JPH02125138A - Automatic transmission - Google Patents

Abstract

PURPOSE:To constitute an automatic transmission for five forward speeds and one reverse speed by connecting and combining a main transmission for four forward speeds and one reverse speed consisting of a planetary gear device and an auxiliary transmission directly coupled or attaining reduction in series. CONSTITUTION:An intermediate shaft 55 is rotatably supported on an input shaft 28 supported at the front of the case 30 of a transmission 1 and an output shaft 120 supported at the rear. A main transmission 4 is constituted with a planetary gear device supported on the intermediate shaft 55 and using a ring gear 96 attaining four forward speeds and one reverse speed with clutches 41, 52, 73, 65 and a brake 71 as an output member. An auxiliary transmission 10 consisting of a reduction planetary gear device supported at the rear of the case 30 and using a ring gear 101 directly coupled or attaining reduction with a clutch 104 and a brake 112 as an input member is combined with the main transmission 4 in series by connecting the ring gears 96 and 101. An automatic transmission for five forward speeds and one reverse speed can be easily constituted.

Description

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

[Prior art]

An automatic transmission in which a main transmission equipped with a starting device and a planetary gear set and an auxiliary transmission equipped with a planetary gear set for deceleration are connected in series is disclosed, for example, in Patent Application Publication No. 502274 of 1988. There is.

In Figure 1 of the above publication, a main transmission with four forward speeds and an auxiliary transmission, which is a reduction gear, are connected, and the auxiliary transmission is directly connected or decelerated only at any of the gears of the main transmission. A skeleton of an automatic transmission is shown that switches between gears to achieve five forward gears.

In this transmission, the output member of the main transmission is a ring gear, and the input member of the auxiliary transmission is also a ring gear.
Since a one-sided clutch is interposed between both ring gears,
Both ring gears are connected via a shaft member. Therefore, the shaft located at the center of the transmission is divided into four shafts.

[Problem to be solved by the invention]

When a multi-stage automatic transmission is configured by connecting a main transmission and a sub-transmission in series, the division of the shafts and the support structure of these shafts are important.

The present invention has three shafts, an input shaft, an intermediate shaft, and an output shaft, arranged at the center of the automatic transmission, and the input shaft and the output shaft are reliably supported by the transmission case, and the intermediate It is an object of the present invention to provide an automatic transmission in which the shaft is supported by an input shaft and an output shaft, thereby reducing the length in the axial direction and rationally disposing a main transmission and a sub-transmission.

[Means to solve the problem]

The present invention includes an input shaft (28) supported at the front of a transmission case (30), an output shaft (120) supported at the rear of the transmission case (30), and an input shaft (28). and an intermediate shaft (5) whose front and rear ends are rotatably supported by the output shaft (120).
5) and is supported by the intermediate shaft (55) to provide 4 forward speeds and 1 reverse speed.
A planetary gear device whose output member is a ring gear (96) that achieves a speed change, and a deceleration planetary gear whose input member is a ring gear (101) that is supported at the rear of the transmission case and that achieves direct connection or deceleration. device, a ring gear (96) of a planetary gear device, and a ring gear (1) of a planetary gear device for reduction.
01,), and has a configuration that connects the carrier (103, 1, 05) of the planetary gear device for reduction and the output shaft (120).

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 3 consists of a main transmission 4 and a sub-transmission 10 that are arranged concentrically.The main transmission 4 achieves four forward speeds and one reverse speed, and the sub-transmission 10 is a direct-coupled transmission with a reduction ratio of 1. 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 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 4o 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 4o 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 the brake drum of the first brake 71, and the first brake 71 is operated 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 9o is integrally fixed to the support 35 fixed to the case 3o. 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, and fixes an outer race 115 of the directional clutch 113 to the case 30. drum 11
0 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 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 increase 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.
and a face plate portion 311 that covers the front opening of the transmission case.

It has a hollow boss part 312 that protrudes from the center of the transmission case into the inside of the case, and a hollow tubular support cylinder 34 is press-fitted into the hollow boss part 312.

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.

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 4o 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 S5 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 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 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 6o, and includes a clutch plate that is spline-engaged to the inside of the clutch drum 60 and a clutch disc that is spline-engaged to 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 6°1.

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. 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 circumferential side of the drum 75, and a piston 76 that operates the clutch 73 is slidably supported on the outer circumferential side of the inner cylinder 751. 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 cylindrical member 771 is coupled 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 toward the front side, and a short boss that protrudes toward the rear 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 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 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
will immediately move 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.
A hydraulic control device (not shown) is provided at the bottom of the case 30 of the nine-speed transmission, which is inserted and fixed to the output shaft 120 with a nut 136, and controls 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, a description will be given of the arrangement of bearings used for supporting parts of the automatic transmission (the automatic transmission), the arrangement of seals provided in the hydraulic circuit, etc.

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. The output shaft 120 has a radial bearing 120a disposed between the rear shaft support member 125 and the rear case 301.

120e.

Intermediate shaft S5 supports large sun gear shaft 48 with radial bearings 552, 553, and large sun gear shaft 48 supports small sun gear shaft 77 with radial bearings 481, 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.
, 531at 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 O rings 42P are installed on both sides of the oil passage to the screw 1-ring 42. Attach the oil 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 76p and a check ball 76a. A piston 94 disposed on the back surface of the central support member 35 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 1168.

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 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. ) indicates operation during engine braking. Table 1 shows the gears in the vertical section and the frictional engagement element in the horizontal shelf. The O mark indicates that the frictional engagement element is operating, and (0) indicates that the frictional engagement element is operating. 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, and shows the input shaft 28.
The power is transmitted from the first clutch 41 to the first one-way clutch 45, which activates the large sun gear shaft 48° and the large sun gear 49. Since the shaft 81 of the long binion 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 sub-transmission is operated to maintain the sub-transmission in a directly connected state, and the human power from the drum 95 is directly transmitted to the output shaft 120.

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
, large sun gear 49° is determined by the number of teeth of 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, 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.

〔Effect of the invention〕

As described above, the present invention provides a main transmission equipped with a planetary gear device in which the ring gear serves as an output member to achieve four forward speeds and one reverse speed, and a planetary gear device in which the ring gear serves as an input member to achieve direct coupling or deceleration. By connecting and combining sub-transmissions in series, an automatic transmission with five forward speeds and one reverse speed is constructed.

The sub-transmission! It is placed immediately after the main transmission and is only connected to the main transmission by a member that connects the ring gears of both.
The auxiliary transmission can be easily replaced, and in combination with auxiliary transmissions having different speed ratios, an automatic transmission having a gear train with different speed ratios can be easily configured.

In addition, the shaft members arranged on the axis of the automatic transmission are composed of three shaft members: an input shaft, an intermediate shaft, and an output shaft, and the input shaft and output shaft are located at the front and rear of the transmission case. Each shaft is rotatably mounted with two-point support, and the intermediate shaft is supported by the input shaft and output shaft.

With this configuration, the structure of each shaft member itself can be simplified, and the support structure of each shaft member can also be simplified. Therefore, the shaft length of the automatic transmission can also be shortened.

Since the planetary gear device, the large sun gear shaft, and the small sun gear shaft are all supported by the intermediate shaft, the structure of the main transmission can be simplified. The planetary gear device of the auxiliary transmission is supported by the outer periphery of the shaft support member attached to the rear part of the transmission case.
The force applied to the sub-transmission can be reliably received by the transmission case.

[Brief explanation of drawings]

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, Fig. 2 is an explanatory diagram showing the outline of the automatic transmission, and Fig. 3 is a 1-speed FIG. 4 is an explanatory diagram showing the power transmission path at 2nd speed, FIG. 5 is an explanatory diagram showing the power transmission path at 3rd speed,
Fig. 6 is an explanatory diagram showing the power transmission line in 4th gear, Fig. 7 is an explanatory diagram showing the power transmission line in 5th gear, and Fig. 8 is an explanatory diagram showing the power transmission line in reverse. The explanatory diagram, FIG. 9, is a diagram showing the gear ratio. 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, 95.・・・・・・
...Drum, 96 ...Ring gear. 101...Ring gear, 103...
...Carrier, 120...Output shaft. Patent Applicant: Aisin AW Co., Ltd. Agent: Patent Attorney: 8 Akira Meiki (2 others)

Claims (1)

[Claims] (1) In an automatic transmission consisting of a main transmission equipped with a starting device and a planetary gear set, and an auxiliary transmission equipped with a planetary gear set for reduction, which are connected in series, an input shaft supported by the rear part of the transmission case, an intermediate shaft whose front and rear ends are rotatably supported by the input shaft and output shaft, and which is supported by the intermediate shaft and has four forward speeds and one reverse speed. A planetary gear device that uses a ring gear as an output member to achieve a speed change, a planetary gear device for reduction that uses a ring gear as an input member that is supported at the rear of a transmission case and achieves direct connection or deceleration, and a planetary gear device. 1. An automatic transmission comprising: a member connecting a ring gear of a planetary gear unit for reduction with a ring gear of a planetary gear unit for reduction; and a member for connecting a carrier of the planetary gear unit for reduction and an output shaft.