reversing.

The servo device of the present invention includes a cylindrical sun gear shaft 108 with a sun gear 106 formed on the outer periphery of the front end, and a 5-sun gear shaft 10.
8 A radial wall 110d provided at the rear and a sun gear shaft 1
A cylindrical inner race 109 formed at the rear end of 08;
It consists of a drum 110 integrally formed on the outer circumference of the drum 110, and the outer circumferential surface of the drum 110 cooperates with a brake band 112a disposed around the second brake 11.
2.

A clutch plate 110a is attached to the inside of the drum 110 via a spline, and a stopper 110 is attached to the front end of the clutch plate 110a.
b. A fourth clutch 104 is constructed by spline-engaging the inner circumference of a clutch disk 107a held between clutch plates 110a and a clutch hub 107. The clutch hub 107 is integrated with the rear end of the shaft 105 that supports the pinion 102, and the carrier 103 that supports the front end of the shaft 105 is integrated with the front end of the output shaft 120 at its inner circumference.

The sun gear shaft 108 has an inner cylinder 108a that guides a piston 116 that operates the fourth clutch 104 on the outer periphery of the center thereof, and the piston 116 and a wall 110d.
A hydraulic chamber is formed between the two.

The cylindrical portion at the rear end of the sun gear shaft 108 has a third outer peripheral portion.
The inner race 109 of the one-way clutch 113 is configured, and the outer periphery of the outer race 115 of the one-way clutch 113 is formed by a spline 30d provided inside the case 30 of the transmission.
and position it with the stopper 30e.

Next, the support structure of the servo device of the present invention will be explained.

A wall 302 is formed perpendicularly to the central axis of the transmission at the rear end of the transmission case 30, and a rear case is attached thereto. A hole 303 is provided in the center of 811.302, the rear shaft support member 125 is inserted into this hole 303, and the bolt 305 is inserted.
It will stick.

The rear shaft support member 125 is a stepped cylindrical member that includes stepped portions 125b and 125C1125d whose outer diameters decrease sequentially from a base portion 125a having a maximum outer diameter toward the front, and a base portion 125a.
A boss portion 125f that protrudes rearward from the base is coaxially formed. The boss portion 125f that protrudes rearward is attached to the wall 3 of the case 30.
The centering accuracy of the rear shaft support member 125 is ensured by engaging the hole 303 provided in the hole 303 in the rear shaft support member 125.

The rear shaft support member 125 supports bearings 125g, 12 by its base 125a and the outer periphery of the stepped portion 125d at the tip.
5h to support the sun gear shaft 108 of the sub-transmission.

A thrust bearing 125j is disposed on a vertical wall surface formed between the base portion 125a and the stepped portion 125b to receive thrust applied to the sun gear shaft 108. Therefore, the sun gear shaft 108 is reliably supported by the rear shaft support member 125 in both the radial direction and the thrust direction.

The sun gear shaft 108 is provided with an oil passage 108b for supplying and discharging hydraulic oil to the piston 116, and an oil passage 125m is also formed in the rear shaft support member 125 corresponding to the oil passage 108b. Since the sun gear shaft 108 rotates, oil seal rings 125nti are fitted on both sides of the oil passage 125m. The wall 302 of the case 30 also communicates with the hydraulic control device via an oil passage (not shown) that communicates with the oil passage 125m of the rear shaft support member 125. An oil passage 1 for lubricating the third one-way clutch 113 is also provided in the inner race 109 at the rear end of the sun gear shaft 108.
09a, and communicates with an oil passage 125p for supplying lubricating oil formed in the rear shaft support member 125.

The inner peripheral portion of the stepped portion 125d at the tip of the rear shaft support member 125 supports the front portion of the output shaft 120 via the bearing 120a. The output shaft 120 has an oil passage 120d at its center, and its rear portion is supported by a bearing on the rear case. The inner peripheral portion of the portion of the output shaft 120 supported by the bearing 120a supports the rear end portion of the intermediate shaft 55 via the bearing 554.

〔Effect of the invention〕

As described above, the present invention provides a servo device for an automatic transmission equipped with a TL star gear device for deceleration in which the input member is the ring gear and the carrier is the output member, in which the brake for fixing the sun gear during deceleration is used as a band brake. The brake drum and sun gear shaft are integrally constructed by a wall surface, and the clutch and its piston that connect the sun gear and carrier are housed inside the drum, so the servo device can be constructed compactly and the axial length can be shortened. . Also.

Since the rear end of the sun gear also serves as the inner race of the one-way clutch, the servo device can be made more compact in this area as well.

Furthermore, as a structure for supporting this servo device, there are two
Since we adopted a structure in which the inner circumferential surface of the sun gear shaft is rotatably supported front and rear through individual bearings, the entire servo device is supported reliably, and there is no risk of the servo device tilting even when the handbrake is activated.

Since the inner race of the one-way clutch also has a bearing located on its inner peripheral surface, concentricity is high and wear caused by rattling can be prevented.

[Brief explanation of the drawing]

FIG. 1A is a sectional view of the automatic transmission of the present invention, FIG. 1B is a sectional view showing the arrangement of bearings and seals, and FIG. 2 is an explanatory diagram showing an outline of the automatic transmission. FIG. 3 is an explanatory diagram showing the power transmission line at the time of first speed, and FIG. 4 is an explanatory diagram showing the power transmission line at the time of second gear. Figure 5 is an explanatory diagram showing the power transmission line at 3rd speed, Figure 6 is an explanatory diagram showing the power transmission line at 4th gear, and Figure 7 is an explanatory diagram showing the power transmission line at 5th gear. FIG. 8 is an explanatory diagram showing the power transmission system during reverse movement, FIG. 9 is a diagram showing the gear ratio, and FIG. 10 is a sectional view of the main part. 1... Automatic transmission, 2... Torque converter, 4...
・Main transmission, 10... Sub-transmission, 28...
......Input shaft, 30...Transmission case, 35...Central support member, 48...Large sun gear shaft, 55・・・・・・
...Intermediate shaft, 77...Small sun gear shaft, 101...Ring gear, 103...
......Carrier, 104...Fourth clutch, 108...
...Sun gear shaft, 109...Inner race, 110...
...Drum, 112...Second brake, 113...
...Third one-way clutch, 115...
...Outer race, 120...Output shaft, 125...Rear shaft support member. Patent originator: Aisin AW Co., Ltd. Agent: Patent attorney: 5 Akira Meiki (2 others)

Claims (1)

[Claims] (1) In a servo system for an automatic transmission consisting of a main transmission equipped with a starting device and a planetary gear system, and an auxiliary transmission equipped with a planetary gear system for reduction, a ring gear connected to an input member and a ring gear connected to an output shaft are used. The servo device of a planetary gear system for reduction equipped with a carrier has a cylindrical sun gear shaft with a sun gear formed at the tip, a radial wall provided at the rear of the sun gear shaft, and a drum provided on the outer periphery of the wall. and a cylindrical inner race formed at the rear end of the sun gear shaft.The outer peripheral surface of the drum also serves as the brake drum of the band brake that operates during deceleration, and the inside of the drum contains a clutch that operates when the carrier and sun gear are directly connected. The outer race of the one-way clutch, which houses the piston for clutch operation and is fitted on the outer circumferential surface of the inner race and operates during deceleration, is engaged with the inside of the transmission case, and is formed on the rear wall of the transmission case. The stepped cylindrical rear shaft support member to be attached to the hole has a base portion with the maximum outer diameter, a plurality of stepped portions whose outer diameters are gradually reduced from the base toward the inside of the case, and a stepped portion with the base portion sandwiched between the steps. a boss portion protruding on the opposite side from the attached portion, and the stepped portion rotatably supports the inner peripheral portion of the sun gear shaft of the servo device via bearings fitted to the front and rear ends of the outer peripheral portion. A support structure for a servo device of an automatic transmission, characterized in that the boss portion is mounted by engaging a hole formed in a rear wall surface of the case with a spigot.