JPH02125137A - Automatic transmission - Google Patents

Abstract

PURPOSE:To facilitate the design change of the change gear ratio by concentratively arranging four clutches for the speed change, two brakes and two one-way clutches in front of a transmission case and providing a planetary gear device at the rear. CONSTITUTION:An intermediate shaft 55 is rotatably supported on an input shaft 28 and an output shaft 100 supported at the front and the rear of a transmission case 30, clutches 41, 52, 65, 73, the first brake 71, and the first one-way clutch 45 are concentratively arranged at the front of a center support member 35, and the second brake 93, the second one-way clutch 90 are arranged at the rear to attain the speed change of four forward speeds and one reverse speed. The brake 93 is a multi-plate type friction brake, its operating piston 94 is inserted into a cylinder on the rear side of the flange section of the center support member 35, and the ring gear 96 of a planetary gear device is connected to the output shaft 100. A friction coupling element such as a brake is not arranged at all on the outer periphery of the planetary gear device 80, the unit replacement of the planetary gear device is facilitated, and the design change of the change gear ratio is facilitated.

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]

In an automatic transmission equipped with a starting device and a planetary gear system,
A support member is provided inside the transmission case, frictional engagement elements including four clutches are disposed in the front part of the support member, and the frictional engagement element including one brake and the planetary gear device are connected to the support member. For example, the automatic transmission installed at the rear of the
ies 880480.

In the above-mentioned document, the brake provided at the rear of the support member is a handbrake, and the drum of the handbrake is disposed on the outer periphery of the ring gear of the planetary gear unit. This poses a problem when adopting a gear set having a large size, and since the width of the drum is large, it also becomes long in the axial direction.

[Problem to be solved by the invention]

The present invention reduces the axial dimension by making the brake disposed at the rear of the central support member a multi-plate brake and by disposing the piston for operating the brake within the central support member. The purpose of the present invention is to provide an automatic transmission with a large degree of freedom in outer diameter dimensions.

[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 (100) 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 (100).
5), a central support member (35) provided inside the transmission, and a friction engagement element including four clutches (41, 52, 65, 73) provided at the front of the central support member (35). and,
One brake (93) located at the rear of the central support member
The brake (93) disposed at the rear of the central support member (35) is a multi-plate friction brake, and a piston (94) for operating the brake (93) is provided. It is arranged in a cylinder on the rear side of the flange portion of the central support member (35), and has a configuration in which a ring gear (96) of a planetary gear device is connected to an output shaft (100).

Note that the above-mentioned symbols in parentheses are used to contrast with the drawings, but do not limit the structure 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 achieves four forward speeds and one reverse speed, and uses four clutches, two brakes, and two 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 transmission 3, 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 the power is passed through the clutch hub 43 to the clutch hub 43 of the first one-way clutch 45 and the outer race 46 that is integrated with the clutch hub 43.
The inner race 47 of the first one-way clutch 45 drives the large sun gear shaft 48 and the large sun gear 49 that is integrated with the large sun gear shaft 48 . First one-way clutch 45
operates between 1st and 4th gears.

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 third and fourth 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 connected to the fourth clutch 65
drum 60. The fourth 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 fourth 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 activated in the second and fourth speeds.

Planetary gear system! ! ! Reference numeral 80 is a so-called Ravigneau-type planetary gear device which has two sun gears with different numbers of teeth and shares a carrier and a ring gear, but in the present invention, a Ravigneaux-type gear train with a ring gear as an output is adopted.

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 second 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 second brake 93 operates during reverse travel and during engine braking in first gear.

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 at first speed.

The short pinion 84 meshes with a ring gear 96 formed inside one end of a drum 95, and this drum 95 is connected to an output shaft 100.

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 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 2
1 connects and drives an engine crankshaft and a pump impeller 22, and the hydraulic oil pressurized by the pump impeller 22 drives a turbine runner 27 and stator 2.
3 to the pump impeller 22. 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 a shaft 28 which is a shaft and also serves as an input shaft of the transmission. An oil pump cover 31 and a partition plate 3 are installed at the joint between the case 20 of the torque converter 2 and the case 30 that houses the transmission 3.
2 and the oil pump housing 33 are arranged.

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 portion 312 that protrudes from the center of the transmission case into the inside of the case, and a hollow tubular support WJ 34 is press-fitted into the hollow boss portion 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 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 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 fourth clutch by a spline.
The clutch drum 60 of the clutch is coupled to the clutch drum 60 of the clutch. A fourth 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 fourth clutch 65 of the clutch drum 60.
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 3o. This central support member 35 has a flange portion that engages with the inner peripheral portion of the case, a stepped boss formed in the inner diameter direction of the flange portion that protrudes to the front side, and a short boss that protrudes to the rear side, and protrudes to the front side. A small-diameter ring member 36 and a large-diameter ring member 37 are respectively fitted to the outer periphery of the stepped portion of the boss.

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

Since the intermediate shaft 55 supports the large sun gear shaft 48 and the large sun gear shaft 4β 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 second 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 second brake 93, and a brake disc is spline-engaged with the outer periphery of the outer race 91. The brake plate of the second 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 9o.
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 drum 95 is integrated with the output shaft 100 via a wall 951 extending in the axial direction.

A parking brake groove 955 is formed on the outer periphery of the ring gear 96 of the drum 95, and together with the pawl 120 disposed on the outer periphery, a parking brake is constructed in a known manner.

A rear case 130 that supports the output shaft 100 is attached to the rear end of the case 30, and the output shaft is supported by a bearing arranged on the inner peripheral side of the rear end of the catcher case 130 on the inner peripheral side of the rear wall 301 of the case 30. The outer diameter portion of the rear end of the intermediate shaft 55 is supported by a bearing at the inner diameter portion of the front end.

A speedometer drive gear 10 is attached to the output shaft 100.
5 will be provided.

A flange 106 is integrally provided on the drive gear 105,
The rotational speed of the output shaft 100 is obtained by detecting passage through the slit of the flange with the sensor 108.

At the rear end of the output shaft 100 is a connecting member 115 to the axle shaft.
is inserted and fixed to the output shaft 100 with the nut 116. A hydraulic control device (not shown) is provided at the bottom of the transmission case 30, and a clutch of the transmission.

Controls brake operation. 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 performs automatic gear shifting of four forward gears and one reverse gear. Table 1 shows each gear gear and the operation of the frictional engagement elements that achieve the gear shifting.

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

Reference numerals 41, 52, 73, 65 indicate the first to fourth clutches, 71, 93 respectively indicate the first brake and the second brake, 45, 90, . represent a first one-way clutch and a second one-way clutch, respectively.

Figures 3 to 7 show the power transmission paths at each gear stage, and the thick line 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 9o, the rotation of the large sun gear 49 is decelerated and transmitted to the ring gear 96. This rotation is output to the output shaft 100 via the drum 95.

FIG. 4 shows the power transmission path at second 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 96 to drive the output shaft 100. The reduction ratio at this time is small sun gear 78. It is determined by the number of teeth of the large sun gear 49 and ring gear 96.

FIG. 5 shows the power transmission path at the third 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 @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. That is, the input shaft 28 and the output shaft 100 are directly connected.

55, large sun gear shaft 48, and since the planetary gear train does not move relative to each other, intermediate shaft 55, large sun gear shaft 48
is directly connected to the drum 95. That is, the input shaft 28 and the output shaft 1
00 is directly connected.

FIG. 6 shows the power transmission path at the fourth 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.

The fourth speed is an overdrive in which the rotational speed of the input shaft 28 is increased and transmitted to the output shaft 100.

FIG. 7 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 as it decelerates, and is transmitted to the ring gear 96 and drum 95 to drive the output shaft 100.

〔Effect of the invention〕

As described above, the present invention provides an automatic transmission equipped with a planetary gear device in which the output side is a ring gear that achieves four forward speeds and one reverse speed. The clutch, two brakes, and two one-way clutches were all placed together at the front of the transmission case, and the planetary gear system was installed at the rear. Therefore, no frictional engagement elements such as brakes are provided on the outer periphery of the planetary gear device.

With this configuration, it is easy to replace the unit of the planetary gear device with another unit, and the design can be easily changed to a transmission with a different gear ratio.

Four clutches are arranged in series, two clutches are supported by a support member attached to the front of the transmission case, and the remaining two clutches are supported by a central support member attached to the inside center of the case. Therefore, the hydraulic oil supply lines for each clutch can be arranged rationally. As a result, the responsiveness of the operation is improved and leakage of hydraulic oil can be prevented.

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. Furthermore, 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.

[Brief explanation of the drawing]

FIG. 1 is a cross-sectional view of an automatic transmission according to the present invention, FIG. 2 is an explanatory diagram showing an outline of the automatic transmission, and FIG. 3 is an explanatory diagram showing a power transmission line at 1st speed. Figure 4 is an explanatory diagram showing the power transmission line at 2nd speed, Figure 5 is an explanatory diagram showing the power transmission line at 3rd gear, and Figure 6 is an explanatory diagram showing the power transmission line at 4th gear. FIG. 7 is an explanatory diagram showing the power transmission system during reverse movement. 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 axis. 93...Second brake, 94...
...Piston, 77...Small sun gear shaft. 95...Drum, 96...Ring gear, 100...Output shaft.

Claims (1)

[Claims] (1) In an automatic transmission equipped with a starting device and a planetary gear system, an input shaft supported at the front of the transmission case, an output shaft supported at the rear of the transmission case, and an input shaft and an output shaft are supported at the front of the transmission case. An intermediate shaft whose front and rear ends are rotatably supported by a shaft, a central support member provided inside the transmission, a friction engagement element including four clutches provided in the front part of the central support member, and a central support. A friction engagement element including one brake disposed at the rear of the member and a planetary gear device are provided, the brake disposed at the rear of the central support member is a multi-plate friction brake, and the piston for operating the brake is located at the center. An automatic transmission characterized in that the automatic transmission is disposed in a cylinder on the rear side of a flange portion of a support member, and a ring gear of a planetary gear device is connected to an output shaft.