JPH02125131A - Structure for coast clutch and reverse clutch of automatic transmission - Google Patents

Abstract

PURPOSE:To save a space and reduce the number of parts by arranging a coast clutch and a reverse clutch in series and integrally storing the coast clutch with small transfer torque in the drum of the reverse clutch. CONSTITUTION:A coast clutch 65 transmitting the torque from driving wheels to the torque converter side and a reverse clutch 73 arranged in series behind it and operated at the time of reverse are provided in a drum 60 integrally rotated with the input shaft of an automatic transmission. The outer periphery of the drum 75 of the reverse clutch 73 serves as the drum of a hand brake 71 for controlling forward stages, the coast clutch 65 is stored at the inside front of the drum 75, and the reverse clutch 73 transmitting the torque between the drum 60 of the coast clutch 65 and its drum 75 is stored at the inside rear of the drum 75. The number of parts is reduced, and the structure can be made compact.

Description

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

[Prior art]

In an automatic transmission equipped with a starting device and a planetary gear system,
An automatic transmission in which frictional engagement elements such as a clutch are arranged centrally at the front part of the transmission and a planetary gear device is arranged at the rear part of the transmission is described, for example, in a published technical document S A E T
880 of electrical paper 5eries
480.

The automatic transmission shown in this technical document includes a direct clutch, coast clutch, forward clutch,
The four clutches of the reverse clutch are arranged in series from the front side of the transmission, and a band brake that operates at 2nd and 4th gear is arranged around the outer periphery of the drum that houses the reverse clutch inside. . Since this handbrake is used frequently and requires a large heat capacity, it is desirable to have a large drum width.

Since the forward clutch disposed in front of the reverse clutch is always engaged during forward movement, it is necessary to have a large capacity and a large outer diameter of the drum.

Therefore, with this clutch and band brake arrangement structure, it is difficult to shorten the axial dimension.

[Problem 1iA to be solved by the invention] In order to shorten the axial dimension of an automatic transmission, it is conceivable to arrange the clutch drums in an overlapping manner.
For band brakes, it is desirable to have a large drum width, and to ensure clutch capacity, it is necessary to satisfy two contradictory conditions: the outer diameter of the clutch drum should be as large as possible. .

An object of the present invention is to provide a coast clutch and reverse clutch structure that satisfies the above-mentioned conditions and shortens the axial dimension by disposing a coast clutch with a small capacity just before the reverse clutch.

[Means to solve the problem]

The present invention includes a drum (60) that rotates together with the input shaft of an automatic transmission, a coast clutch (65) that is provided inside the drum (60) and transmits torque from the drive wheels to the torque converter side, A reverse clutch (65) that operates when going backwards is installed in series behind the coast clutch (65).
73), and the drum (73) of the reverse clutch (73).
The outer peripheral surface of the band brake (75) for forward gear control is
), and accommodates the coast clutch (65) inside and in front of the drum (75) of the reverse clutch (73).
The reverse clutch (73) that transmits torque between the drum (6o) of the coast clutch and the drum (75) of the reverse clutch is housed at the inner rear of the clutch.

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, in which the automatic transmission 1 includes a torque converter 2, which is a starting device, and a transmission 3.
Equipped with. The transmission 3 is a main transmission 4 arranged concentrically.
and an auxiliary transmission 10, the main transmission 4 achieves four forward speeds and one reverse speed, and the auxiliary transmission 10 achieves two speeds, a direct connection with a reduction ratio of 1 and a reduction ratio of 1 or more. Achieve. 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 that is an input member connected to the crankshaft of the engine, and the converter case 21 drives 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. An inner race 47 of the one-way clutch 45 drives a large sun gear shaft 48 and a large sun gear 49 that is integrated with the 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 attached 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 to directly connect the two sub-transmissions 10. 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, and fixes an outer race 115 of the - direction clutch 113 to the case 30. drum 1
10 is integrally coupled to shaft 108.

Figure 1 shows a cross section of an automatic transmission, and the whole is denoted by 1.
The automatic transmission shown by is composed of a torque converter 2 and a transmission 3. The torque converter 2 is installed in a case 2o, and includes a drum-shaped converter case 21 connected to the engine crankshaft at the frontmost part (hereinafter, the side closer to the engine is referred to as "front side j").Converter case 2
1 connects and drives an engine crankshaft and a pump impeller 22, and hydraulic oil pressurized by the pump impeller 22 drives a turbine runner 27.

It passes through the stator 23 and returns to the pump impeller 22 .

The turbine runner 27 drives a turbine shaft 28 directly connected thereto.

23 stators fixed part 30 via 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 reduce the turbine output. The converter case 21 is directly connected to the shaft 28 which serves as the input shaft of the transmission. An oil pump cover 31, a partition plate 32, and an oil pump housing 33 are arranged at the joint between the case 2o 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 @ 34 supports the shaft 28 connected to the turbine runner 27 of the torque converter through a sleeve or 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.

The outer peripheral portion of the flange 281 is coupled to the inner cylinder 401 of the clutch drum 40, and the first clutch 41 is installed inside the clutch drum 4o. 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 401
The inner diameter side of the front support 31 slides and rotates on the outer circumferential surface of a cylindrical oil passage member 315 that forms an oil passage and is fitted to the outer circumference of the boss portion 312 of the front support 31 .

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
3 forms an outer race 46 of the first one-way clutch 45, and an inner race 47 of the directional clutch 45 is formed integrally with the front end of the large sun gear shaft 48. A large sun gear 49 is attached to the rear end of the large sun gear 48 via 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 5 is disposed inside the large diameter piston 42 in the radial direction.
2 and a small-diameter clutch piston 56 that operates the clutch 52. Clutch plate 1 is spline engaged with the inner circumferential 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 41 and the second clutch 52 is connected to a fifth clutch by a spline.
The clutch drum 60 of the clutch is coupled to the clutch drum 60 of the clutch. A fifth clutch 65 is provided inside the clutch drum 60 and includes a clutch plate that is spline-engaged with the clutch drum 60 and a clutch disc that is spline-engaged with a clutch hub 67 located inside the clutch drum.
Deploy. 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.

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 clutch drum 60 on the opposite side of the fifth clutch 650.
0, and the clutch hub 74 supports a clutch disk constituting the third clutch 73 via a spline. The clutch plate 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.
It slidably supports a piston 76 that operates. A return spring 761 is provided between the inner cylinder 751 and the piston 76.

The tip of the inner cylinder 751 is spline engaged with the cylindrical member 771, and the inner circumference of the cylindrical member 771 is connected to the small sun gear @
Since the drum 75 is connected to the front end of the small sun gear shaft 77, 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. The 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 forward, and a short boss that protrudes rearward.
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 that projects forward. The small diameter ring member 36 has a cylindrical member 771 at its outer periphery.
The large diameter ring member 37 is rotatably supported by the ring member 37 at its outer circumference via the inner circumference of the inner cylinder 751 of the drum 75 and a bearing.

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 part 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-sided clutch 90 also serves as the hub of the third brake 93, and a brake disc is spline-engaged with the outer periphery of the outer race 91. The brake plate of the third brake 93 is fitted onto the inner periphery of the case 30 with a spline.

A ring member 911 is fixed to the rear side of the outer race 91 of the second one-sided clutch 90.
1 and the carrier 54 of the intermediate shaft 55.
and supports the pinion shaft 83. These pinion shafts 8
A plurality of pinion shafts 1.83 are provided, and the pinion shaft 81 supports a long pinion 82 and the pinion shaft 83 supports a short pinion 84. The short pinion 84 meshes with the small sun gear 78 and the ring gear 96, and 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 pinion 102 that meshes with a ring gear 101 meshes with a sun gear 106, and the pinion 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 that meshes with the pinion 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 bearings arranged inside the front end of the rear shaft support member 125 and inside the rear end of the rear case 301. 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 126 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.

The operation of this 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 gears on the vertical side and frictional engagement elements on the horizontal shelves. The O mark indicates that the frictional engagement elements are operating. , (0) indicates that it operates during engine braking.

The codes 41, 52, 73°104.6'5 are the first
The fifth clutch from the clutch is shown, and the reference numeral 71,112
．． Reference numerals 93 indicate first to third brakes, and numerals 45, 90, and 113 indicate first to third one-way clutches, respectively.

Figures 3 to 8 show the power transmission paths at each gear stage, and the thick line portion 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-sided clutch 45 and drives the large sun gear shaft 48 and the 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-sided 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 first speed, the sun gear shaft 108 of the planetary device constituting the auxiliary speed reducer is fixed by the action of the third one-sided 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 up to the drum 95, which also serves as the output shaft of the main transmission and the input 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 of the auxiliary 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. 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, when reversing, the auxiliary transmission further decelerates the vehicle.

This speed change state 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 the clutch structure of the present invention,
For purposes of explanation, only the portion above the centerline of the automatic transmission of FIG. 1 is shown.

A drum 60 is engaged with the rear end of the drum 40, which rotates together with the input shaft of the automatic transmission, through a spline 60b.

This drum 6o includes a cylindrical outer cylinder 60d, a rear end At60e of the outer cylinder 60d, and an inner cylinder 6.
01, a piston 66 is fluid-tightly inserted between the cylinder surface 60f formed between the rear part of the inner peripheral surface of the outer cylinder and the rear end wall 60e, and the outer peripheral surface of the inner cylinder 601, and a return spring 661 will be established. A clutch plate 60a is fitted onto the inner peripheral portion of the outer cylinder 60d so as to be slidable in the axial direction via a spline 60h, and its front end is positioned by a stopper 60j. A clutch disk 67a sandwiched between clutch plates 60a is slidably fitted to an opposing clutch hub 67 by a spline 67b, thereby forming a fifth clutch 65.

The front end of the hub 67 has an annular wall 671 extending in the inner circumferential direction.
Thus, the inner peripheral end of the annular wall 671 is fixed to the inner race 47 of the first one-way clutch.

Therefore, the hub 67 rotates together with the inner race 47 that is integral with the large sun gear shaft 48.

The front end of the inner cylinder 601 has a stepped cylindrical portion 601a with a small diameter, and the inner circumferential surface of this cylindrical portion 601a is rotatably supported by a cylindrical hub 771 integrated with the large sun gear shaft foot through a bearing 771a. Ru. An annular thrust washer 771b is interposed between the stepped portion of the inner cylinder 601 and the corresponding stepped portion of the hub 771 to receive the thrust force applied to the inner cylinder 601. The inner circumference of the hub 771 is a small-diameter ring member 3 press-fitted into the central support member 35.
6 and is slidably supported.

A large-diameter drum 75 is placed over the outside of the drum 6o constituting the fifth clutch 65. This drum 75 has a cylindrical shape, and an outer cylinder 75b is provided at the inner peripheral part of the rear part of the drum 75.
are provided integrally. Rear end wall 7 of outer cylinder 75b
5d is integrally coupled with the inner cylinder 751 at the inner circumference,
A piston 76 is fitted between the outer cylinder 75b and the inner cylinder 751 in a fluid-tight manner. A return spring 761 is provided between the piston 76 and the inner cylinder 751.

A clutch plate 75a is spline engaged with the inner peripheral portion of the drum 75, and its front end is regulated by a stopper 75c.

The inner periphery of the clutch disc 74a sandwiched between the clutch plates 75a is spline engaged with an opposing hub 74 to constitute the third clutch 73, and the hub 74 is connected to the drum 60 constituting the fifth clutch 65. It is integrally fixed to the rear surface of the rear end wall 60e.

The inner cylinder 751 is rotatably supported by a large-diameter ring member 37 press-fitted into the central support member 35 via a bearing 37a. Central support member 35 and drum 75
An annular thrust washer 75f is provided between the rear end walls 75d.
is inserted to receive the thrust force of the drum 75. The distal end of the inner cylinder 751 engages with the rear end outer circumference of the hub 771 via a spline 752 .

A band 71a is arranged on the outer peripheral surface of the drum 75 with a specified gap, and the first brake 71
Configure.

The hydraulic chamber of the piston 76 that operates the third clutch 73 is connected to the oil passage (not shown) formed in the central support member 35 through the oil passage 37b of the large-diameter ring member 37, and the oil formed in the inner cylinder 751. Hydraulic oil is supplied through passage 751a.

The hydraulic chamber of the piston 66 that operates the fifth clutch 65 is connected to the oil passage (not shown) formed in the central support member 35 through the oil passage 36a of the small-diameter ring member 36, to the oil passage 771c of the hub 771, to the inner Hydraulic oil is supplied through the oil passage 601d of the cylinder 601.

As mentioned above, the third clutch 73 is a so-called reverse clutch that is activated when moving backward, and the first brake 71 installed on the drum of the third clutch 73 operates at the third and fifth speeds. It has high brakes. Therefore, the first brake 71 generates a lot of heat and requires a brake with a large heat capacity. For this reason, it is desirable that the width of the drum 75 is also large.

The fifth clutch 65 is a so-called coast clutch that operates in the first to fourth speeds to transmit torque from the driving wheels to the engine, and the transmitted torque is relatively small.

Therefore, the capacity of the clutch can be small, and the elements constituting the clutch can also be made small.

Since the present invention has a structure in which the coast clutch and the reverse clutch are arranged in order from the engine side, the entire coast clutch is housed inside the drum of the reverse clutch that also serves as the first brake, making use of the above-mentioned characteristics of the clutch. can be adopted. With this configuration, the axial length can be shortened and space can be used effectively.

〔Effect of the invention〕

As described above, by arranging the coast clutch and the reverse clutch in series, the present invention miniaturizes the coast clutch, which requires small transmission torque, and houses it integrally within the drum of the reverse clutch, thereby saving space and reducing the number of parts. can be reduced. Further, since the outer circumferential surface of the drum of the reverse clutch also serves as the drum of the band brake for forward gear control, it has the effect of achieving further compactness.

[Brief explanation of drawings]

Fig. 1 is a sectional view of the automatic transmission of the present invention, Fig. 2 is an explanatory diagram showing an overview of the automatic transmission, Fig. 3 is an explanatory diagram showing the power transmission line at 1st speed, and Fig. 4 is An explanatory diagram showing the power transmission line at 2nd speed, FIG. 5 is an explanatory diagram showing the power transmission line at 3rd gear, and FIG. 6 is an explanatory diagram showing the power transmission line at 4th gear.
Fig. 7 is an explanatory diagram showing the power transmission system in 5th gear, Fig. 8 is an explanatory diagram showing the power transmission system in reverse, Fig. 9 is a diagram showing the gear ratio, and Fig. 10 is an explanatory diagram showing the power transmission system in 5th gear. FIG. 3 is a cross-sectional view of main parts. 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, 60...Drum, 65... ......Fifth clutch (coast clutch), 66...Piston, 71...First brake, 73...
...Third clutch (reverse clutch), 75
......Drum, 76...Piston, 77...Small sun gear shaft, 120...
...Output shaft. Patent applicant: Aisin AW Duburi Ni Co., Ltd. Agent: Patent attorney: 5 Akira Meiki (2 others) Figure 1: Onori Hen Takara 1B Association. Output No. 1O Figure 1゜2゜3゜4゜Procedural amendment (method) % formula % Display of incident 1988 Patent application No. 277225 Name of invention Person who makes structural corrections of coast clutch and reverse clutch of automatic transmission Relationship to the case Patent applicant

Claims (1)

[Claims] (1) The structure of the coast clutch and reverse clutch of an automatic transmission equipped with a starting device and a planetary gear device includes a drum that rotates together with the input shaft of the automatic transmission, and a drive wheel installed inside the drum. It is equipped with a coast clutch that transmits the torque from the engine to the torque converter side, and a reverse clutch that is placed in series behind the coast clutch and operates when traveling in reverse. A coasting clutch is formed at the front of the inside of the reverse clutch drum, and a reverse clutch that transmits torque between the coasting clutch drum and the reverse clutch drum is housed at the inside rear of the reverse clutch drum. The structure of automatic transmission coast clutch and reverse clutch is characterized by: