JPH02125164A - Structure for forward stage control clutch of automatic transmission and hydraulic circuit - Google Patents

Abstract

PURPOSE:To simplify the operating mechanism and reduce the number of parts by independently controlling the first and second pistons operating forward and direct clutches with the operating oil from an oil path formed on an inner cylinder. CONSTITUTION:A drum 40 with a hydraulic chamber is fitted to the outer periphery of an inner cylinder 401 directly coupled with the input shaft 28 of a transmission, a forward clutch 41 slidable in the axial direction and integrally rotated with the drum 40 is provided inside, and it is operated by the first piston 42. A direct clutch 52 and the second piston 56 operating it are provided in the first piston 42. The first and second pistons 42 and 56 are independently controlled by the operating oil fed via an oil path formed on the inner cylinder 401, the hub of the clutch 41 transmits the power to a large sun gear shaft 48, and the hub of the clutch 52 transmits the power to an intermediate shaft 55. A drain oil path 318 is provided at the middle of oil paths of both pistons 42 and 56. The operating mechanism is simplified, the number of parts is reduced, and the axial length can be shortened.

Description

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

[Prior art]

In an automatic transmission with only a starting device and a planetary gear device,
A clutch having a double piston structure for controlling the forward gear is disclosed, for example, in Japanese Patent Application Publication No. 95236 of 1985. By making the pistons double-structured, the axial length can be shortened, but on the other hand, the oil passages that send hydraulic oil to each piston are provided close to each other, which tends to cause hydraulic oil leaks, and the clutch It can also cause dragging. In addition, since the inner piston can only be operated when the outer piston of the double piston is operating, the combination of clutches to be installed is restricted, and the outer diameter of the clutch operated by the inner piston is limited. Another constraint is that the outer piston is smaller than the outer diameter of the clutch in which it operates.

[Problem to be solved by the invention]

Therefore, in the present invention, a large-capacity forward clutch that is always engaged and transmits a large amount of power during forward movement is arranged so that it is operated by an outer piston, and a direct clutch that requires relatively little power transmission is arranged to be operated by an inner piston. By operating the clutch, the eight clutches are distributed rationally, and r
The operation Ml that occurs between the oil passages arranged in contact with lJJ! The purpose of the present invention is to provide a structure and a hydraulic circuit for a forward gear control clutch that prevents leakage.

[0! Means for Solving the Problem] The clutch of the present invention includes an inner cylinder (401) directly connected to an input shaft (28) of a transmission, and an inner cylinder (40
A drum (40) having a hydraulic chamber inside is attached to the outer periphery of the drum (40), and a first clutch (40) installed inside the drum.
1), and a first forward clutch that is slidably fitted inside the drum in the axial direction and rotates together with the drum.
a first piston (42) that operates a clutch (41);
and a second clutch (52) that is a direct clutch installed inside the first piston (42) and a second piston (56) that operates the second clutch, Piston (42, 56) k Inner cylinder (401)! The hub of the first clutch is connected to the large sun gear shaft (48), and the hub of the second clutch is connected to the intermediate shaft (48). (55).

Further, a drain oil passage is provided between the oil passage of the first piston and the oil passage of the second piston.

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.

FIG. 2 shows a skeleton of an automatic transmission, and the automatic transmission 1 includes a torque converter 2 and a transmission 3 as a starting device. The transmission 1a3 consists of a main transmission 4 and a sub-transmission 1o that are arranged concentrically, the main transmission 4 achieving four forward speeds and one reverse speed, and the sub-transmission 10 being directly connected with a reduction ratio of 1. To achieve a two-speed shift with 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 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 moves a large sun gear shaft 48 and a large sun gear 49 integrated with the large sun gear +1I148. 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 at the fourth or fifth speed, 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. The hub 74 of the third clutch 73 is connected to the fifth clutch driver 460 . 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 unit 80 is a so-called Ravignon-type planetary gear unit that has two sun gears with different numbers of teeth and shares a carrier and a ring gear, but in the present invention, a Ravignon-N 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 and the small sun gear 78 engage a long pinion 82 and a 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. 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 1a4 as well as an input member of the auxiliary transmission 10.

That is, a ring gear 101 is provided inside the other end of the drum 95.
is integrally formed into this ring gear 101! l11
The shaft 10 meshes with the pinion 102 supported by the shaft 1105.
5 is supported by the carrier 103, and the carrier 10
3 is integrated into the output shaft 120. It! The other end of l 105 is coupled to a clutch hub of fourth clutch 104, and clutch drum 110 of fourth clutch 104 also serves as a brake drum of second brake 112.

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 1.09 of a third one-way clutch 113, and fixes an outer race 115 of the directional clutch 113 to the case 30. drum 11
0 is physically connected to axis 108 +CI-.

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 2o, and includes a drum-shaped converter case 21 connected to the engine crankshaft 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 2
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 stator 23 is connected to the fixed part 30 via the 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 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 WJ 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 has a flange portion 281 that expands in the radial direction, and thrust bearings of the same diameter are interposed on both sides of the flange portion 281.

The outer circumference 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 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 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
The inner diameter portion of No. 3 forms an outer race 46 of the first one-way clutch 45, and an inner race 47 of the - direction 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 shaft 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. The clutch plate 1- is spline engaged with the inner peripheral surface of the piston 42, and the clutch disc is spline engaged with a clutch hub 53 disposed inside.

A piston 56 with a diameter of tJz transmits power between a hub 53 and a large-diameter piston 42 that rotates together with the drum 4o.

A return spring 54 is stretched between the large diameter piston 42 and the small diameter piston 56 and the inner cylinder 401.
1, it is always biased in the non-operating direction.

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 drum 6 on the opposite side of the fifth clutch 65 of the clutch drum Go.
0, and the clutch hub 74 supports a clutch disk that also supports the third clutch 73 via splines. The clutch plate of the third clutch 73 is supported by a drum 75 that 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.
The piston 76 that operates the piston 76 is slidably supported. 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 coupled to the front end of the small sun gear shaft 77, so that the drum 75 rotates integrally 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.

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 9o 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 splined to 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-way 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 the long pinion 82 and the pinion shaft 83 supports the 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.

Ring gear 101 is subliquid i! ! As mentioned above, the sub-transmission is a speed reducer having a set of planetary gear trains, and is of the type that takes the input of the ring gear from the carrier and outputs it. ring gear 10
1 meshes with the sun gear 106,
The binion 102 is supported by a shaft 105. The shaft 105 has a carrier 103 whose front end is formed at the front end of the output shaft 120.
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 3o.

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.

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 by a radial bearing 551, and the rear end of the intermediate shaft 55 is supported by the front end of the output shaft 120 by a radial bearing 554. 815 The force shaft 120 is a radial bearing 120 disposed between the rear shaft support member 125 and the rear case 301.
a.

120e.

The intermediate shaft 55 supports the large sun gear shaft 48 with radial bearings 552 and 553, and the large sun gear shaft 48 supports the 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.
a', 531 a, 431 a, 43 l
b.

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 driver 1% 40 integrated with the input shaft 28 is equipped with a pair of O-rings 42p between it and the sliding surface of the cylinder, and a pair of oil channels are installed on both sides of the oil path to the piston 42. Attach the seal ring 316a. A check ball 40g is attached to the wall of the drum 40 facing the piston 42. 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 in the two clutch drums supported by the central support member 35, and a small-diameter ring member 36 and a hub 771 are attached to the piston 66 disposed on the front side. Since hydraulic pressure is supplied through the oil passage, oil seal rings 36a and 771a are provided on both sides of the oil passage. The piston 66 has a pair of O rings 66p 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 66p and a check ball 66a. A piston 94 disposed on the back side of the central support member 35, which has a ring 76p and a check ball 76a, also has a pair of O-rings 9.
Has 4p.

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 facing the outer periphery of the clutch drum 40 that is integrated with the input shaft 28.

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 the gears on the vertical side and the frictional engagement elements on the horizontal shelves. The ○ mark indicates that the frictional engagement elements are operating. , (0) indicates that it operates during engine braking,
Reference numerals 41, 52, 73°104.65 indicate the first to fifth clutches, and reference numerals 71, 112, .
93 indicates the first brake to the third brake, respectively;
Reference numerals 45, 90, and 113 indicate the 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, where input #12
The power of 8 is transmitted from the first clutch 41 to the first one-way 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-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 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 connected state, and the input from the drum 95 is transmitted as is to the output @120.

FIG. 5 shows the power transmission path at the third speed, in which the first brake 71 operates to fix the /h 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. At this time, the reduction ratio is small sun gear 7.
8. Determined by 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.
8, and since the planetary gear train does not move relative to each other, the intermediate shaft 55. The large sun gear @48 is 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 to fix the short pinion shaft 83 that is tightly meshed 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 the 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 "i1m" 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 shown in FIG. 1 is shown.

The outer circumference of a flange portion 281 formed at the rear end of the input shaft 28 of the automatic transmission is coupled to the inner circumference of the rear end of the inner cylinder 401 . The front end of the drum 4o is attached to the outer periphery of the tip of the inner cylinder 401, and a first clutch 41 and a second clutch 52 are installed inside the drum 40.

The drum 40 has an outer cylindrical part 40c whose rear end is open and a part of its inner periphery becomes a 7-outer cylinder, and an inner cylinder 401.
and an annular wall surface 40e connecting between the wall surface 40 and
Install a check valve 40g at e. A piston 42 having a similar shape to the drum 40 is inserted into the inner peripheral part of the outer cylinder part 40c. At the front end of the inner circumferential surface of the drum 40, a sliding portion 42h formed on the outer periphery of the annular front end surface 42f of the piston 42 slides the cylinder wall 40i on which the piston 42 slides in a fluid-tight manner by the sliding length of the piston 42. The annular wall surface 40e is formed as follows.
A hydraulic chamber is formed between the front end surface 42f of the piston 42 and a spline 40dt is formed on the inner wall surface of the cylindrical wall 40i extending to the rear side of the cylinder wall 4oh. : is provided and engaged with a spline parallel to the axial direction formed on the cylindrical peripheral portion rearward of the sliding portion 42g formed on the front end of the outer peripheral portion of the piston 42. The spline 40d is further fitted with the clutch plate 40a of the first clutch 41, and its movement is restricted by a stopper 40b. The parts fit together.

Between the clutch plates 40a is a clutch disc 43 spline-fitted to the clutch hub 43 in parallel with the axial direction.
a is inserted to constitute the first clutch 41. The clutch hub 43 has an annular wall 431 extending from the front end to the center, and both sides of the inner peripheral edge of the wall 431 are supported by thrust bearings 431a and 431b having the same diameter. The inner peripheral edge of the wall 431 is not supported in the radial direction, and the concentricity of the clutch hub 43 with respect to the input shaft 28 is ensured by the first one-way clutch 45 in which the clutch hub 43 is configured as an outer race. That is, the clutch hub 43
The inner periphery of the 7 outer race 4 of the first one-way clutch 45
6, and the inner race 47 of the one-way clutch 45 is integrally formed with the large sun gear shaft as described in FIG. Since the large sun gear shaft is supported on the intermediate shaft 55, the concentricity of the first one-way clutch 45 including the inner race 47 and the outer race 46 and the large sun gear shaft is ensured.

The piston 42 that operates the clutch 41 has an outer cylinder and an inner cylinder 401 formed on the inner circumference of the drum 40.
Hydraulic oil for operating the piston 42 is supplied to an oil hole 401a formed in an oil passage member 315 provided between the inner circumference of the inner cylinder 401 and the hollow boss portion 312 of the oil pump cover 31. Supply and discharge via.

A clutch plate 42a is fitted onto the inner periphery of the cylindrical peripheral portion of the piston 42 via a spline 42d parallel to the axial direction, and a spline is fitted parallel to the axial direction to the clutch hub S3 facing between the clutch plates 42a. The second clutch 52 is constructed by inserting the clutch plate 53a. The clutch hub 53 has an annular wall 531 extending from the rear end to the center, and the inner diameter portion of the wall 431 is fixed to the intermediate @55 via serrations parallel to the axial direction. The rear surface of the wall 531 is the hub 4 of the first clutch 41
Thrust bearing 4 inserted between wall 431 of 3
31a, and the wall 531 and the flange portion 2 of the input shaft 28
A similar thrust bearing 531a is also inserted between it and 81.

At the front end of the inner peripheral surface of the cylindrical wall 42i that connects to the annular front end surface 42f of the piston 42 that operates the first clutch 41, a sliding part formed on the outer periphery of the piston 56 that operates the clutch 52 is fluid-tight. The sliding cylinder wall 42h is formed to correspond to the sliding length of the binton 56, and the piston 5
6 is slidably fitted into cylinder N42h. The piston 56 has a check valve 56a, and hydraulic oil for operating the piston 56 is supplied and discharged through an oil passage 401b formed in the oil passage member 315 provided on the inner circumference of the inner cylinder 401. A spring 541 is interposed between the piston 56 and the inner cylinder 401 to always urge the piston 56 and the piston 42 in the non-operating direction.

The oil passage member 315 is fixed to the outer periphery of a boss portion 312 that constitutes a part of the oil pump cover 31 that is attached to the front surface of the transmission case. The support cylinder 34 is press-fitted into the inner peripheral part of the boss part 312 of the oil pump cover 31, and the support cylinder 34
An oil passage 341 is provided in the portion that contacts the inner circumferential surface of the boss portion 312 of No. 4.
form.

The inner peripheral part of the support cylinder 34 supports the rear end part of the input shaft 28 in the radial direction by a bearing 283, and a flange part 281 is provided between the flange part 281 of the input shaft 28 and the support cylinder 34.
A thrust bearing 281a similar to the thrust bearing 531a placed on the rear surface is placed to receive the thrust load of the input shaft 28. Thus, the rear end surface of the support cylinder 34, the flange portion 281 of the input shaft 28, the annular wall 531 of the clutch hub 53, the annular wall 431 of the clutch hub 43, and the radially inner end of the inner race 47 of the one-way clutch 45 are all Thrust bearings 281a, 531a are arranged perpendicularly to the axial direction, and between them.

431a and 431b are interposed at the same radial position in the radial direction and are relatively rotatable.

The oil passage member 315 has an oil passage 3 that communicates with an oil passage 314 formed on the outer periphery of the boss portion 312 of the oil pump cover 31.
16 and an oil passage 317 are provided. The oil passage member 315 is fixed to the oil pump cover 31, but the inner cylinder 40
1 rotates together with the input shaft 28, the parts of the oil passages 316 and 317 facing the inner cylinder 401 are formed into ring grooves, and oil seal rings 3168 are provided on both sides of the ring grooves.
．． 317a and seal the oil. Oil passage member 3
The oil passages 401a and 401 formed in the inner cylinder 401 facing the 15 ring groove-shaped oil passages 316 and 317.
b are communicated with oil passages 316 and 317, respectively. The oil passages 316 and 317 of the oil passage member 315 communicate with the hydraulic control device through an oil passage 314 provided in the boss portion 312, an oil passage 341 provided in the support cylinder 34, etc., and receive a supply of hydraulic oil.

This automatic transmission is configured so that the first clutch 41 is always operated during forward movement. Therefore, the first clutch 41
The clutch plate 40a and the clutch disk 43a also need to have a large diameter and a large capacity because it is necessary to transmit a large torque when in first or second gear.

For this reason, the drum 40 and piston 42 that actuate the clutch 41 are arranged at the outermost side in the radial direction, allowing them to have a large outer diameter.

On the other hand, the second clutch 52 is configured to operate in the 4th and 5th forward speeds, and in the 64th and 5th speeds, the transmitted torque is relatively small and the clutch capacity is small, so the clutch plate 42a and clutch disc 53a are The diameter can also be small. For this reason, the piston 56 that operates the clutch 52 is arranged radially inward of the drum 40 of the first clutch 41, and its diameter is reduced.

In the present invention, by utilizing the above-mentioned structural features, it is possible to employ a configuration in which a second clutch and a piston that operates the clutch are provided on the inner diameter portion of the piston that operates the first clutch.

By making the piston a double structure, the number of parts can be reduced and the clutch can be made more compact, and the axial length of the clutch can be shortened. Hydraulic oil is constantly supplied to the oil passage 316 of the oil passage member 315 to operate the piston 42 during forward movement.
Since the inner cylinder 401 rotates and slides with respect to the oil passage member 315, if the sealing in this part is insufficient, the oil passage 3
17, which causes the second clutch 52 to drag during 1st, 2nd, and 3rd gears. Therefore, oil seal rings 316a and 317a are inserted on both sides of the oil passages 316 and 317, and
．． 317, an oil passage 318 was established in the middle of the oil passage 318.
is connected to the drain side circuit to prevent problems caused by oil leaks.

〔Effect of the invention〕

As described above, the present invention provides a first clutch that is a forward clutch that is always activated during forward movement, and a second clutch that is activated in 4th and 5th speeds, among the clutches that control the forward gear of the planetary gear system of the transmission. It has five components that are combined in series with a clutch. Focusing on the fact that the second clutch requires only a small transmission torque, the piston that operates the first clutch installed in the clutch drum is made into a cylindrical shape with a bottom. It is equipped with a second clutch and a piston that operates this clutch.

With this configuration, the first and second clutches and their operating mechanisms can be simplified, and the number of parts can also be reduced.

By adopting the double piston structure, the axial length can also be shortened.

By adopting a double piston structure, it is necessary to place the hydraulic oil supply oil passages close to each other in order to control each piston independently, and it is possible to prevent oil leaks between the oil passages that are placed close to each other. more likely to occur. Therefore, in the present invention, a drain oil passage communicating with the return side of the hydraulic oil is provided between each oil passage constituting the hydraulic circuit, thereby completely preventing the bowing of the second clutch due to oil leakage. can do.

[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 view showing an outline of the automatic transmission. FIG. 3 is an explanatory diagram showing the power transmission line when the first gear is on. FIG. 4 is an explanatory diagram showing the power transmission line when the second gear is on. FIG. 5 is an explanatory diagram showing the power transmission line at the third speed. FIG. 6 is an explanatory diagram showing the power transmission line at 4th speed. FIG. 7 is an explanatory diagram showing the power transmission line at 5th speed. FIG. 8 is an explanatory diagram showing the power transmission system when moving in reverse, FIG. 9 is a diagram showing the gear ratio, and FIG. 10 is a sectional view of the main parts. 1... Automatic transmission, 2... Torque converter, 4...
...Main transmission, 1o...Sub-transmission, 28...Input shaft, 30...
...Transmission case, 35...Central support member, 40...Drum, 41...
・・・・・・First clutch, 42・・・・・・・・・
Piston, 48...Large sun gear shaft, 52...
...Second clutch. 55・・・・・・Intermediate shaft, 56・・・・・・
...Piston, 77...Small sun gear shaft, 120...Output shaft, 318...Drain oil path. 401・・・・・・Inner cylinder. Patent Applicant Aisin AW Co., Ltd. Agent Patent Attorney Masaaki Meiki (2 others) Figure Figure Output Figure 10

Claims (3)

[Claims] (1) In the structure of a clutch for speed change control of an automatic transmission equipped with a starting device and a planetary gear device, an inner cylinder is directly connected to the input shaft of the transmission, and a hydraulic chamber is installed inside the inner cylinder on the outer periphery. a first clutch installed inside the drum; and a first clutch that operates the first clutch, which is a forward clutch that is fitted inside the drum so as to be slidable in the axial direction and rotates integrally with the drum. A piston, a second clutch that is a direct clutch installed inside the first piston, and a second piston that operates the second clutch, the first and second pistons being formed into an inner cylinder. A structure of a forward gear control clutch for an automatic transmission, characterized in that it is independently controlled by hydraulic oil supplied through an oil path. (2) In the clutch structure according to claim (1), the hub of the first clutch, which is a forward clutch, is connected to the front end of a large sun gear shaft disposed on the outer periphery of the intermediate shaft via a one-way clutch. The structure of a forward gear control clutch for an automatic transmission is characterized in that the hub of the second clutch, which is a direct clutch, is connected to the front end of an intermediate shaft. (3) In the hydraulic circuit of the clutch for speed change control of an automatic transmission equipped with a starting device and a planetary gear device, there is an inner cylinder directly connected to the input shaft of the transmission, and a hydraulic chamber inside the inner cylinder attached to the outer circumference of the inner cylinder. a first clutch installed inside the drum; a first piston that operates the first clutch that is slidably fitted inside the drum and rotates integrally with the drum; a second clutch installed inside the first piston; a second piston that operates the second clutch; and an oil passage communicating with hydraulic chambers of the first piston and the second piston formed in the inner cylinder. , an oil passage member disposed on the inner periphery of the inner cylinder, and a drain communicating with the hydraulic circuit on the return side of the hydraulic oil in an intermediate part of the oil passage formed in the oil passage member and communicating with the oil passage of the inner cylinder. A hydraulic circuit for a forward gear control clutch of an automatic transmission, characterized by having an oil passage for the forward gear control clutch of an automatic transmission.