JPH05180281A - Vehicular automatic transmission of planetary gear system - Google Patents

Abstract

PURPOSE:To shorten a shaft directional dimension by providing a clutch drum which is projected in the shaft direction from the outer peripheral edge part of a bottom wall and has an outer peripheral wall of a bottomed cylindrical motive power transmitting member, superposing frictional plates of a clutch upon each other, and engaging them respectively with the inner peripheral surface of the drum and the outer peripheral surface of the motive power transmitting member. CONSTITUTION:There is provided a bottomed cylindrical clutch drum 170 which is projected in the shaft direction from the outer peripheral edge part of a bottom wall 184 and has an outer peripheral wall 186 situated on the outer peripheral side of a bottomed cylindrical motive power transmitting member 201. In a condition that frictional plates 196a and 196b of a high speed stage use clutch 100 are superposed upon each other, they are engaged respectively with the inner peripheral surface of the clutch drum 170 and the outer peripheral surface of the bottomed cylindrical motive power transmitting member 201. Thereby, the frictional plates 196a and 196b and a planetary gear device composed of a sun gear 90, a ring gear 92, a planetary gear 94 and so on are housed in the clutch drum 170, and are also arranged so as to be superposed upon the outer peripheral wall 186 in the diametrical direction, and a shaft directional dimension of the whole of a non continuous variable transmission 18 can be shortened, so that the transmission can be mounted easily on a vehicle.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a planetary gear type automatic transmission for a vehicle, and more particularly to a technique for reducing the axial dimension.

[0002]

2. Description of the Related Art "Toyota A240" issued in March 1986
The automatic transmission described in "L Automatic Transaxle Repair Manual" has a first rotating shaft and a second rotating shaft that rotate about an axis, and has inner teeth and is connected to the first rotating shaft. The ring gear and the planetary gear that meshes with the inner peripheral teeth of the ring gear by extending from the shaft end of the second rotating shaft to the outer peripheral side and wrapping around from the outer peripheral side of the ring gear to the first rotating shaft side. A rotatably supported carrier, a bottomed cylindrical power transmission member connecting the carrier and the second rotating shaft so as to cover the ring gear, and a carrier capable of being relatively opposed to the outer peripheral side of the first rotating shaft. A planetary gear device including a tubular member having a sun gear that is fitted and meshes with the planetary gear is provided, and a multi-plate clutch for connecting the sun gear and the second rotating shaft is provided.

[0003]

However, in the above-described automatic transmission including the planetary gear device and the multi-plate clutch, the clutch for connecting the tubular member and the second rotary shaft is usually the planetary gear device. Since it is arranged on one side in the direction of the rotation axis, there is a drawback that the axial dimension of the automatic transmission becomes long in a vehicle in which the allowable space is limited. Especially, when the automatic transmission is used as the auxiliary transmission of the belt type continuously variable transmission in the trunk axle housing, the disadvantage becomes remarkable.

The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a planetary gear type automatic transmission for a vehicle having a further reduced axial dimension.

[0005]

The gist of the present invention for achieving the above object is as follows: (a) a first rotating shaft and a second rotating shaft which rotate around a uniaxial center; An inner peripheral tooth of the ring gear having a ring gear connected to the first rotating shaft and extending from the shaft end portion of the second rotating shaft to the outer peripheral side and wrapping around from the outer peripheral side of the ring gear to the first rotating shaft side. A carrier that rotatably supports a planetary gear that meshes with the first rotation shaft side thereof, a bottomed cylindrical power transmission member that connects the carrier and the second rotation shaft so as to cover the ring gear, A planetary gear unit including a tubular member having a sun gear that is fitted relative to the outer peripheral side of the first rotating shaft and meshes with the planetary gear; and (b) a disc-shaped friction plate, With a multi-plate clutch that connects two rotating shafts In a vehicle planetary gear type automatic transmission including, (c) a bottom wall fixed to the tubular member, and an outer peripheral side of the bottomed cylindrical power transmission member protruding axially from the outer peripheral edge portion of the bottom wall. A bottomed cylindrical clutch drum having an outer peripheral wall located therein is provided. (D) The friction plates of the clutch are stacked on each other, and the inner peripheral surface of the clutch drum and the outer peripheral surface of the bottomed cylindrical power transmission member. It is characterized in that they are engaged with and respectively.

[0006]

With this structure, the bottom wall fixed to the tubular member and the outer peripheral wall projecting in the axial direction from the outer peripheral edge portion of the bottom wall and located on the outer peripheral side of the bottomed cylindrical power transmission member are formed. The bottomed cylindrical clutch drum is provided, and the friction plates of the clutch are engaged with the inner peripheral surface of the clutch drum and the outer peripheral surface of the bottomed cylindrical power transmission member, respectively, in a state of being overlapped with each other. Therefore, the planetary gear unit and the friction plate of the clutch are housed in the clutch drum and arranged so as to overlap the outer peripheral wall in the radial direction.

[0007]

Therefore, the axial dimension of the planetary gear unit and the clutch is greatly reduced, and the axial dimension of the automatic transmission as a whole is also shortened, so that the automatic transmission can be easily mounted on a vehicle having a limited allowable space. Become.

[0008]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described in detail below with reference to the drawings.

FIG. 1 is a skeleton diagram for explaining a driving force transmission system of an FF vehicle transverse transaxle equipped with a vehicle transmission according to an embodiment of the present invention, and FIGS. It is sectional drawing which shows a transaxle. Although the respective axes of the transaxle are arranged as shown in FIG. 5, the axes of FIGS. 2 to 4 are developed in one plane for easy understanding.

The engine 10 is powered by a fluid coupling 12 with a lockup clutch, a forward / reverse switching device 14,
Belt type continuously variable transmission (hereinafter referred to as CVT) 16, stepped transmission 18, reduction gear device 20, and differential gear device 2
It is adapted to be transmitted to the wheel 26 connected to the drive shaft 24 via the wheel 2. The fluid coupling 12 includes a pump impeller 30 connected to the crankshaft 28 of the engine 10, a turbine impeller 32 rotated by oil from the pump impeller 30, and a turbine impeller 32 thereof.
An output shaft 34 that is connected to the shaft so that it cannot rotate relative to the damper 36.
And a lockup clutch 38 provided on the output shaft 34 via the. A rotor 42 of a hydraulic pump 40 (see FIG. 2) is connected to the pump impeller 30 and an internal gear 4 eccentrically meshed with the rotor 42 is engaged.
When 4 is rotationally driven together with the rotor 42, hydraulic pressure for operating the hydraulic actuators of the respective parts is generated.

The forward / reverse switching device 14 is a double pinion type planetary gear device which is selectively switched between a forward gear stage and a reverse gear stage in accordance with an operating position of a shift lever (not shown), and the fluid cup with the CVT 16 interposed therebetween. It is arranged on the opposite side of the ring 12. The output shaft 34 of the fluid coupling 12 is inserted through the shaft center of the CVT 16 and protrudes to the opposite side, and the planetary gear device is concentric with the sun gear 50 provided on the output shaft 34 such that the sun gear 50 cannot rotate relative to the sun gear 50. The provided ring gear 52, a pair of planet gears 54 and 56 that mesh with one and the other of the sun gear 50 and the ring gear 52, and mesh with each other, and rotatably support the planet gears 54 and 56 and input the CVT 16. The carrier 60 is connected to the shaft 58 so as not to rotate relative to the shaft 58. A multi-plate type forward clutch 62 is provided between the sun gear 50 and the carrier 60, and a multi-plate type reverse brake 66 is provided between the ring gear 52 and the housing 64, each of which is a hydraulic cylinder 63. , 67 (see FIG. 2). When the forward clutch 62 is engaged by the hydraulic cylinder 63 in the state where the reverse brake 66 is released, the output shaft 34 and the carrier 60 are relatively non-rotatably connected, and the input shaft 58 rotates integrally with the output shaft 34. When the forward clutch 62 is released and the reverse brake 66 is engaged by the hydraulic cylinder 67, the ring gear 5
Since the rotation of 2 is blocked, the carrier 60 and the input shaft 5
8 the rotational speed / input shaft 5 of the output shaft 34 in the opposite direction, i.e. the speed ratio gamma _G1 a direction to reverse the vehicle (= the output shaft 34
Rotational speed of 8) = is rotated by 1- (number of teeth Z _S of the number of teeth Z _R / sun gear 50 of the ring gear 52). The input shaft 58 is formed with an insertion hole through which the output shaft 34 is inserted, and the input shaft 58 is arranged so as to be rotatable relative to the output shaft 34 about a common axis a.

The CVT 16 comprises an input shaft 58 and an output shaft 70 rotatably arranged around an axis b parallel to the axis a of the input shaft 58.
The output shaft 70 is provided with a drive side variable pulley 72 and a driven side variable pulley 74, respectively, and a transmission belt 76 is wound between the variable pulleys 72, 74. The variable pulleys 72 and 74 are fixed rotating bodies 78 and 8 fixed to the input shaft 58 and the output shaft 70, respectively.
0, and movable rotating bodies 82 and 84 provided on the input shaft 58 and the output shaft 70 so as to be movable in the axial direction and non-rotatable around the shafts, respectively. The V-groove width, that is, the transmission belt 76, is moved in the axial direction by the hydraulic cylinders 86 and 88 as the driving means provided.
By changing the hanging diameter (effective diameter) of CVT 16, the gear ratio γ of CVT 16 (= rotational speed of input shaft 58 / rotational speed of output shaft 70) is changed.

The stepped transmission 18 is a single-pinion type planetary gear type automatic transmission, and is arranged concentrically with the output shaft 70 on the rear side of the fixed rotating body 80 of the driven side variable pulley 74. .. This planetary gear device meshes with a sun gear 90 that is rotatably arranged concentrically with the output shaft 70, a ring gear 92 that is relatively non-rotatably connected to the output shaft 70, and the sun gear 90 and the ring gear 92. The planetary gear 94 and the carrier 98 that rotatably supports the planetary gear 94 and is connected to the second output shaft 96 so as not to rotate relative to each other. Between the sun gear 90 and the carrier 98, a multi-plate high speed clutch 10 is provided.
0 is provided, and a one-way clutch 102 and a multi-plate low speed stage brake 104 are provided in series between the sun gear 90 and the housing 64. The high speed gear clutch 100 and the low speed gear brake 104 are controlled to be engaged by hydraulic cylinders 106 and 108 (see FIG. 3), respectively.
02 is the ring gear 9 when the sun gear 90 is moving forward when the low speed gear brake 104 is engaged and controlled.
Prevents rotation in the opposite direction of 2 but
Rotation in the opposite direction is allowed. Therefore,
When the output shaft 70 is rotated in the direction to move the vehicle forward in a state in which the high speed gear clutch 100 is released and the low speed gear brake 104 is engagement-controlled by the hydraulic cylinder 108, the carrier 98 and the second output are rotated. The shaft 96 has its output shaft 7 driven by the action of the one-way clutch 102.
In the same direction as the rotation direction of 0, the gear ratio γ _G2 (= output shaft 70
Rotation speed / rotation speed of the second output shaft 96) = 1 + (the number of teeth Z _{S of the} sun gear 90 / the number of teeth Z _{R of the} ring gear 92), that is, a higher gear than the gear ratio when the Ravigneaux compound planetary gear device is used ( It can be rotated at a reduced speed with a small reduction ratio. Conversely, when the low speed gear brake 104 is released and the high speed gear clutch 100 is engagement-controlled by the hydraulic cylinder 106, the sun gear 90 and the carrier 98 are coupled to each other so that they cannot rotate relative to each other. Are integrally rotated, and the second output shaft 96 is rotated in the same direction as the output shaft 70 at the gear ratio γ _G2 = 1.
It should be noted that when the vehicle is moving forward, the shift stage can be switched by engaging the high speed clutch 100 while engaging the low speed brake 104.

The second output shaft 96 is provided with a first gear 110, and the second gear 1 provided on the intermediate shaft 112.
It is meshed with 14. The intermediate shaft 112 is rotatably arranged around an axis c parallel to the axis b of the second output shaft 96, and also has a large-diameter gear 11 of the differential gear device 22.
The third gear 118 meshed with the gear No. 6 is provided. Second
The gear 114 has a larger diameter than the first gear 110, and
18 has a smaller diameter than the large-diameter gear 116.
The reduction gear device 20 is constituted by the gear 110, the second gear 114, and the third gear 118.

The differential gear unit 22 is rotatably supported around an axis orthogonal to the rotation axis d of the drive shaft 24 and rotates in unison with the large diameter gear 116.
And a pair of large differential gears 122 that mesh with the small differential gear 120 and are connected to the drive shaft 24. Therefore, the power transmitted from the reduction gear device 20 is evenly distributed to the left and right drive shafts 24 in the differential gear device 22 and then transmitted to the left and right wheels 26.

The housing 64 is, for example, an aluminum die-cast product, and as is apparent from FIGS. 2 to 4, the first case 130, the second case 132, and the third case integrally connected to each other by a large number of bolts. Case 13
4 and a cap 136, and a first chamber 138 for housing the fluid coupling 12 and a CVT.
16, a second chamber 140 for accommodating the forward-reverse switching device 14, a third chamber 142 for accommodating the forward-reverse switching device 14, a fourth chamber 144 for accommodating the stepped transmission 18, a reduction gear device 20 and a differential gear device 2
And a fifth chamber 146 that accommodates 2 is provided. Also,
In the second case 132, the hydraulic cylinders 63, 67,
A valve body 148 (see FIG. 2) incorporating a control valve or the like for controlling the supply of hydraulic oil to 106, 108, etc.
Is fixed by bolts, and a cover 150 is fixed so as to cover the valve body 148. The valve body 148 is fixedly provided with an accumulator 152 for suppressing fluctuations in hydraulic pressure.
The accumulator 152 is located in the second chamber 140. The second case 132 also includes the first case 1
A pump housing 154 that constitutes the hydraulic pump 40 is fixedly provided on the end surface on the side of 30.

Then, the transaxle clutches 62 and 100 and the brake 6 configured as described above.
6 and 104 are shown in FIG. 6 according to the operation range of the shift lever.
The engagement is controlled as shown in FIG.

The step-variable transmission 18 is constructed so that its axial dimension is as short as possible. That is, as shown in detail in FIG. 7, the ring gear 9 is connected via a disc-shaped connecting member 158 that is spline-fitted to the shaft end of the output shaft 70 of the CVT 16 that functions as the input shaft of the stepped transmission 18.
2 is connected to its output shaft 70. Second output shaft 96
Is provided so that the shaft end of the output shaft 70 is fitted in the end opening of itself so as to be relatively rotatable about the common axis with the output shaft 70. A bottomed cylindrical power transmission member 201 for connecting the carrier 98 to the second output shaft 96.
The center portion of the second output shaft 96 is spline-fitted with the shaft end portion of the second output shaft 96.
It is rotatably supported from the 0 side, that is, the CVT 16 side via the pinion pin 160 and the bearing 161. The sun gear 90 is provided at the end of the tubular member 162.

The tubular member 162 has a cylindrical portion 164 protruding from the second case 132 on the outer peripheral side of the output shaft 70.
Are supported so as to be relatively rotatable via a sleeve 166 and a bearing 168 fitted to the inner peripheral surface thereof. A bearing 169 is inserted between the shaft end portion of the output shaft 70 and the inner peripheral surface of the tubular member 162, whereby the bearing 169 between the planetary gear device that constitutes the stepped transmission 18 and the output shaft 70 is interposed. The centering is done.

A clutch drum 170 is fixed to the tubular member 162 via an inner peripheral member 172. Further, the one-way clutch 10 is provided on the outer periphery of the inner peripheral member 172.
2 and the outer peripheral member 174 are fitted together. The inner peripheral member 172 and the outer peripheral member 174 form the one-way clutch 10.
It corresponds to two inner and outer rings. Second case 132
A plurality of disc-shaped friction plates 17 that constitute the low speed stage brake 104 are provided on the inner wall of the outer peripheral member 174 and the outer peripheral portion of the outer peripheral member 174.
6a and 176b are engaged with each other so as to be movable in the axial direction in a state of being overlapped with each other. The hydraulic cylinder 108 has a cylinder case 180 having an annular groove 178.
And an annular piston 182 slidably fitted in the cylinder case 180. The annular piston 182 allows the friction plates 176a and 176b to be disposed.
Is configured to be pressed.

The clutch drum 170 is a tubular member 1.
Bottom wall 184 fixed to 62 via an inner peripheral member 172
And an outer peripheral wall 186 projecting from the outer peripheral edge portion of the bottom wall 184 in the axial direction and located on the outer peripheral side of the bottomed cylindrical power transmission member 201 to form a bottomed cylindrical shape. An annular groove 188 is formed at the bottom of the clutch drum 170, and an annular piston 190 of the hydraulic cylinder 106 is slidably fitted in the annular groove 188. The bottom of the clutch drum 170 also serves as the cylinder case of the hydraulic cylinder 106. Then, the outer peripheral wall 186
Ribs 192 on the inner peripheral surface of the cylinder and a cylindrical power transmission member 201 with a bottom
The ribs 194 on the outer peripheral surface of the
A plurality of disc-shaped friction plates 196a and 19
6b are overlapped with each other and engaged with each other so as to be movable in the axial direction. The friction plates 196a and 196b
Is prevented from moving in the axial direction by a retaining ring 197 on the inner peripheral surface of the outer peripheral wall 186.
It is adapted to be pressed by a protrusion (not shown) protruding from. Further, the spring receiving member 198 is fitted on the inner peripheral surface of the outer peripheral wall 186 in a state of being axially positioned by the retaining ring 200, and the spring receiving member 1
A return spring 202 is inserted between the 98 and the annular piston 190. The spring receiving member 198 and the return spring 202 are also located between the inner peripheral surface of the outer peripheral wall 186 and the outer peripheral surface of the bottomed cylindrical power transmission member 201.

The pair of seal members 2 for sealing the oil passage 206 that guides the engagement operating pressure to the hydraulic cylinder 106.
08 is disposed in the annular groove on the outer peripheral portion of the cylindrical portion 164. Further, the bottomed cylindrical power transmission member 201 and the connecting member 158 are lubricated in the pinion pin 160 with the oil guided by the cylindrical protrusion 209 after lubricating the bearing supporting the second output shaft 96. Through holes 212 and 214 for leading to the oil passage 210 are provided, respectively. The arrow in FIG. 7 indicates the path of the oil. Further, the lubricating oil that has been pressure-fed to the oil passage 202 flows according to centrifugal force, and the sun gear 90, the planetary gear 94, and the ring gear 92.
At the same time, the high speed gear clutch 100 on the outer periphery of the above is lubricated.

As described above, according to this embodiment, the bottom wall 184 fixed to the tubular member 162 and the cylindrical power transmission member 2 with a bottom protruding axially from the outer peripheral edge portion of the bottom wall 184.
01, a bottomed cylindrical clutch drum 170 having an outer peripheral wall 186 located on the outer peripheral side is provided, and friction plates 196a and 196b of the high speed stage clutch 100 are provided.
, The sun gear 90 and the ring gear 9 are engaged with the inner peripheral surface of the clutch drum 170 and the outer peripheral surface of the cylindrical power transmission member 201, respectively, in a state of being overlapped with each other.
2. A planetary gear unit including the planetary gear 94 and the friction plates 196a and 196b of the high speed clutch 100.
Is housed in the clutch drum 170 and the outer peripheral wall 18
6 will be arranged so as to overlap in the radial direction. Therefore, the dimension of the entire stepped transmission 18 in the axial direction is shortened, and the stepped transmission 18 can be easily mounted on a vehicle in which the allowable space is limited.

Further, according to this embodiment, as described above,
Since the axial dimension of the stepped transmission 18 is shortened, the centering accuracy is improved, and the end portion of the output shaft 70 and the supporting portion of the tubular member 162 are reduced, so that the number of bearings is reduced.

Further, according to this embodiment, since the clutch drum 170 has a large diameter and the pressure receiving area of the annular piston 190 in the hydraulic cylinder 106 increases, the transmission torque capacity of the high speed clutch 100 can be easily obtained. Therefore, there is an advantage that the number of friction plates 196a and 196b can be reduced.

Further, according to the present embodiment, the releasing action of the one-way clutch 102 reduces the drag loss of the low-speed stage brake 104 during normal traveling, which is advantageous in improving fuel consumption.

Further, according to this embodiment, the sun gear 90,
By supplying the lubricating oil to the inner peripheral portion of the planetary gear device including the ring gear 92 and the planetary gear 94, not only the planetary gear device but also the high-speed stage clutch 100 can be lubricated at the same time, and at the same time, the high-speed stage Since the clutch 100 rotates integrally with the carrier 98, the clutch 100 is favorably lubricated by the scraping effect even during the engagement thereof.

Further, since the planetary gear device and the high speed clutch 100 are centered around a common axis of rotation, the friction plates 196a and 196b in engagement can be stably contacted with each other and durability is improved. Be done.

Although one embodiment of the present invention has been described in detail with reference to the drawings, the present invention can be implemented in other modes.

For example, in the above-described embodiment, the stepped transmission 18 provided in the CVT 16 is described as an example of the planetary gear type automatic transmission, but a plurality of planetary gear devices should be arranged in the axial direction. It is also possible to use an automatic transmission of a type in which a plurality of gears are selectively established by the above, that is, an automatic transmission called a so-called A / T.

Further, although the one-way clutch 102 is provided in the stepped transmission 18 of the above-mentioned embodiment, it is not always essential.

Although not illustrated one by one, the present invention can be implemented in various modified and improved modes based on the knowledge of those skilled in the art.

[Brief description of drawings]

FIG. 1 is a skeleton diagram illustrating a driving force transmission system of a transaxle to which the present invention is applied.

2 is a partial cross-sectional view showing the configuration of the embodiment of FIG. 1 together with FIG. 3 and FIG.

3 is a partial cross-sectional view showing the configuration of the embodiment of FIG. 1 together with FIG. 2 and FIG.

4 is a partial cross-sectional view showing the configuration of the embodiment of FIG. 1 together with FIG. 2 and FIG.

5 is a side view showing the positional relationship of each axis of the embodiment of FIG. 1. FIG.

FIG. 6 is a diagram for explaining the operation of the clutch and the brake in the embodiment of FIG.

FIG. 7 is a diagram illustrating in detail the stepped transmission shown in FIG.

[Explanation of symbols]

 18 stepped transmission (planetary gear type automatic transmission) 70 output shaft (first rotary shaft) 90 sun gear 92 ring gear 94 planetary gear 96 second output shaft (second rotary shaft) 98 carrier 100 high speed clutch 170 clutch drum 184 Bottom wall 186 Outer peripheral wall 196a, 196b Friction plate 201 Bottomed cylindrical power transmission member

Claims (1)

[Claims] 1. A first rotating shaft and a second rotating shaft that rotate about a uniaxial center, a ring gear that has inner peripheral teeth and is connected to the first rotating shaft, and meshes with the inner peripheral teeth of the ring gear. A carrier that rotatably supports the planetary gears from the first rotation shaft side thereof, a bottomed cylindrical power transmission member that connects the carrier and the second rotation shaft so as to cover the ring gear, and the first A planetary gear device including a tubular member having a sun gear that is fitted relative to the outer peripheral side of a rotating shaft and meshes with the planetary gear; and a sun gear that includes a disc-shaped friction plate and the second rotating shaft. In a vehicular planetary gear type automatic transmission including a multi-plate clutch for connecting the above, a bottom wall fixed to the tubular member, and the cylindrical power with a bottom protruding axially from an outer peripheral edge portion of the bottom wall. And an outer peripheral wall located on the outer peripheral side of the transmission member. A bottomed cylindrical clutch drum is provided, and the friction plates of the clutch are engaged with the inner peripheral surface of the clutch drum and the outer peripheral surface of the bottomed cylindrical power transmission member, respectively, in a state of being overlapped with each other. A characteristic planetary gear type automatic transmission for vehicles.