JP2002227940A - Automatic transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an automatic transmission which can add a speed change stage containing a direct connection stage on the high speed stage side so as to make a gear ratio closer, derive the optimum performance of an engine in the high speed range of the vehicle speed, and obtain a gear ratio of 7th stage forward or higher which provides high effectiveness and small vehicle speed change at gear change to offer excellent feeling. SOLUTION: The automatic transmission is provided with a reduction gear device generating decelerated revolution whose number of revolution is less than that of an input shaft. A decelerated revolution output member is changed to be at decelerated revolution status or free revolution status by revolution status switching means. Decelerated revolution of the decelerated revolution output member is selectively transmitted to the fourth and the first elements of a dual planetary gear train for speed change through the first and third control clutches. While revolution of the input shaft is transmitted to the second element through the second control clutch, the revolutions of the first and the second elements are selectively regulated with the second control brake to connect the third element to the output shaft.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a control compound clutch and a control brake connected to each element of a dual gear planetary gear system connected to an input shaft to shift the rotation of the input shaft to a plurality of stages. And an automatic transmission for transmitting power to an output shaft.

[0002]

2. Description of the Related Art First and second sun gears are directly meshed with the first sun gear, and the second sun gear is connected to the second sun gear via an intermediate pinion.
A transmission double planetary gear device having a long pinion meshed with the sun gear, a carrier supporting the intermediate pinion, and a ring gear meshed with the long pinion and connected to the output shaft; a ring gear connected to the input shaft; and a transmission case. A reduction planetary gear device comprising a carrier that supports a pinion engaged with the fixed sun gear and ring gear and the sun gear; and a reduction planetary gear device reduced in speed so that the number of rotations is smaller than the rotation of the input shaft. The rotation of the carrier is selectively transmitted to the second and first sun gears by the first and third control clutches, and the rotation of the input shaft is selectively transmitted to the carrier of the dual gear planetary gear set by the second control clutch. The rotation of the first sun gear and the carrier of the compound planetary gear unit for shifting is controlled by the first and second control brakes. In 6 forward speeds and selectively regulated, automatic transmission holds the gear ratio of the first stage recession Patent 4-219
No. 553.

[0003]

The above-mentioned conventional automatic transmission has a short overall length and is suitable for a front-wheel drive vehicle of a horizontal engine. However, in recent years, in order to improve fuel efficiency and power transmission performance, or to obtain a gear ratio that matches the driver's preference, an automatic transmission that can establish a gear ratio of seven or more forward gears that are appropriately separated has been developed. It has been demanded.

SUMMARY OF THE INVENTION The present invention has been made in order to meet such a demand, and a gear ratio including a directly connected gear is added to a high gear to further increase the gear ratio, thereby optimally extracting engine performance in a high vehicle speed range. It is an object of the present invention to provide an automatic transmission that can achieve a high gear ratio of seven or more forward speeds with high efficiency, a small change in output torque at the time of gear change, and a good feeling.

[0005]

In order to solve the above-mentioned problems, a structural feature of the present invention according to claim 1 is that an input shaft is connected to the input shaft and the number of rotations is smaller than that of the input shaft. A gear reduction device that generates reduced rotation at a reduced rotation output member, and first, second, third, and fourth elements corresponding to four elements sequentially arranged at intervals corresponding to a gear ratio in a velocity diagram. A speed change compound planetary gear device having four elements, rotation state switching means for switching the reduced rotation output member to a reduced rotation state or a free rotation state, and the reduced rotation output member and the fourth and first elements, respectively. First and third control clutches detachably connected to each other, the input shaft and the second control clutch;
A second control clutch for releasably connecting the elements, first and second control brakes for selectively restricting rotation of the first and second elements, and an output shaft connected to the third element. It is to have.

A structural feature of the invention according to claim 2 is that, in the automatic transmission according to claim 1, the rotation state switching means rotates the reduced rotation output member by the gear reduction device in the reduced rotation state in the reduced rotation state. In the free rotation state, the reduced rotation output member is allowed to rotate other than the reduced rotation.

According to a third aspect of the present invention, in the automatic transmission according to the first aspect, in the automatic transmission, the rotation state switching means controls the reduced rotation by the gear reduction device in the reduced rotation state. In the free rotation state, the reduced speed rotation is not generated by the reduced speed output member by the gear reduction device.

According to a fourth aspect of the present invention, in the automatic transmission according to the first aspect, when the rotation state switching means is in a reduced rotation state, the rotation state switching means is connected to the input shaft via a gear reduction device to reduce the rotation. Power transmission between the output member and the output member is permitted, and in a free rotation state, power transmission between the input shaft and the reduced rotation output member via the gear reduction device is cut off.

According to a fifth aspect of the invention, there is provided an automatic transmission according to any one of the first to fourth aspects, wherein the small-diameter and large-diameter sun gears have a large diameter and a small-diameter and large-diameter sun gear, respectively. The gear reduction device is composed of a carrier supporting a stepped pinion made of a small diameter pinion, and a double planetary gear device for reduction composed of a ring gear connected to the input shaft and meshing with the large diameter pinion, wherein the carrier is the gear reduction device. The rotation state switching means is constituted by first and second rotation control brakes connected to the first and third control clutches as deceleration rotation output members for selectively restricting rotation of the small-diameter and large-diameter sun gears, respectively. It was done.

According to a sixth aspect of the present invention, in the automatic transmission according to any one of the first to fourth aspects, a sun gear, a long pinion meshed with the sun gear, and an intermediate pinion meshed with the long pinion are provided. The gear reduction device is constituted by a double reduction gear planetary gear device having a carrier that supports the input shaft, a front ring gear that is connected to the input shaft and meshes with the long pinion, and a rear ring gear that meshes with the intermediate pinion. The rotation state switching means is constituted by first and second rotation control brakes which are connected to the first and third control clutches as deceleration rotation output members of the reduction gear transmission and selectively restrict the rotation of the sun gear and the subsequent ring gear, respectively. It was done.

According to a seventh aspect of the present invention, in the automatic transmission according to any one of the first to fourth aspects, a sun gear, a carrier that supports a pinion that meshes with the sun gear, and the input shaft are connected to the sun gear. The gear reduction device is configured by a reduction planetary gear device including a ring gear meshing with the pinion, and the carrier is connected to the first and third control clutches as a reduction rotation output member of the gear reduction device. The rotation state switching means is constituted by a rotation control brake for selectively restricting rotation and a rotation control clutch for detachably connecting any two of the sun gear, carrier and ring gear.

According to an eighth aspect of the invention, there is provided an automatic transmission according to any one of the first to fourth aspects, wherein the sun gear whose rotation is restricted, a carrier that supports a pinion that meshes with the sun gear, and the carrier. A deceleration planetary gear device comprising a ring gear connected to an input shaft and meshing with the pinion; The gear reduction device is constituted by members, the reduced rotation output member is connected to the first and third control clutches, and the ring gear and the carrier are removably connected to the reduced rotation output member, respectively. First, the rotation state switching means is constituted by the second rotation control clutch.

According to a ninth aspect of the present invention, in the automatic transmission according to any one of the first to fourth aspects, a sun gear whose rotation is restricted, a carrier that supports a pinion that meshes with the sun gear, and the carrier. The gear reduction device is configured by a reduction planetary gear device including a ring gear that meshes with a pinion, and the carrier is connected to the first and third control clutches as a reduction rotation output member of the gear reduction device,
The rotation state switching means is constituted by first and second rotation control clutches which releasably connect the carrier and the ring gear of the planetary gear device for reduction with the input shaft.

[0014] The constitutional feature of the invention according to claim 10 is as follows.
5. The automatic transmission according to claim 1, wherein the gear comprises a sun gear, a carrier that supports a pinion that meshes with the sun gear, and a reduction planetary gear device that is connected to the input shaft and meshes with the pinion. 6. A speed reduction device, wherein the carrier is connected to the first and third control clutches as a speed reduction rotation output member of the gear speed reduction device, and the rotation state switching means includes a rotation control brake for selectively restricting rotation of the sun gear. That is,

[0015] The constitutional feature of the invention according to claim 11 is as follows.
5. The automatic transmission according to claim 1, wherein the planetary gear comprises a sun gear whose rotation is restricted, a carrier that supports a pinion that meshes with the sun gear, and a ring gear that is connected to the input shaft and meshes with the pinion. 6. A gear device, and a reduced-speed rotation output member that is provided rotatably concentrically with the reduction planetary gear device and selectively transmits the rotation of the carrier to form the gear reduction device; The rotation state switching means is constituted by a rotation control clutch that is connected to the first and third control clutches and that releasably connects the carrier and the reduced rotation output member.

According to a twelfth aspect of the present invention,
5. The automatic transmission according to claim 1, wherein the reduction gear comprises a sun gear whose rotation is restricted, a carrier that supports a pinion that meshes with the sun gear, and a ring gear that meshes with the pinion. A gear, and the carrier is connected to the first and third control clutches as a reduction rotation output member of the planetary gear unit for reduction, so that the ring gear of the planetary gear unit for reduction and the input shaft can be disengaged. The rotation state switching means is constituted by the rotation control clutch to be connected.

The constitutional feature of the invention according to claim 13 is that
The automatic transmission according to any one of claims 1 to 4, wherein a plurality of gears fixed to an input shaft are rotatably supported concentrically with the speed change double planetary gear device, and mesh with the plurality of gears for input. A reduction gear train composed of a plurality of gears that generate rotation and reduced rotation, and a reduced rotation output member that is rotatably provided concentrically with the double gear planetary gear device for transmission and to which the reduced rotation is selectively transmitted. A rotation that constitutes the gear reduction device, connects the reduced rotation output member to the first and third control clutches, and removably connects the reduced rotation output member to a gear that generates reduced rotation of the gear train. The rotation state switching means is constituted by a control clutch.

According to a fourteenth aspect of the present invention,
The automatic transmission according to any one of claims 1 to 13, wherein at least one of two sets of planetary gear mechanisms constituting the double gear planetary gear device for shifting is a double pinion type planetary gear mechanism, and a third element. Is a ring gear.

The constitutional feature of the invention according to claim 15 is that
14. The automatic transmission according to claim 1, wherein the first and second sun gears, the long pinion that meshes directly with the first sun gear, and meshes with the second sun gear via an intermediate pinion. A carrier that supports an intermediate pinion and a ring gear that meshes with the long pinion and is connected to the output shaft to constitute the double gear planetary gear device for shifting, wherein the first element is the first sun gear, the second element is the carrier, The third element is a ring gear, and the fourth element is a second sun gear.

[0020]

According to the first aspect of the present invention, there is provided a gear reduction device for generating a reduced rotation at a reduced rotation output member, the reduced rotation having a lower rotation speed than the rotation of the input shaft. The member is switched to any one of the reduced rotation state and the free rotation state by the rotation state switching means, and the reduced rotation of the reduced rotation output member is controlled by the first and third control clutches of the fourth and first gear shift planetary gear units. Selectively transmitting the rotation of the input shaft to the second element by the second control clutch, and transmitting the rotation of the first and second elements to the first and second elements.
The second control brake selectively regulates and the third element is connected to the output shaft, so with only minimal changes to the conventional automatic transmission, the rotation of the input shaft is more than seven steps forward with proper separation. And a compact automatic transmission having a short overall length that can be transmitted to the output shaft after being shifted at the gear ratio described above. Furthermore, since the gear ratio on the high speed side can be made denser, the engine performance can be optimally brought out in the high speed range of the vehicle speed, and the change in the gear ratio at the time of the gear change and, consequently, the output torque change. It becomes small and a good feeling can be obtained. In addition, the first and fourth elements of the double planetary gear device for transmission are connected by connecting the first to third control clutches with the reduced rotation output member in the free rotation state, and the input shaft transmitted to the second element is transmitted. Can be obtained at a gear ratio of 1 to transmit the rotation of the third element to the third element.
Fuel efficiency can be improved.

According to the second aspect of the present invention, the deceleration rotation output member is rotated by the deceleration rotation state by the rotation state switching means in the deceleration rotation state, and the deceleration rotation output member is decelerated in the free rotation state. Since rotation other than rotation is allowed, the first and fourth elements of the compound planetary gear device for transmission are connected by connecting the first to third control clutches and transmitted to the second element. It is possible to obtain a direct connection stage in which the rotation of the input shaft is transmitted to the third element at a gear ratio of 1, thereby improving fuel efficiency.

In the invention according to claim 3 configured as described above, the rotation state switching means allows the gear reduction device to generate reduced speed rotation on the reduced speed rotation output member in the reduced speed rotation state. In the rotating state, the reduced speed rotation is prevented from being generated in the reduced speed rotation output member by the gear reduction device. , A direct connection stage for transmission can be obtained, and fuel efficiency can be improved.

In the invention according to claim 4 configured as described above, the rotation state switching means transmits the power transmission between the input shaft and the reduced rotation output member via the gear reduction device in the reduced rotation state. In the free rotation state, the power transmission between the input shaft and the reduced rotation output member via the gear reduction device is cut off. It is possible to obtain a direct connection stage in which rotation is transmitted to the third element at a gear ratio of 1, thereby improving fuel efficiency.

According to the fifth aspect of the present invention, the rotation of the small-diameter and large-diameter sun gears of the compound planetary gear device for reduction is selectively regulated by the first and second rotation control brakes, respectively. Is switched to one of the first, second, and free rotation states, and the first and second rotations are selected by the first and third control clutches as the fourth and first elements of the compound planetary gear device for shifting. And the rotation of the input shaft is selectively transmitted to the second element by the second control clutch. Therefore, in addition to the effect of the invention described in claim 1, it is necessary to reduce the speed of the conventional automatic transmission. The planetary gear set is a double type having a stepped pinion, and the rotation of the input shaft is appropriately separated by simply adding two rotation control brakes.
It is possible to obtain a compact automatic transmission having a short overall length that can be transmitted at a gear ratio of two-stage reverse and two-stage reverse and transmitted to the output shaft.

In the sixth aspect of the present invention, the rotation of the sun gear and the rear ring gear of the compound planetary gear device for reduction is selectively regulated by the first and second rotation control brakes to selectively control the carrier. The first and second rotations are switched to any one of the first and second rotation states and the free rotation state, and the first or second rotation is transmitted to the fourth and first elements of the dual gear planetary gear device for gear shifting via the first and third control clutches. Since the rotation is selectively transmitted and the rotation of the input shaft is selectively transmitted to the second element by the second control clutch, in addition to the effect of the invention described in claim 1, it is possible to reduce the speed of the conventional automatic transmission. With another type of planetary gear set, simply adding two rotation control brakes will transmit the input shaft rotation to the output shaft by shifting the rotation of the input shaft at a gear ratio of 12 forward gears and 2 reverse gears that are appropriately separated. The short length that can be It can be obtained transfected automatic transmission.

In the invention according to claim 7, the rotation of the sun gear of the planetary gear unit for reduction is selectively regulated by the rotation control brake, and any two of the sun gear, the carrier and the ring gear are rotated. The control clutch connects the carrier to one of the first and second rotation states and the free rotation state, and switches the first or second rotation by the first and third control clutches. 4. Selectively transmit to the first element and rotate the rotation of the input shaft to the second
Since the control clutch selectively transmits to the second element, in addition to the effect of the invention described in claim 1, the input shaft can be obtained simply by adding a rotation control clutch and a rotation control brake to the conventional automatic transmission. Forward with proper rotation of the rotation 9
It is possible to obtain a compact automatic transmission having a short overall length that can be transmitted at a gear ratio of two-stage reverse and two-stage reverse and transmitted to the output shaft.

In the invention according to claim 8 configured as described above, the reduction rotation output member is provided rotatably concentrically with the planetary gear device for reduction, and the reduction rotation output member is provided with a ring gear of the planetary gear device for reduction. The deceleration rotation output member is selectively connected to the carrier by first and second rotation control clutches to switch the deceleration rotation output member to one of the first, second rotation state and free rotation state, and the rotation of the deceleration rotation output member is changed to the first rotation state. First and third control clutches make it possible to change the speed of the compound planetary gear train.
Since the rotation of the input shaft is selectively transmitted to the second element by the second control clutch,
In addition to the effects of the invention as set forth in claim 1, in addition to the conventional automatic transmission, only by adding a deceleration rotation output member and two rotation control clutches, the forward rotation of the input shaft is appropriately separated by nine steps,
It is possible to obtain a compact automatic transmission having a short overall length which can be transmitted at a gear ratio of two reverse speeds and transmitted to the output shaft.

In the invention according to the ninth aspect, the input shaft is selectively connected to the ring gear and the carrier of the planetary gear device for reduction by the first and second rotation control clutches to connect the carrier to the first gear. , Switching to one of the second rotation state and the free rotation state, and selectively connecting the first or second rotation to the fourth and first elements of the dual gear planetary gear device for shifting by the first and third control clutches. Since the rotation of the input shaft is selectively transmitted to the second element by the second control clutch, the conventional automatic transmission has two rotation control clutches in addition to the effect of the invention described in claim 1. 9 steps forward with the input shaft rotating properly separated,
It is possible to obtain a compact automatic transmission having a short overall length which can be transmitted at a gear ratio of two reverse speeds and transmitted to the output shaft.

In the invention according to claim 10 configured as described above, the rotation of the sun gear of the planetary gear unit for reduction is selectively regulated by the rotation control brake to switch the carrier to the reduced rotation state or the free rotation state, Deceleration rotation is first,
The third control clutch selectively transmits the rotation to the fourth and first elements of the compound planetary gear device for transmission, and the rotation of the input shaft is selectively transmitted to the second element by the second control clutch. In addition to the effect of the invention described in the item 1, in addition to the addition of a rotation control brake to the conventional automatic transmission, the rotation of the input shaft is shifted and output at a gear ratio of seven forward steps and one reverse step which are appropriately separated. A compact automatic transmission having a short overall length that can be transmitted to a shaft can be obtained.

According to the eleventh aspect of the present invention, the deceleration rotation output member is rotatably provided concentrically with the deceleration planetary gear device, and the deceleration rotation output member is mounted on the carrier of the deceleration planetary gear device. The deceleration rotation output member is switched to a deceleration rotation state or a free rotation state by being selectively connected by a rotation control clutch, and the rotation of the deceleration rotation output member is rotated by a first and a third control clutch. , To selectively transmit the rotation of the input shaft to the second element.
Since the control clutch selectively transmits to the second element, in addition to the effect of the invention described in claim 1, the input can be achieved simply by adding a deceleration rotation output member and a rotation control clutch to the conventional automatic transmission. Advance 7 with proper rotation of shaft
It is possible to obtain a compact automatic transmission having a short overall length, which can be transmitted to the output shaft by shifting at a gear ratio of one step and one reverse.

In the twelfth aspect of the present invention, the input shaft is selectively connected to the ring gear of the planetary gear unit for reduction by the rotation control clutch to switch the carrier to the reduced rotation state or the free rotation state. The decelerated rotation is selectively connected to the fourth and first elements of the dual gear planetary gear set for shifting by the first and third control clutches, and the rotation of the input shaft is selectively transmitted to the second element by the second control clutch. Therefore, in addition to the effect of the invention described in claim 1, the addition of a rotation control clutch to the conventional automatic transmission only allows the input shaft to rotate appropriately in the forward seven stages and the reverse one
It is possible to obtain a compact automatic transmission having a short overall length that can be transmitted to the output shaft by shifting at a gear ratio of the step.

In the thirteenth aspect of the present invention, the deceleration rotation output member is provided so as to be rotatable concentrically with the transmission planetary gear device, and the deceleration rotation output member is used to reduce the rotation of the reduction gear train. The deceleration rotation output member is selectively connected to the gear to be generated by a rotation control clutch to switch the deceleration rotation output member to the deceleration rotation state or the free rotation state, and the deceleration rotation output member is switched to the first rotation output member.
And the third control clutch selectively couples to the fourth and first elements of the dual gear planetary gear set for transmission, and selectively transmits the input rotation generated by the reduction gear train to the second element by the second control clutch. Therefore, in addition to the effect of the invention described in claim 1, the conventional planetary gear device for reduction of the automatic transmission is converted into a simple reduction gear train, and a reduction rotation output member and a rotation control clutch are added. By simply performing this operation, it is possible to obtain a compact automatic transmission having a short overall length capable of transmitting the rotation of the input shaft to the output shaft by appropriately shifting the gear ratio at seven or more forward gear ratios.

In the fourteenth aspect of the present invention, at least one of the two sets of planetary gear mechanisms forming the double gear planetary gear unit for shifting is a double pinion type planetary gear mechanism, and the third element is Since the output shaft is connected to the ring gear described above, in addition to the effect of the invention described in claim 1, a compact automatic transmission having a simple structure and a short overall length can be obtained.

According to the fifteenth aspect of the present invention, the first and second sun gears, the long pinion directly meshing with the first sun gear and meshing with the second sun gear via the intermediate pinion, and the intermediate pinion A double planetary gear device for speed change is constituted by a carrier supporting the pinion and a ring gear meshed with the long pinion and connected to the output shaft, the first element being a first sun gear, the second element being a carrier, the third element being a ring gear, Since the four elements are used as the second sun gear, the rotation of the input shaft is transmitted to the output shaft by shifting the rotation of the input shaft at a gear ratio of seven or more forward stages that are appropriately spaced apart with a minimum change to the conventional automatic transmission. A compact automatic transmission having a simple structure and a short overall length can be obtained.

[0035]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment of an automatic transmission according to the present invention will be described below with reference to the drawings. In FIG. 1, reference numeral 10 denotes an automatic transmission according to the present invention, for example, a fluid torque converter 1 rotationally driven by an automobile engine.
1 is used to transmit the output rotation to the drive wheels at a variable speed. The automatic transmission 10 includes an input shaft 15, a double reduction planetary gear unit 16, a double transmission planetary gear unit 17, and an output shaft 18, which are sequentially supported on a common axis 13 in a transmission case 12 mounted on a vehicle body. Have been. The compound planetary gear unit 16 for reduction includes the carriers C1, C of two single pinion type planetary gear mechanisms 51, 52.
2 and the ring gears R1 and R2 are connected and shared. That is, the compound planetary gear unit 16 for reduction includes the large-diameter and small-diameter sun gears S1 and S2 rotatably supported on the common axis 13 and the small-diameter and large-diameter pinions 23 meshing with the large-diameter and small-diameter sun gears S1 and S2, respectively. 24, a common carrier C1 and C2 rotatably supported on the common axis 13 and a large-diameter pinion 24 for rotatably supporting the stepped pinion 25 and engaging with the large-diameter pinion 24 on the common axis 13. Common ring gear R rotatably supported
1 and R2. The input shaft 15 is connected to the ring gears R1, R2.

The large-diameter and small-diameter sun gears S1 and S2 are connected to the transmission case 12, respectively, to selectively restrict the rotation. Each is connected to S2. As a result, the carriers C1 and C2 as the reduced rotation output members 55 are rotated at the first reduced rotation smaller than the rotation of the input shaft 15 because the rotation of the small-diameter sun gear S2 is restricted by the first rotation control brake B-1. In the reduced rotation state, the second rotation control brake B-2 restricts the rotation of the large-diameter sun gear S1, and the second reduced rotation state in which the number of rotations is smaller than the first reduced rotation is the second reduced rotation state. The two-rotation control brakes B-1 and B-2 are switched between a free rotation state in which the rotation is not operated and the rotation is not restricted.

The compound planetary gear unit 16 for reduction includes the input shaft 1
5 and a gear reduction device 49 for generating first and second reduced rotations having a lower rotation speed than the rotation of the input shaft 15, wherein the first and second rotation control brakes B- 1 and B- 2 are The rotation state switching means 50 for switching the carriers C1 and C2 as the reduced rotation output member 55 to the reduced rotation state or the free rotation state is configured.

The dual gear planetary gear set 17 for transmission is constructed by connecting and commonizing the carriers C3, C4 and the ring gears R3, R4 of the single pinion type planetary gear mechanism 53 and the double pinion type planetary gear mechanism 54, respectively. . That is, the first shaft rotatably supported on the common axis 13.
And directly mesh with the second sun gears S3, S4 and the first sun gear S3, and the intermediate pinion 33 is connected to the second sun gear S4.
Common carriers C3, C rotatably supported on the common axis 13 and rotatably supporting the long pinion 34, the long pinion 34 and the intermediate pinion 33 meshing with each other via
4 and common ring gears R3 and R4 that are engaged with the long pinion 34 and rotatably supported on the common axis 13. The output shaft 18 is connected to the ring gears R3 and R4.
Are connected.

Carrier C of double planetary gear set 16 for reduction
The first and second control clutches C-3 and C-1 for releasably connecting the first and second sun gears S3 and S4 of the transmission compound planetary gear set 17 with the input shaft 15; A second control clutch C-2 is provided for removably connecting the common carriers C3 and C4 of the dual gear planetary gear set 17 for shifting. Then, the first sun gear S3 and the carrier C3,
The first and second control brakes B-3 and B-4 for selectively connecting the first sun gear S3 and the carriers C3 and C4 to the transmission case 12 to restrict rotation are provided at C4.
Are connected. F-1 is a one-way clutch that regulates the rotation of the carriers C3 and C4 in the reverse direction.

The pump impeller 45 of the fluid torque converter 11 is driven to rotate by an engine (not shown) to send out oil, and the stator 46 receives a reaction force of the oil and generates torque to the turbine 47. The input shaft 15 is connected to a turbine 47. 48
Is a lock-up clutch for directly connecting the pump impeller 45 and the turbine 47.

In the automatic transmission 10 configured as described above, the first to third control clutches C-1 to C-3 are selectively disengaged and the first and second control brakes B-3, B −
By selectively operating the fourth and first and second rotation control brakes B-1 and B-2 to regulate the rotation of the elements of the planetary gear set, a gear ratio of 12 forward gears and 2 reverse gears is established. be able to. In FIG. 2, a black circle in the column of each control clutch and control brake corresponding to each shift speed indicates that the control clutch is in the connected state and the control brake is in the rotation restricting state. Also, in FIG.
The first reduction gear planetary gear mechanism 51 including the large-diameter sun gear S1, the stepped pinion 25, the carrier C1, and the ring gear R1 of the double reduction planetary gear set 16 has a gear ratio λ1 of 0.77.
8, small diameter sun gear S2, large diameter pinion 24, carrier C
2 and the gear ratio λ2 of the second planetary gear mechanism 52 for reduction including the ring gear R2 is 0.361, and the first sun gear S3, the long pinion 34, the carrier C3 and the ring gear R3 of the double planetary gear unit 17 for speed change are used. The gear ratio λ3 of the first planetary gear mechanism 53 is 0.458, and the second sun gear S
4, when the gear ratio λ4 of the second speed-changing planetary gear mechanism 54 including the intermediate pinion 33, the long pinion 34, the carrier C4, and the ring gear R4 is 0.375, the gear ratio (the rotational speed of the input shaft 15) / Output shaft 1
8 is shown in the gear ratio column.

In the single-pinion type first and second planetary gear mechanisms 51 and 52 for reduction and the first planetary gear mechanism 53 for speed change, the rotation speed Ns of the sun gear and the rotation speed N of the carrier are used.
c, Number of rotations Nr of ring gear and gear ratio λ of planetary gear mechanism
Is expressed by equation (1). In the double pinion type second planetary gear mechanism 54 for transmission, the sun gear rotation speed Ns, the carrier rotation speed Nc, and the ring gear rotation speed Nc
The relationship between r and the gear ratio λ of the planetary gear mechanism is expressed by Expression (2), and the gear ratio at each shift speed is calculated based on Expressions (1) and (2). The number of teeth of the large diameter, small diameter, first and second sun gears S1, S2, S3, S4 is Zs1, Zs2, Zs.
3, Zs4 and the number of teeth of the ring gears R1, R2, R3, and R4 are Zr1, Zr2, Zr3, and Zr4, the first and second reduction gears and the first and second speed change planetary gear mechanisms 51 to 54 are provided.
Gear ratios are λ1 = Zs1 / Zr1, λ2 = Zs2 / Zr
2, λ3 = Zs3 / Zr3, λ4 = Zs4 / Zr4.

Nr = (1 + λ) Nc−λNs (1) Nr = (1−λ) Nc + λNs (2) Selectively the first and second rotation control brakes B-1 and B-2. Activating the first and third control clutches C-1 to C-3 to selectively connect the first and second control brakes B-
When 3, B-4 is selectively operated, the speed ratio of each element of the compound planetary gear unit 16 for reduction and the compound planetary gear unit 17 for transmission is as shown in the velocity diagram shown in FIG. In the velocity diagram, each element consisting of the sun gear, the carrier, and the ring gear of the planetary gear device was arranged at intervals corresponding to the gear ratio in the horizontal axis direction, and the speed ratio was taken in the vertical axis direction corresponding to each element. Things. FIG. 3 shows speed diagrams of the compound planetary gear units 16 and 17 for speed reduction and speed change, arranged side by side. In the first and second reduction gear planetary gear mechanisms 51 and 52 that constitute the reduction compound planetary gear device 16, the carriers C1 and C2 are used.
Since C2 and the ring gears R1 and R2 are common,
C1, C2 and R1, R2 respectively represent the speed ratios of the common carriers C1, C2 and the common ring gears R1, R2 on one vertical line respectively, each of which has S1, S2 respectively. The speed ratio between the sun gears S1 and S2 is shown on the vertical line. Regarding the single pinion type first planetary gear mechanism 51, the distance a between the vertical line of the carrier C1 and the vertical line of the ring gear R1 is regarded as the gear ratio λ1 of the first planetary gear mechanism 51,
The vertical line of the sun gear S1 is arranged on the opposite side of the vertical line of the ring gear R1 from the vertical line of the carrier C1 with an interval a / λ1. Similarly, for the single-pinion type second planetary gear mechanism 52, the distance a between the vertical line of the carrier C2 and the vertical line of the ring gear R2 is regarded as the gear ratio λ2 of the second planetary gear mechanism 52, and the vertical line of the sun gear S2 is The carrier C2 is disposed on the opposite side of the vertical line of the ring gear R2 from the vertical line of the carrier C2, at a distance of a / λ2.

In the transmission first and second planetary gear mechanisms 53 and 54 constituting the double transmission planetary gear unit 17, the carriers C3 and C4 and the ring gears R3 and R4 are common, so that C3, C4 and R3 and R4 are used. Represent the speed ratios of the common carriers C3 and C4 and the common ring gears R3 and R4 on one vertical line respectively marked S3 and S4.
The speed ratio of the sun gears S1 and S2 is represented on each of the vertical lines with. For the single pinion type first planetary gear mechanism 53 for transmission, the vertical line of the carrier C3 and the ring gear R
3 is regarded as the gear ratio λ3 of the first planetary gear mechanism 53 for transmission, and the vertical line of the sun gear S3 is defined as the carrier C3.
From the vertical line of the ring gear R3 to the opposite side of the vertical line of the ring gear R3.
Place them three spaces apart. Second for double pinion type shifting
Regarding the planetary gear mechanism 54, the distance b between the vertical line of the carrier C4 and the vertical line of the ring gear R4 is regarded as the gear ratio λ4 of the second planetary gear mechanism 54 for shifting, and the vertical line of the sun gear S4 is shifted from the vertical line of the carrier C4. The ring gear R4 is disposed on the same side of the vertical line as the ring gear R4 with an interval b / λ4. The speed diagram shows the first and second rotation control brakes B-1, B-2, the first to third control clutches C-1 to C-3, and the first and second control brakes B-3, B-. 4 are selectively activated at points B-1 to B
-4, C-1 to C-3 are entered.

In the speed diagram of the compound planetary gear device 17 for shifting thus prepared, the elements corresponding to the four vertical lines are represented by the first, second, third and fourth elements in the order of the vertical lines. And In the case of the first embodiment, the first sun gear S3 as the first element is connected to the third control clutch C-3 and the first control brake B-3, and the carriers C3 and C as the second elements.
4 is a second control clutch C-2 and a second control brake B-
4, ring gears R3, R4 as third elements
Is connected to the output shaft 18, and the second sun gear S4 as a fourth element is connected to the first control clutch C-1.

The operation of each shift speed will be described below.
In the case of the first forward speed, the rotation of the large-diameter sun gear S1 is restricted by the operation of the second rotation control brake B-2 constituting the rotation state switching means 50, and the carriers C1 and C2 as the reduced rotation output members 55 are moved to the second rotation. The state is switched to the deceleration rotation state, the first control clutch C-1 is operated, and the carrier C
1, C2 and the second sun gear S4 are connected, and the one-way clutch F-1 operates to restrict the reverse rotation of the carriers C3, C4. Therefore, the rotation input to the input shaft 15 is the same as that of the ring gears R1, R2. The restricted large-diameter sun gear S1 and the carriers C1 and C2 that support the reaction force reduce the speed of the input shaft 15 to a second reduced rotation that is lower in rotation speed than the rotation of the input shaft 15, and
The reverse rotation is regulated by the control clutch C-1, the second sun gear S4, and the one-way clutch F-1 and transmitted to the ring gears R3 and R4 via the carriers C3 and C4 that support the reaction force, and the output shaft 18 is moved to the first gear. Is driven forward at a gear ratio of 4.741. The rotation of the carriers C3 and C4 may be restricted by operating the second control brake B-4.

In the second forward speed, the rotation of the small-diameter sun gear S2 is restricted by the first rotation control brake B-1 constituting the rotation state switching means 50, and the carriers C1 and C2 are switched to the first reduced rotation state. First control clutch C-
1 is operated and the carriers C1 and C2 and the second sun gear S4
Is connected, and the one-way clutch F-1 operates to restrict the reverse rotation of the carriers C3 and C4. Therefore, the rotation input to the input shaft 15 is restricted by the ring gears R1 and R2 and the rotation to support the reaction force. Small diameter sun gear S2, carrier C
1 and C2, the rotation speed is reduced to a first reduced rotation that is smaller than the rotation of the input shaft 15 and larger than the second reduced rotation, and the first control clutch C-1, the second sun gear S4, and the one-way clutch F-1 restrict reverse rotation. And transmitted to the ring gears R3 and R4 via the carriers C3 and C4 that support the reaction force,
The output shaft 18 is driven to rotate normally at a gear ratio of 3.630 at the second speed.

In the case of the third forward speed, the rotation of the large-diameter sun gear S1 is regulated by the operation of the second rotation control brake B-2, and the carriers C1 and C2 are switched to the second reduced speed rotation state. -1 is activated and carrier C
1, C2 and the second sun gear S4 are connected, and the first control brake B-3 is operated to regulate the rotation of the first sun gear S3. , The large-diameter sun gear S1 supporting the reaction force and being reduced to the second reduced rotation by the carriers C1 and C2, the first control clutch C-1, the second sun gear S4,
The rotation is regulated and transmitted to the ring gears R3 and R4 via the first sun gear S3 and the carriers C3 and C4 that support the reaction force, and the output shaft 18 is driven to rotate forward at the gear ratio 2.709 of the third speed change step.

In the fourth forward speed, the rotation of the small-diameter sun gear S2 is restricted by the first rotation control brake B-1, and the carriers C1 and C2 are switched to the first reduced rotation state.
When the first control clutch C-1 is operated, the carriers C1, C
2 and the second sun gear S4 are connected, and the first control brake B
-3 is operated and the rotation of the first sun gear S3 is restricted, so that the rotation input to the input shaft 15 is controlled by the ring gear R1,
R2, small-diameter sun gear S whose rotation is regulated to support the reaction force
2. The speed is reduced to the first reduced speed by the carriers C1 and C2, and via the first control clutch C-1, the second sun gear S4, the first sun gear S3 whose rotation is regulated and the reaction force is supported, and the carriers C3 and C4. The power is transmitted to the ring gears R3 and R4, and the output shaft 18 is driven to rotate forward at a gear ratio of 2.074 at the fourth speed.

In the case of the fifth forward speed, the rotation of the large-diameter sun gear S1 is restricted by the operation of the second rotation control brake B-2, and the carriers C1 and C2 are switched to the second reduced rotation state. Since the control clutch C-1 is operated to connect the carriers C1 and C2 to the second and first sun gears S4 and S3, the rotation input to the input shaft 15 is restricted by the rotation of the ring gears R1 and R2, and is restricted. The large-diameter sun gear S1 supporting the force is reduced to the second reduced rotation by the carriers C1 and C2, and transmitted to the second and first sun gears S4 and S3 via the first and third control clutches C-1 and C-3. Then, the ring gears R3, R4 are rotated via the carriers C3, C4 in accordance with the rotation of the first and second sun gears S3, S4, and the output shaft 18 is driven to rotate forward at a gear ratio of 1.778 at the fifth speed.

In the case of the sixth forward speed, the rotation of the small-diameter sun gear S2 is restricted by the operation of the first rotation control brake B-1, and the carriers C1 and C2 are switched to the first deceleration rotation state. When the clutches C-1 and C-3 are operated, the carriers C1, C2 and the second and first sun gears S4, S
3 is connected, the rotation input to the input shaft 15 is
The ring gears R1 and R2, the small-diameter sun gear S2 whose rotation is restricted to support the reaction force, are reduced to the first reduced rotation by the carriers C1 and C2, and the first and third control clutches C-1 and C-1 are rotated.
The gears are transmitted to the second and first sun gears S4 and S3 via C-3, and are transmitted via carriers C3 and C4 to ring gears R3 and R4.
Is rotated in accordance with the rotation of the first and second sun gears S3 and S4, and the output shaft 18 is driven to rotate normally at a gear ratio of 1.361 at the sixth speed.

In the case of the seventh forward speed, the rotation of the large-diameter sun gear S1 is restricted by the operation of the second rotation control brake B-2, and the carriers C1 and C2 are switched to the second reduced rotation state. The control clutches C-1 and C-2 are operated to connect the carriers C1 and C2 to the second sun gear S4, and the input shaft 15 to the carriers C3 and C4. , R2, a large-diameter sun gear S1 whose rotation is restricted to support a reaction force, is reduced to a second reduced rotation speed by carriers C1 and C2, and transmitted to a second sun gear S4 via a first control clutch C-1. , The carrier C via the second control clutch C-2.
3 and C4, the ring gears R3 and R4
The output shaft 18 rotates in accordance with the rotation difference between the sun gear S4 and the carriers C3 and C4, and drives the output shaft 18 in the forward direction at a gear ratio of 1.196 at the seventh speed.

In the case of the eighth forward speed, the rotation of the small-diameter sun gear S2 is restricted by the operation of the first rotation control brake B-1, and the carriers C1 and C2 are switched to the first reduced rotation state, and the first and second control steps are performed. The clutches C-1 and C-2 are operated to connect the carriers C1 and C2 to the second sun gear S4, and the input shaft 15 to the carriers C3 and C4. R2, a small-diameter sun gear S2 whose rotation is restricted to support the reaction force, is reduced to the first reduced rotation speed by the carriers C1 and C2, transmitted to the second sun gear S4 via the first control clutch C-1, and Carrier C via 2 control clutch C-2
3 and C4, the ring gears R3 and R4
The output shaft 18 rotates in accordance with the rotation difference between the sun gear S4 and the carriers C3 and C4, and drives the output shaft 18 in the forward direction at a gear ratio of 1.100 at the eighth speed.

In the case of the ninth forward speed, the first, second, and third control clutches C-1, C-2, and C-3 are connected, and the first and second sun gears S3 and S4 output the reduced rotation output. Connected via carriers C1 and C2 as member 55,
The first and second rotation control brakes B-1 and B-2 serving as the rotation state switching means 50 become inoperative, and the carriers C1 and C2 are deactivated.
2 is in a free rotation state, the rotation input to the input shaft 15 is directly transmitted to the carriers C3 and C4 of the dual gear planetary gear set 10 for transmission by the second control clutch C-2, and the integrated first rotation is performed. Then, the ring gears R3, R4 are rotated via the second sun gears S3, S4, and the output shaft 18 is driven to rotate forward at the ninth speed gear ratio 1.000.

In the case of the tenth forward speed, the rotation of the small-diameter sun gear S2 is restricted by the operation of the first rotation control brake B-1, and the carriers C1 and C2 are switched to the first reduced speed rotation state. The clutches C-3 and C-2 are operated to connect the carriers C1 and C2 to the first sun gear S3, and the input shaft 15 to the carriers C3 and C4. R2, a small-diameter sun gear S2 whose rotation is regulated to support the reaction force, is reduced to the first reduced rotation by the carriers C1 and C2, transmitted to the first sun gear S3 via the third control clutch C-3, and 2 is transmitted directly to the carriers C3 and C4 via the control clutch C-2, and rotates the ring gears R3 and R4 in accordance with the rotation difference between the first sun gear S3 and the carriers C3 and C4, and the output shaft 8 a gear ratio of the 10 shift speed 0.89
2 drives forward.

In the case of the eleventh forward speed, the rotation of the large-diameter sun gear S1 is restricted by the operation of the second rotation control brake B-2, and the carriers C1 and C2 are switched to the second reduced rotation state. Since the control clutches C-3 and C-2 are operated to connect the carriers C1 and C2 to the first sun gear S3 and the input shaft 15 to the carriers C3 and C4, the rotation input to the input shaft 15 is applied to the ring gear R1. , R2, a large-diameter sun gear S1 whose rotation is regulated to support a reaction force, reduced to a second reduced rotation by carriers C1 and C2, and transmitted to a first sun gear S3 via a third control clutch C-3. Is transmitted directly to the carriers C3 and C4 via the second control clutch C-2, and rotates the ring gears R3 and R4 in accordance with the rotation difference between the first sun gear S3 and the carriers C3 and C4, and the output shaft 8 a gear ratio 0.83 eleventh gear position
3 drives forward.

In the case of the twelfth forward speed, the second control clutch C-2 is operated and the input shaft 15 and the carriers C3 and C4 are actuated.
Is connected, the first control brake B-3 is operated, and the first
Since the rotation of the sun gear S3 is restricted, the rotation input to the input shaft 15 is transmitted to the carriers C3 and C4 via the second control clutch C-2, and a reaction force is applied to the first sun gear S3 whose rotation is restricted. The ring gears R3 and R4 are rotated while being supported, and the output shaft 18 is driven to rotate normally at a gear ratio of 0.686 at the twelfth speed.

In the case of the first reverse speed, the rotation of the large-diameter sun gear S1 is restricted by the operation of the second rotation control brake B-2, the carriers C1 and C2 are switched to the first reduced rotation state, and the third control clutch C -3 is activated and carrier C
1, C2 and the first sun gear S3 are connected, and the second control brake B-4 is operated to regulate the rotation of the carriers C1, C2. Therefore, the rotation input to the input shaft 15 is controlled by the ring gears R1, R2, The rotation is restricted to the large-diameter sun gear S1 that supports the reaction force and is reduced to the second reduced rotation by the carriers C1 and C2, transmitted to the first sun gear S3 via the third control clutch C-3, and the rotation is restricted. Carrier C3
With the reaction force supported by C4, the ring gears R3, R4 rotate in the reverse direction, and the output shaft 18 is driven to rotate in the reverse direction at the reverse first gear ratio of 3.879.

In the second reverse speed, the rotation of the small-diameter sun gear S2 is restricted by the operation of the first rotation control brake B-1, the carriers C1 and C2 are switched to the first reduced rotation state, and the third control clutch C- 3 is activated and carrier C
1, C2 and the first sun gear S3 are connected, and the second control brake B-4 is operated to regulate the rotation of the carriers C1, C2. Therefore, the rotation input to the input shaft 15 is controlled by the ring gears R1, R2, The rotation is restricted to a small-diameter sun gear S2 that supports the reaction force while being reduced, and is reduced to the first reduced rotation by the carriers C1 and C2, transmitted to the first sun gear S3 via the third control clutch C-3, and the rotation is restricted. Carrier C3
With the reaction force supported by C4, the ring gears R3 and R4 rotate in the reverse direction, and the output shaft 18 is driven to rotate in the reverse direction at the second reverse gear ratio of 2.970.

When the number of rotations of the ring gears R1 and R2 of the compound planetary gear unit 16 for reduction connected to the input shaft 15 is 1, the large diameter, small diameter, first and second sun gears S1 to S4, Carriers C1, C2 and C3, C4,
As is clear from the speed diagram of FIG. 3 showing the rotation ratios of the ring gears R1, R2 and R3, R4, the rotation ratios of the common ring gears R3, R4, that is, the gear ratios at each shift speed are arranged at appropriate intervals. According to the automatic transmission according to the present invention, it is possible to obtain a gear ratio of 12 forward gears and 2 reverse gears that are appropriately separated. Further, at any speed, any one of the sun gear, the carrier, and the ring gear does not rotate at an extremely high speed.

Next, a second embodiment will be described with reference to FIG. The second embodiment is different from the first embodiment in that the compound planetary gear unit 17 for shifting, the first to third clutches C-1 to C-3, the first and second control brakes B-3 and B-4, the one-way clutch F-1 and the like are provided. Is the same as that of the first embodiment, the same reference numerals are given to the drawings, and the description thereof will be omitted. Only the reduction compound planetary gear device 60 different from that of the first embodiment will be described.

The compound planetary gear device 60 for reduction includes sun gears S1 and S2 and a carrier C of a double pinion type planetary gear mechanism 65 and a single pinion type planetary gear mechanism 66.
1 and C2 are connected and shared. That is, a common sun gear S rotatably supported on the common axis 13
1, S2, the long pinion 62 meshing with the sun gears S1, S2, the long pinion 62 and the long pinion 6
A common carrier C rotatably supported on the common axis 13 and rotatably supporting an intermediate pinion 63 meshing with the second pinion 63.
1, C2, ring gears R2, R1 meshed with the long pinion 62 and the intermediate pinion 63 and rotatably supported on the common axis 13. The input shaft 15 is connected to the preceding ring gear R2.

The first and second rotation control brakes B-1 and B-2 for selectively restricting rotation by connecting the common sun gears S1 and S2 and the subsequent ring gear R1 to the transmission case 12 respectively are provided with sun gears S1 and S2. And the ring gear R1. Thus, the carriers C1 and C2 as the reduced rotation output members 55 are rotated at the first reduced rotation smaller than the rotation of the input shaft 15 because the rotation of the sun gears S1 and S2 is restricted by the first rotation control brake B-1. 1 deceleration rotation state, second deceleration rotation state in which the rotation of the ring gear R1 is restricted by the second rotation control brake B-2, and is rotated in a second deceleration rotation whose rotation speed is lower than the first deceleration rotation, first and second The rotation control brakes B-1 and B-2 are switched between a free rotation state in which the rotation is not restricted and the rotation is not restricted.

The compound planetary gear unit 60 for reduction has an input shaft 1
5 and a gear reduction device 49 for generating first and second reduced rotations having a lower rotation speed than the rotation of the input shaft 15, wherein the first and second rotation control brakes B- 1 and B- 2 are The rotation state switching means 50 for switching the carriers C1 and C2 as the reduced rotation output member 55 to the reduced rotation state or the free rotation state is configured.

Also in the second embodiment, the rotation of the input shaft 15 and the first and second reduced rotations generated on the carriers C1 and C2 of the planetary gear unit 60 for reduction are applied to the first to third control clutches C-1 to C-1. Double planetary gear set 17 for shifting by C-3
Second and first sun gears S4, S3 and common carrier C
3 and C4, and the rotation of the first sun gear S3 and the carriers C3 and C4 is controlled by the first and second control brakes B-
3, the input shaft 1 is selectively regulated by B-4.
Shifting the rotation of No. 5 to 12 forward steps and 2 reverse steps is the same as in the first embodiment, and a detailed description thereof will be omitted. FIG. 5 shows the operation state of each control clutch and control brake at each shift speed. In the second embodiment, the fourth gear and the fifth gear are located between the second gear and the third gear.
The operation states of the control brake and the control clutch between the gears are reverse to those in the first embodiment.

FIG. 5 shows a double planetary gear unit 6 for reduction.
The gear ratio λ1 of the first reduction gear planetary gear mechanism 65 including the sun gear S1, the long pinion 62, the intermediate pinion 63, the carrier C1, and the ring gear R1 is 0.273, and the sun gear S2, the long pinion 62, the carrier C2, and the ring gear R2. The gear ratio λ2 of the second planetary gear mechanism 66 for reduction is 0.391, and the first planetary gear mechanism 53 for transmission comprising the first sun gear S3, the long pinion 34, the carrier C3 and the ring gear R3 of the double planetary gear train 17 for transmission.
In the case where the gear ratio λ3 of the second planetary gear mechanism 54 for shifting composed of the gear ratio λ3 of 0.556, the second sun gear S4, the intermediate pinion 33, the long pinion 34, the carrier C4, and the ring gear R4 is 0.417. The gear ratio (the number of rotations of the input shaft 15 / the number of rotations of the output shaft 18) at the speed is shown in the gear ratio column.

The velocity diagram of the second embodiment is as shown in FIG. Also in the second embodiment, the first sun gear S3 as the first element is connected to the third control clutch C-3 and the first control brake B-3, and the carriers C3 and C4 as the second elements are connected to the second control clutch. Ring gear R as a third element, which is connected to C-2 and the second control brake B-4.
3, R4 is connected to the output shaft 18, and the second sun gear S4 as a fourth element is connected to the first control clutch C-1.

Next, an embodiment in which a single planetary gear device is used as the gear reduction device will be described. The third embodiment is different from the first embodiment in that the compound planetary gear device 17 for shifting, the first to third clutches C-1 to C-3, the first and second control brakes B-3, B
-4 and one-way clutch F-1 etc.
7, the same reference numerals are given to FIG. 7 and the description is omitted, and the reduction planetary gear device 70, the reduction planetary gear device 70, and the transmission double planetary gear device 17 different from the first embodiment are described. Will be described.

The planetary gear unit 70 for reduction has a common axis 13
Sun gear S2 rotatably supported above, sun gear S2
And a carrier C2 rotatably supported on the common axis 13 and rotatably supported on the common axis 13, and a ring gear R2 meshed with the pinion 71 and rotatably supported on the common axis 13. ing. The input shaft 15 is connected to the ring gear R2. A rotation control clutch C-4 selectively connects the carrier C2 to the ring gear R2, and a rotation control brake B-2 selectively restricts rotation of the sun gear S2. As a result, the carrier C2 as the reduced rotation output member 55 is connected to the ring gear R2 by the rotation control clutch C-4, and is rotated at the same number of rotations as the input shaft 15 in the input rotation state, the rotation control brake B-2. The rotation of the sun gear S2 is restricted by the rotation of the input shaft 15, and the rotation of the input shaft 15 is reduced.
-4, switching between a free rotation state in which the rotation control brake B-2 is inoperative and rotation is not restricted.

The reduction planetary gear unit 70 is connected to the input shaft 15 and generates an input rotation having the same rotation speed as the rotation of the input shaft 15 and a reduced speed rotation having a lower rotation speed than the rotation of the input shaft 15. And the rotation control clutch C
-4 and the rotation control brake B-2 constitute rotation state switching means 50 for switching the carrier C2 as the reduced rotation output member 55 to the reduced rotation state or the free rotation state.

In the third embodiment configured as described above, the first to third control clutches C-1 to C-3 and the rotation control clutch C-4 are selectively engaged and disengaged, and the first and second control clutches C-1 to C-3 are selectively disengaged. By selectively operating the brakes B-3 and B-4 and the rotation control brake B-2 to restrict the rotation of the element members of the planetary gear set, a gear ratio of nine forward gears and two reverse gears is established. Can be.

FIG. 8 shows the operating state of each control clutch and control brake at each shift speed. FIG. 8 shows that the gear ratio λ2 of the planetary gear unit 70 for reduction is 0.417, the first sun gear S3 of the compound planetary gear unit 17 for shifting, and the long pinion 3
4, the gear ratio λ3 of the first speed change planetary gear mechanism 53 including the carrier C3 and the ring gear R3 is 0.458, the second sun gear S4, the intermediate pinion 33, the long pinion 34,
When the gear ratio λ4 of the second speed-changing planetary gear mechanism 54 including the carrier C4 and the ring gear R4 is 0.375, the gear ratio at each shift speed (the rotational speed of the input shaft 15 /
The number of revolutions of the output shaft 18 is shown in the gear ratio column.

The velocity diagram of the third embodiment is as shown in FIG. Also in the third embodiment, the first sun gear S3 as the first element is connected to the third control clutch C-3 and the first control brake B-3, and the carriers C3 and C4 as the second elements are connected to the second control clutch. Ring gear R as a third element, which is connected to C-2 and the second control brake B-4.
3, R4 is connected to the output shaft 18, and the second sun gear S4 as a fourth element is connected to the first control clutch C-1.

Hereinafter, the operation of each shift speed will be described.
In the case of the first forward speed, the rotation of the sun gear S2 is restricted by the operation of the rotation control brake B-2 constituting the rotation state switching means 50, and the carrier C2 as the reduced rotation output member 55 is switched to the reduced rotation state. 1 The control clutch C-1 is operated to connect the carrier C2 and the second sun gear S4, and the one-way clutch F-1 is operated to restrict reverse rotation of the carriers C3 and C4. Is reduced to a reduced rotation by a ring gear R2, a sun gear S2 whose rotation is regulated to support a reaction force, and a carrier C2, and a reverse rotation is regulated by a first control clutch C-1, a second sun gear S4, and a one-way clutch F-1. Ring carrier R via carriers C3 and C4 supporting the reaction force
3, the output shaft 18 is driven forward at a gear ratio of 3.778 at the first speed. The second control brake B
-4 may be operated to regulate the rotation of the carriers C3 and C4.

In the case of the second forward speed, the carrier C2 is connected to the ring gear R2 by the operation of the rotation control clutch C-4 constituting the rotation state switching means 50, and is brought into an input rotation state in which the carrier C2 rotates integrally with the input shaft 15. The first control clutch C-1 is operated, the carrier C2 and the second sun gear S4 are connected, and the one-way clutch F-1 is operated to restrict the reverse rotation of the carriers C3 and C4. The input rotation is directly transmitted as input rotation to the carrier C2 by the rotation control clutch C-4,
The reverse rotation is regulated by the control clutch C-1, the second sun gear S4, and the one-way clutch F-1 and transmitted to the ring gears R3 and R4 via the carriers C3 and C4 that support the reaction force, and the output shaft 18 is moved to the second gear. Is driven forward at a gear ratio of 2.667.

In the case of the third forward speed, the rotation of the sun gear S2 is restricted by the operation of the rotation control brake B-2, the carrier C2 is switched to the reduced rotation state, and the first control clutch C-1 is operated to activate the carrier C2. And the second sun gear S
4 is connected, the first control brake B-3 is operated, and the rotation of the first sun gear S3 is regulated, so that the rotation inputted to the input shaft 15 is restricted by the ring gear R2 and the rotation to support the reaction force. The sun gear S2 and the carrier C2 reduce the speed to the reduced speed, the first control clutch C-1, the second sun gear S4, and the first sun gear S whose rotation is regulated to support the reaction force.
3. Ring gears R3, R4 via carriers C3, C4
And the output shaft 18 is shifted to the third gear ratio 2.15.
In step 9, the motor is driven to rotate forward.

In the case of the fourth forward speed, the carrier C2 is connected to the ring gear R2 by the operation of the rotation control clutch C-4 and is switched to an input rotation state in which the carrier C2 rotates integrally with the input shaft 15, and the first control clutch C-4 -1 is actuated, the carrier C2 is connected to the second sun gear S4, and the first control brake B-3 is actuated to restrict the rotation of the first sun gear S3. The input rotation is directly transmitted to the carrier C2 and is transmitted to the ring gears R3 and R4 via the first control clutch C-1, the second sun gear S4, the first sun gear S3 whose rotation is restricted to support the reaction force, and the carriers C3 and C4. The output shaft 18 is
The motor is driven to rotate normally at a gear ratio of 1.524.

In the case of the fifth forward speed, the rotation of the sun gear S2 is restricted by the operation of the rotation control brake B-2, the carrier C2 is switched to the reduced rotation state, and the first and third control clutches C-1, C- 3, the carrier C2 is connected to the second and first sun gears S4 and S3, so that the rotation input to the input shaft 15 is applied to the ring gear R2, the sun gear S2 whose rotation is regulated to support the reaction force, and the carrier. C2, the first and third control clutches C
-1, C-3 to the second and first sun gears S4, S3, and the ring gear R via the carriers C3, C4.
3, R4 is rotated in accordance with the rotation of the first and second sun gears S3, S4, and the output shaft 18 is shifted to the fifth gear ratio 1.41.
7 to drive forward.

In the case of the sixth forward speed, the rotation of the sun gear S2 is restricted by the operation of the rotation control brake B-2, the carrier C2 is switched to the reduced rotation state, and the first and second control clutches C-1, C-C are switched. 2, the carrier C2 is connected to the second sun gear S4, and the input shaft 15 is connected to the carriers C3, C4. The sun gear S2 and the carrier C2 reduce the speed to a reduced speed.
The power is transmitted to the second sun gear S4 via the control clutch C-1 and is also directly transmitted to the carriers C3 and C4 via the second control clutch C-2. The output shaft 18 is rotated in accordance with the rotation difference of C4 to set the output shaft 18 to a gear ratio of 1.124 at the sixth speed.
To drive forward.

In the case of the seventh forward speed, the first, second and third control clutches C-1, C-2 and C-3 are connected, and the first and second sun gears S3 and S4 output the reduced rotation output. Since the rotation control clutch C-4 and the rotation control brake B-2 as the rotation state switching means 50 are inoperable and the carrier C2 is in a free rotation state, the input shaft 15 is connected. Is directly transmitted to the carriers C3 and C4 of the dual gear transmission 10 by the second control clutch C-2, and is integrated with the ring gear R3 via the first and second sun gears S3 and S4. , R4 to rotate the output shaft 18 forward at a gear ratio of 1.000 at the ninth speed.

In the case of the eighth forward speed, the rotation of the sun gear S2 is restricted by the operation of the rotation control brake B-2, the carrier C2 is switched to the reduced rotation state, and the third and second control clutches C-3, C- 2, the carrier C2 is connected to the first sun gear S3, and the input shaft 15 is connected to the carriers C3, C4. Sun gear S2 and the carrier C2 reduce the speed to a reduced speed.
The power is transmitted to the first sun gear S3 via the control clutch C-3, and is also directly transmitted to the carriers C3 and C4 via the second control clutch C-2. The output shaft 18 is rotated according to the rotation difference of C4, and the output shaft 18 is shifted to a gear ratio of 0.881 at the eighth speed.
To drive forward.

In the case of the ninth forward speed, the second control clutch C-2 is operated to connect the input shaft 15 to the carriers C3 and C4, and the first control brake B-3 is operated to operate the first control brake B-3.
Since the rotation of the sun gear S3 is restricted, the rotation input to the input shaft 15 is transmitted to the carriers C3 and C4 via the second control clutch C-2, and a reaction force is applied to the first sun gear S3 whose rotation is restricted. The ring gears R3 and R4 are rotated while being supported, and the output shaft 18 is driven to rotate normally at a gear ratio of 0.686 at the ninth speed.

In the case of the first reverse speed, the rotation of the sun gear S2 is restricted by the operation of the rotation control brake B-2, the carrier C2 is switched to the reduced rotation state, and the third control clutch C-3 is operated to activate the carrier C2. And the first sun gear S
3 is connected, the second control brake B-4 is operated, and the rotation of the carriers C3 and C4 is restricted.
Is reduced to reduced rotation by the ring gear R2, the sun gear S2 whose rotation is restricted and supports the reaction force, and the carrier C2, and is transmitted to the first sun gear S3 via the third control clutch C-3. The reaction force is supported by the carriers C3 and C4 whose rotation is restricted, the ring gears R3 and R4 are reversed, and the output shaft 18 is moved backward to the first gear ratio of 3.09.
1 drives in reverse.

In the case of the second reverse speed, the carrier C2 is connected to the ring gear R2 by the operation of the rotation control clutch C-4 to switch to the input rotation state in which the carrier C2 rotates integrally with the input shaft 15, and the third control clutch C-4 -3 is operated to connect the carrier C2 and the first sun gear S3, and the second control brake B-4 is operated to regulate the rotation of the carriers C3 and C4. The ring gears R3, R4 are transmitted directly to the carrier C2, transmitted to the first sun gear S3 by the third control clutch C-3, and supported by the carriers C3, C4 whose rotation is restricted to support the reaction force.
4 is reversed, and the output shaft 18 is moved backward to the second gear ratio.
At 182, reverse drive is performed.

In the third embodiment, the reduction planetary gear train 7
0, the rotation of the sun gear S2 is regulated by the rotation control brake B-2 to generate a reduced rotation of the carrier C2 at a lower rotational speed than the rotation of the input shaft 15, and the carrier C2 is connected to the ring gear R2.
Connected to the carrier C2 by the rotation control clutch C-4.
The input rotation of the same speed as that of the input shaft 15 is generated, but the deceleration rotation is similarly generated by restricting the rotation of the sun gear S2, and the input rotation is generated by the carrier C2 as shown in FIGS. A rotation control clutch C-4 may be used to connect and disconnect between the sun gear S2 and the ring gear R2 and the sun gear S2. In this case, the speed diagram of the compound planetary gear unit 17 for shifting and the operating states of the control brake and the control clutch at each shift speed are the same as those in the third embodiment.

Fourth and fifth embodiments in which a single planetary gear device in which the rotation of a sun gear is restricted are used for a reduction planetary gear device will be described with reference to FIGS. 12, the reduction planetary gear set 72 includes a sun gear S2 whose rotation is restricted, a carrier C2 that supports a pinion 73 that meshes with the sun gear S2, and a ring gear R2 that meshes with the pinion 73. The input shaft 15 is a ring gear R
2 are connected. Accordingly, a second rotation having a lower rotation speed than the rotation of the input shaft 15 is generated on the carrier C2, and a first rotation having the same rotation speed as the rotation of the input shaft 15 is generated on the ring gear R2.
A rotation is generated.

Reference numeral 74 denotes a connecting member rotatably provided on the common axis 13. The connecting member 74 is connected to the second and first sun gears S by the first and third control clutches C-1 and C-3.
4 and S3 so as to be detachably connected to each other, and to be detachably connected to the ring gear R2 and the carrier C2 by first and second rotation control clutches C-4 and C-5. Accordingly, the connecting member 74 as the reduced rotation output member 55 is
An input rotation state in which the first rotation control clutch C-4 is connected to the ring gear R2 and is rotated at the same rotation speed as the input shaft 15 in the input rotation state. A deceleration rotation state in which the rotation speed is smaller than the rotation speed of the rotation number 15;
The rotation control clutches C-4 and C-5 are switched to a free rotation state in which the rotation is not restricted and the rotation is not restricted.

Reduction planetary gear set 72 and connecting member 74
Constitutes a gear reduction device 49 connected to the input shaft 15 for generating an input rotation having a rotation speed equal to the rotation of the input shaft 15 and a reduced rotation having a rotation speed smaller than the rotation of the input shaft 15. The rotation control clutches C-4 and C-5 constitute a rotation state switching unit 50 that switches the connection member 74 as the reduced rotation output member 55 to the reduced rotation state or the free rotation state.

The operation state of the control brake and the control clutch at each shift speed is determined by the second rotation control brake B-
If the second rotation control clutch C-5 is operated instead of 2, the operation is the same as that of the third embodiment. The speed diagram of the compound planetary gear unit 17 for shifting is the same as that of the third embodiment.

In FIG. 13, the planetary gear unit 72 for reduction
Is composed of a sun gear S2 whose rotation is restricted, a carrier C2 that supports a pinion 73 that meshes with the sun gear S2, and a ring gear R2 that meshes with the pinion 73.
First and third control clutches C-1 and C-3 are provided between the carrier C2 and the second and first sun gears S4 and S3, and a first rotation control clutch C is provided between the input shaft 15 and the carrier C2. -4, a second rotation control clutch C-5 is provided between the input shaft 15 and the ring gear R2. As a result, the carrier C2 as the reduced rotation output member 55 is connected to the input shaft 1 by the first rotation control clutch C-4.
5, the input shaft 15 is connected to the ring gear R2 by the second rotation control clutch C-5.
5, the first and second rotation control clutches C-4 and C-5.
Is switched to a free rotation state in which rotation is not restricted due to inactivity.

The planetary gear unit 72 for reduction is connected to the input shaft 15 and generates a first rotation having the same rotation speed as the rotation of the input shaft 15 and a reduction rotation having a lower rotation speed than the rotation of the input shaft 15. 49, and the first and second rotation control clutches C-4 and C-5 form a rotation state switching means 50 for switching the carrier C2 as the reduced rotation output member 55 to a reduced rotation state or a free rotation state. in this case,
The operating states of the control brake and the control clutch at each shift speed are the same as those of the third embodiment if the second rotation control clutch C-5 is operated instead of the second rotation control brake B-2. The speed diagram of the compound planetary gear unit 17 for shifting is the same as that of the third embodiment.

Next, another embodiment in which a single planetary gear device is used as the gear reduction device will be described. Since the sixth embodiment has a configuration in which the rotation control clutch C-4 is removed from the third embodiment, the same reference numerals are given to the components corresponding to the third embodiment in FIG. 14, and detailed description of the configuration will be omitted.
In this case, the carrier C2 as the reduced rotation output member 55
Is a decelerated rotation state in which the rotation of the sun gear S2 is regulated by the rotation control brake B-2 and the input shaft 15 is rotated at a reduced rotation speed smaller than the rotation speed of the input shaft 15, and the rotation control brake B-
2 is switched between a non-operating and unrestricted free rotation state.

The reduction planetary gear device 70 is connected to the input shaft 15 and constitutes a gear reduction device 49 for generating a reduced rotation at a lower rotation speed than the rotation of the input shaft 15. The rotation state switching means 50 for switching the carrier C2 as the rotation output member 55 to the reduced rotation state or the free rotation state is configured.

As shown in FIG. 15, the operation state of the control clutch and the control brake at each shift speed is the same as that of the third embodiment shown in FIG.
4 is the same as that in which the operating speed stages 2nd, 4th, and Rev2 are removed and the speed stages are renumbered in order from the top, and the reduction planetary gear device 70 at each speed stage.
The operation of the planetary gear device 17 for shifting is also the same as that of the corresponding shift speed of the third embodiment except for the gear ratio at each shift speed, and thus the description thereof is omitted. Regarding the gear ratio at each shift speed, the gear ratio λ2 of the planetary gear device 70 for reduction is set to 0.
556, first sun gear S of double planetary gear train 17 for shifting
3, the gear ratio λ3 of the first speed-changing planetary gear mechanism 53 including the long pinion 34, the carrier C3, and the ring gear R3.
Is 0.458, the second sun gear S4, the intermediate pinion 33,
Long pinion 34, carrier C4 and ring gear R4
The case where the gear ratio λ4 of the second speed change planetary gear mechanism 54 is 0.375 is shown in the gear ratio column of FIG.

The velocity diagram of the sixth embodiment is as shown in FIG. Also in the sixth embodiment, the first sun gear S3 as the first element is connected to the third control clutch C-3 and the first control brake B-3, and the carriers C3 and C4 as the second elements are connected to the second control clutch. C-2 and the second control brake B-4, the ring gears R3 and R4 as the third element are connected to the output shaft 18, and the second sun gear S4 as the fourth element is connected to the first control clutch C-1. Are linked.

Next, the seventh and eighth embodiments in which a single planetary gear unit in which the rotation of the sun gear is restricted are used for a reduction planetary gear unit.
An embodiment will be described with reference to FIGS. The seventh embodiment is different from the fourth embodiment in that the first rotation control clutch C-
4, the same reference numerals are given to components corresponding to those in the seventh embodiment in FIG. 17, and detailed description of the configuration will be omitted. In this case, the connection member 74 as the reduced rotation output member 55 is connected to the carrier C by the rotation control clutch C-5.
2, a rotation control clutch C in a decelerated rotation state in which the input shaft 15 is rotated at a deceleration speed lower than the rotation speed of the input shaft 15.
-5 is switched between an inactive and unrestricted free rotation state.

Reduction planetary gear set 72 and connecting member 74
Constitutes a gear reduction device 49 that is connected to the input shaft 15 and generates a reduced rotation at a lower rotation speed than the rotation of the input shaft 15. The rotation control clutch C-5 includes a reduced rotation output member 55.
The rotation state switching means 50 for switching the connection member 74 as the rotation state to the reduced rotation state or the free rotation state is configured. The operating states of the control clutch and the control brake at each shift speed are the same as those in the sixth embodiment if the rotation control clutch C-5 is operated instead of the rotation control brake B-2. The speed diagram of the double planetary gear unit 17 for shifting is the same as that of the sixth embodiment.

Since the eighth embodiment has a configuration in which the first rotation control clutch C-4 is removed from the fifth embodiment, the components corresponding to those of the fifth embodiment are given the same reference numerals in FIG. Description is omitted. In this case, the carrier C2 as the reduced rotation output member 55 has a reduced rotation state in which the ring gear R2 is connected to the input shaft 15 by the rotation control clutch C-5 and is rotated at a reduced rotation speed smaller than the rotation speed of the input shaft 15. Is switched between a free rotation state in which the rotation control clutch C-5 is inoperative and the rotation is not restricted.

The planetary gear device 72 for reduction is connected to the input shaft 15 to constitute a gear reduction device 49 for generating a reduced rotation having a lower rotation speed than the rotation of the input shaft 15. The rotation state switching means 50 for switching the carrier C2 as the rotation output member 55 to the reduced rotation state or the free rotation state is configured. The operating states of the control clutch and the control brake at each shift speed are the same as those in the sixth embodiment if the rotation control clutch C-5 is operated instead of the rotation control brake B-2. The speed diagram of the double planetary gear unit 17 for shifting is the same as that of the sixth embodiment.

Next, a ninth embodiment in which the gear reduction device 49 is constituted by a reduction gear train will be described. The ninth embodiment is different from the first embodiment in that the compound planetary gear unit 17 for shifting, the first to third control clutches C-1 to C-3, the first and second control brakes B-
3, B-4, one-way clutch F-1 and the like are the same as those in the first embodiment. The connection relationship between the speed reduction gear train 75 and the speed change compound planetary gear device 17 will be described. Automatic transmission 1
The turbine 47 of the fluid torque converter 11 is connected to an input shaft 76 that is rotatably supported by the transmission case 12, and large-, medium-, and small-diameter gears 77, 78, and 79 are fixed to the input shaft 76. . Large diameter gear 77
The first and second gears 80 having the same diameter meshing with the first and second gears 8 are rotatably supported on the axis 21 of the double planetary gear set 17 for shifting, and mesh with the middle and small diameter gears 78 and 79, respectively.
1, 82 are rotatably mounted on the axis 21. As a result, the first gear 80 rotates at the input rotation having the same rotation speed as the rotation of the input shaft 76, the second gear 81 rotates at the first reduced rotation whose rotation speed is smaller than the input rotation, and the third gear 82 rotates at the first rotation.
The motor rotates at a second reduced rotation speed lower than the rotation speed.

Reference numeral 83 denotes a connecting member rotatably provided on the axis 21. The connecting member 83 is connected to the second and first sun gears S4 and S3 by the first and third control clutches C-1 and C-3.
3 and is detachably connected to the second and third gears 81 and 82 by the first and second rotation control clutches C-4 and C-5. As a result, the connecting member 83 as the reduced rotation output member 55 is connected to the second gear by the first rotation control clutch C-4, and is rotated at the first reduced rotation having a lower rotation speed than the input rotation. , The third gear 8 by the second rotation control clutch C-5.
2, a second reduced rotation state in which the rotation speed is lower than the first reduced rotation speed in the second reduced rotation speed, and the first and second rotation control clutches C-4 and C-5 are inoperative and the rotation is restricted. It can be switched between the free rotation state and the free rotation state.

The reduction gear train 75 and the connecting member 83 are connected to the input shaft 76 to perform a first reduced rotation having a smaller rotation speed than the rotation of the input shaft 76 and a second reduced rotation having a smaller rotation speed than the first reduced rotation. The first and second rotation control clutches C-4 and C-5 constitute a gear reduction device 49 that generates the rotation, and the rotation state switching that switches the coupling member 74 as the reduced rotation output member 55 to the reduced rotation state or the free rotation state. The means 50 is constituted. The operation states of the control brake and the control clutch at each shift speed are determined by the first and second rotation control brakes B-
1, B-2 instead of the first and second rotation control clutches C-
Activating 4, C-5 is the same as in the first embodiment. The speed diagram of the compound planetary gear unit 17 for shifting is the same as that of the first embodiment.

In the ninth embodiment, the reduction gear train 75 is composed of large, medium, and small diameter gears 77 to 79 and first to third gears 80 to 82 meshing with these gears, respectively.
, The small-diameter gear 79 and the third gear 82 may be removed. In the tenth embodiment, the first gear 80 rotates with the input rotation having the same rotation speed as the rotation of the input shaft 76, and the second gear 81 rotates with the reduced rotation whose rotation speed is smaller than the input rotation. The connecting member 83 includes first and second sun gears S3 and S
4 is connected to the first and second control clutches C-3 and C-1 in a detachable manner, and the second gear 81 and the rotation control clutch C-
The connection 5 is detachably connected. As a result, the connecting member 83 serving as the reduced rotation output member 55 is connected to the second gear 81 by the rotation control clutch C-5, and is rotated at a reduced rotation speed smaller than the rotation speed of the input shaft 76. The state is switched between a free rotation state in which the control clutch C-5 is inoperative and the rotation is not restricted.

The reduction gear train 75 and the connecting member 83 are connected to the input shaft 76 to generate an input rotation having the same rotation speed as the rotation of the input shaft 76 and a reduction gear 49 for generating a reduced rotation having a smaller rotation speed than the input rotation. And the rotation control clutch C
Reference numeral -5 denotes a rotation state switching unit 50 that switches the connection member 83 as the reduced rotation output member 55 to the reduced rotation state or the free rotation state. The operating states of the control clutch and the control brake at each shift speed are the same as those in the sixth embodiment if the rotation control clutch C-5 is operated instead of the rotation control brake B-2. The speed diagram of the double planetary gear unit 17 for shifting is the same as that of the sixth embodiment.

Next, another embodiment in which the same single planetary gear device as that of the third embodiment is used for the gear reduction device 49 and the double planetary gear device 17 for shifting is constituted by a compound planetary gear device different from that of the above embodiment. An embodiment will be described. Since the reduction planetary gear device 70 is the same as that of the third embodiment, the same reference numerals are given to the drawings and the description is omitted.

As shown in FIG. 21, the double gear planetary gear train 84 of the eleventh embodiment has a double pinion type planetary gear mechanism 93 and a single pinion type planetary gear mechanism 9.
4 and the sun gear S4, and the ring gear R3 and the carrier C4. That is, the sun gear S rotatably supported on the common axis 13.
3, S4, pinion 86 meshing with sun gear S3 via intermediate pinion 85, pinion 86 and intermediate pinion 8
5, a carrier C3 connected to the sun gear S4 and rotatably supported on the common axis 13, a ring gear R3 rotatably supported on the common axis 13 and meshing with the pinion 86, a pinion 87 meshing with the sun gear S4, The pinion 87 is supported, is connected to the ring gear R3, and
Carrier C4 rotatably supported on top, common axis 13
The ring gear R4 is rotatably supported above and meshes with the pinion 87. The output shaft 18 is connected to the ring gear R4. The carrier C3 connected to the sun gear S4 is connected to a first control brake B-3 for selectively connecting the sun gear S4 and the carrier C3 to the transmission case 12 to restrict rotation.
3 is connected to a second control brake B-4 that selectively connects the ring gear R3 and the carrier C4 to the transmission case 12 to restrict rotation.

The first and third control clutches C-1 and C-3 for selectively transmitting the rotation of the carrier C2 of the reduction planetary gear set 70 to the sun gear S3 and the carrier C3 of the double transmission planetary gear set 84, respectively. And a second control clutch C-2 for selectively transmitting the rotation of the input shaft 15 to the carrier C4. Then, as in the case of the third embodiment, the rotation control clutch C-4 selectively connects the carrier C2 of the reduction planetary gear device 70 to the ring gear R2, and the rotation control brake B-2 controls the rotation of the sun gear S2. The carrier C2 as the deceleration rotation output member 55
Is an input rotation state in which the input shaft is connected to the ring gear R2 by the rotation control clutch C-4 and is rotated at the same rotation speed as the input shaft 15; the rotation of the sun gear S2 is restricted by the rotation control brake B-2; Switching is made between a decelerating rotation state in which the rotation speed is smaller than the rotation speed of 15 and a free rotation state in which the rotation control clutch C-4 and the rotation control brake B-2 are inoperative and the rotation is not restricted.

In the eleventh embodiment configured as described above, the first and second control brakes B-3 and B-4, the first to third control clutches C-1 to C-3, and the rotation control clutch C
-4 and the rotation control brake B-2 are selectively operated, so that a gear ratio of nine forward speeds and two reverse speeds can be established. The velocity diagram of the eleventh embodiment is as shown in FIG. In the eleventh embodiment, the sun gear S4 and the carrier C3 as the first elements are connected to the third control clutch C
-3 and the first control brake B-3, the ring gear R3 and the carrier C4 as the second elements are connected to the second control clutch C-2 and the second control brake B-4,
The ring gear R4 as the third element is connected to the output shaft 18, and the sun gear S3 as the fourth element is connected to the first control clutch C-1. The operation state of each control clutch and control brake at each shift speed is the same as that of the third embodiment shown in FIG.

As shown in FIG. 23, the double gear planetary gear set 88 for shifting according to the twelfth embodiment connects the sun gears S3 and S4 of the two sets of double pinion type planetary gear mechanisms 31 and 32, and connects the ring gear R3 and the carrier. And C4. That is, the sun gears S3, S4 and the sun gear S3 rotatably supported on the common axis 13 and connected to each other.
, A pinion 90 meshing with an intermediate pinion 89, a pinion 92 meshing with the sun gear S4 via an intermediate pinion 91, a carrier C3 rotatably supported on the common axis 13 by supporting the intermediate pinion 89 and the pinion 90,
The intermediate pinion 91 and the pinion 92 are supported and connected to the ring gear R3 and rotatably supported on the common axis 13 and the carrier C4 rotatably supported on the common axis 13 and engaged with the pinion 92 and connected to the output shaft 18. And a ring gear R4. A first control brake B-3 for selectively rotating the carrier C3 to the transmission case 12 to restrict rotation is connected to the carrier C3, and the carrier C4 is selectively connected to the transmission case 12 for the carrier C4. The second control brake B-4 for restricting rotation by the rotation is connected. First and third control clutches C-1 and C- for selectively transmitting the rotation of the carrier C2 of the reduction planetary gear set 70 to the sun gears S3 and S4 and the carrier C3 of the double transmission planetary gear set 88, respectively.
3 and a double planetary gear train 88 for shifting the rotation of the input shaft 15
Control clutch C that selectively transmits to carrier C4
-2 is provided. Then, as in the third embodiment, the rotation control clutch C-4 selectively connects the carrier C2 of the reduction planetary gear device 70 to the ring gear R2, and the rotation control brake B-2 controls the rotation of the sun gear S2. Since the carrier C2 is selectively regulated, the carrier C2 as the reduced rotation output member 55 is connected to the ring gear R2 by the rotation control clutch C-4, and is rotated at the same rotation speed as the input shaft 15 in the input rotation state. The rotation of the sun gear S2 is regulated by the control brake B-2, and the rotation of the sun gear S2 is reduced at a reduced rotation speed smaller than the rotation speed of the input shaft 15, the rotation control clutch C-4, and the rotation control brake B-2.
Is switched to a free rotation state in which rotation is not restricted due to inactivity.

The velocity diagram of the twelfth embodiment is as shown in FIG. In the twelfth embodiment, the carrier C3 as the first element is connected to the third control clutch C-3 and the first control brake B-3, and the ring gear R3 and the carrier C4 as the second element are connected to the second control clutch C-3. -2 and the second control brake B-4, the ring gear R4 as the third element is connected to the output shaft 18, and the second sun gears S3 and S4 as the fourth element are connected to the first clutch C-1. I have. The operation state of each control clutch and control brake at each shift speed is the same as that of the third embodiment shown in FIG.

As shown in FIG. 25, the double gear planetary gear train 95 of the thirteenth embodiment comprises a single pinion type planetary gear mechanism 98 and a double pinion type planetary gear mechanism 9.
Nine sun gears S3, S4 and carriers C3, C4 are connected and shared. That is, the common axis 1
3, the sun gears S3, S4 rotatably supported on the common axis 3, and the sun gears S3, S rotatably supported on the common axis 13.
4 and a ring gear R meshing via a long pinion 96
3. The sun gear S rotatably supported on the common axis 13
The ring gear R4 meshes with S3, S4 via the long pinion 96 and the intermediate pinion 97, and the common carrier C3, C4 rotatably supported on the common axis 13 by supporting the long pinion 96 and the intermediate pinion 97. ing. The output shaft 18 is connected to the ring gear R4. A first control brake B-3 for selectively connecting the ring gear R3 to the transmission case 12 to restrict rotation is connected to the ring gear R3.
4 is connected to a second control brake B-4 for selectively connecting the carriers C3 and C4 to the transmission case 12 to restrict rotation. Planetary gear set 70 for reduction
, The first and third control clutches C-1, C-3 for selectively transmitting the rotation of the carrier C2 to the sun gears S3, S4 and the ring gear R3 of the transmission compound planetary gear set 95, respectively, and the rotation of the input shaft 15. Control clutch C- for selectively transmitting the power to the carriers C3 and C4 of the compound planetary gear device 95 for shifting.
2 are provided. Then, as in the third embodiment, the rotation control clutch C-4 selectively connects the carrier C2 of the reduction planetary gear device 70 to the ring gear R2, and the rotation control brake B-2 controls the rotation of the sun gear S2. Since the carrier C2 is selectively regulated, the carrier C2 as the reduced rotation output member 55 is connected to the ring gear R2 by the rotation control clutch C-4, and is rotated at the same rotation speed as the input shaft 15 in the input rotation state. The rotation of the sun gear S2 is regulated by the control brake B-2, and the rotation of the sun gear S2 is reduced at a reduced rotation speed smaller than the rotation speed of the input shaft 15, the rotation control clutch C-4, and the rotation control brake B-2.
Is switched to a free rotation state in which rotation is not restricted due to inactivity.

The velocity diagram of the thirteenth embodiment is as shown in FIG. In the thirteenth embodiment, the ring gear R3 as the first element is connected to the third clutch C-3 and the second control brake B-3, and the carriers C3 and C4 as the second elements are connected to the second clutch C-2 and The ring gear R4 is connected to the output shaft 18 as a third element, and is connected to the second control brake B-4.
S4 is connected to the first clutch C-1. The operation state of each control clutch and control brake at each shift speed is the same as that of the third embodiment shown in FIG.

[Brief description of the drawings]

FIG. 1 is a skeleton diagram showing a first embodiment of an automatic transmission according to the present invention.

FIG. 2 is a diagram illustrating an operation state of a control brake and a control clutch at each shift speed according to the first embodiment.

FIG. 3 is a velocity diagram showing a rotation ratio of each element of the planetary gear device at each shift speed of the first embodiment.

FIG. 4 is a skeleton diagram showing a second embodiment.

FIG. 5 is a diagram illustrating an operation state of a control brake and a control clutch at each shift speed according to a second embodiment.

FIG. 6 is a velocity diagram showing a rotation ratio of each element of the planetary gear device at each shift speed of the second embodiment.

FIG. 7 is a skeleton diagram showing a third embodiment.

FIG. 8 is a diagram illustrating an operation state of a control brake and a control clutch at each shift speed according to a third embodiment.

FIG. 9 is a velocity diagram showing a rotation ratio of each element of the planetary gear device at each shift speed of the third embodiment.

FIG. 10 is a view showing that a first rotation control clutch is connected between a sun gear and a carrier of the planetary gear device for reduction.

FIG. 11 is a diagram showing that a first rotation control clutch is connected between a sun gear and a ring gear of the planetary gear device for reduction.

FIG. 12 is a skeleton diagram showing a fourth embodiment.

FIG. 13 is a skeleton diagram showing a fifth embodiment.

FIG. 14 is a skeleton diagram showing a sixth embodiment.

FIG. 15 is a diagram showing operating states of a control brake and a control clutch at each shift speed according to a sixth embodiment.

FIG. 16 is a velocity diagram showing a rotation ratio of each element of the planetary gear device at each shift speed of the sixth embodiment.

FIG. 17 is a skeleton diagram showing a seventh embodiment.

FIG. 18 is a skeleton diagram showing an eighth embodiment.

FIG. 19 is a skeleton diagram showing a ninth embodiment.

FIG. 20 is a skeleton diagram showing a tenth embodiment.

FIG. 21 is a skeleton diagram showing an eleventh embodiment.

FIG. 22 is a velocity diagram showing a rotation ratio of each element of the planetary gear device at each shift speed of the eleventh embodiment.

FIG. 23 is a skeleton diagram showing a twelfth embodiment.

FIG. 24 is a velocity diagram showing a rotation ratio of each element of the planetary gear device at each shift speed of the twelfth embodiment.

FIG. 25 is a skeleton diagram showing a thirteenth embodiment.

FIG. 26 is a velocity diagram showing a rotation ratio of each element of the planetary gear device at each shift speed of the thirteenth embodiment.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 10 ... Automatic transmission, 11 ... Fluid torque converter, 12 ... Transmission case, 13 ...
Common axis, 15, 76 ... input shaft, 16, 60 ...
Compound planetary gear unit for reduction, 17, 84, 88, 95 ...
· Double planetary gearing for shifting, 18 ··· output shaft, 23 ·
..Small diameter pinion, 24 ... large diameter pinion, 25
.Stepped pinions, 31, 32, 54, 93, 99 ...
Double pinion type planetary gear mechanism, 33, 63 ... intermediate pinion, 34, 62 ... long pinion, 49
..Gear reduction gears, 50... Rotation state switching means, 5
3, 94, 98 ... single pinion type planetary gear mechanism, 70, 72 ... planetary gear device for reduction, 55 ...
Deceleration rotation output member, 71 ... pinion, 74, 83
..Connecting member, 75: reduction gear train, 84: connecting member, S1, S2, S3, S4: sun gear, C
1, C2, C3, C4 ... carrier, R1, R2, R
3, R4: ring gear, C-1 to C-3: first
To third control clutch, C-4, C-5: rotation control clutch, B-1, B-2: rotation control brake, B
-3, B-4 ... first and second control brakes, F1 ...
・ One-way clutch.

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Satoru Kasuya 10 Takane, Fujiimachi, Anjo, Aichi Prefecture Inside Aisin AW Co., Ltd.・ Within AW Co., Ltd. (72) Inventor Toshihiko Aoki 10th, Takane, Fujii-machi, Anjo-shi, Aichi F-term in Aisin AW Co., Ltd. (reference) 3J028 EA25 EA27 EA30 EB09 EB14 EB31 EB37 EB62 EB66 FA13 FA14 FB02 FC13 FC16 FC18 FC20 FC23 FC24 FC25 FC62 GA02 HA14

Claims (15)

[Claims] An input shaft, a gear reduction device connected to the input shaft and configured to generate a reduced rotation at a reduced rotation output member having a lower rotation speed than the rotation of the input shaft, and at an interval corresponding to a gear ratio in a speed diagram. A multiple speed planetary gear set having first, second, third and fourth elements respectively corresponding to the four elements arranged in sequence and the reduced rotation output member in a reduced rotation state or a free rotation state; Rotating state switching means for switching, first and third control clutches for removably connecting the decelerated rotation output member and the fourth and first elements, respectively;
A second connecting means for detachably connecting the input shaft and the second element;
An automatic transmission comprising: a control clutch; first and second control brakes for selectively restricting rotation of the first and second elements; and an output shaft connected to the third element. . 2. The automatic transmission according to claim 1, wherein
The rotation state switching means, in the reduced rotation state, to rotate the reduced rotation output member at reduced rotation by the gear reduction device,
An automatic transmission characterized by allowing rotation of a reduced rotation output member other than reduced rotation in a free rotation state. 3. The automatic transmission according to claim 1, wherein
The rotation state switching unit allows the reduced speed rotation to be generated in the reduced rotation output member by the gear reduction device in the reduced rotation state, and does not cause the reduced speed rotation member to generate the reduced rotation by the gear reduction device in the free rotation state. An automatic transmission characterized in that: 4. The automatic transmission according to claim 1, wherein
The rotation state switching means allows power transmission between the input shaft and the reduced rotation output member via the gear reduction device in the reduced rotation state, and reduces the speed with the input shaft via the gear reduction device in the free rotation state. An automatic transmission, wherein power transmission between the rotary output member and the rotary output member is interrupted. 5. The automatic transmission according to claim 1, wherein a stepped pinion comprising a small-diameter and a large-diameter sun gear, and a large-diameter and a small-diameter pinion that meshes with the small-diameter and the large-diameter sun gear, respectively. The gear reduction device is constituted by a reducing double planetary gear device including a carrier to be supported and a ring gear connected to the input shaft and meshing with the large-diameter pinion, and the carrier is used as the reduced rotation output member of the gear reduction device. Connected to the first and third control clutches,
An automatic transmission, wherein the rotation state switching means is constituted by first and second rotation control brakes for selectively restricting rotation of the small-diameter and large-diameter sun gears, respectively. 6. The automatic transmission according to claim 1, wherein the input shaft is a carrier that supports a sun gear, a long pinion that meshes with the sun gear, and an intermediate pinion that meshes with the long pinion. The gear reduction device is constituted by a double planetary gear device for reduction having a former ring gear meshed with the long pinion and a latter ring gear meshed with the intermediate pinion, and the carrier is used as a reduced rotation output member of the gear reduction device. An automatic transmission, wherein the rotation state switching means is constituted by first and second rotation control brakes connected to the first and third control clutches and selectively restricting rotation of the sun gear and the subsequent ring gear, respectively. Machine. 7. The automatic transmission according to claim 1, further comprising a sun gear, a carrier that supports a pinion that meshes with the sun gear, and a ring gear that is connected to the input shaft and meshes with the pinion. The gear reduction device is constituted by a planetary gear device for reduction, and the carrier is used as the first rotation reduction member of the gear reduction device.
A rotation control brake connected to a third control clutch to selectively restrict rotation of the sun gear;
An automatic transmission, wherein the rotation state switching means is constituted by a rotation control clutch that connects and detachably connects any two of the carrier and the ring gear. 8. The automatic transmission according to claim 1, wherein the sun gear whose rotation is restricted, a carrier that supports a pinion that meshes with the sun gear, and the pinion that is connected to the input shaft. The reduction gear planetary gear device including a meshing ring gear, and a reduction rotation output member that is rotatably provided concentrically with the reduction planetary gear device and selectively transmits the rotation of the ring gear or the carrier. The first and second rotation control clutches are configured to connect the deceleration rotation output member to the first and third control clutches, and to connect the ring gear and the carrier to the deceleration rotation output member in a detachable manner, respectively. An automatic transmission, comprising the rotation state switching means. 9. The automatic transmission according to claim 1, comprising a sun gear whose rotation is restricted, a carrier that supports a pinion that meshes with the sun gear, and a ring gear that meshes with the pinion. The gear reduction device is constituted by a planetary gear device for use, the carrier is connected to the first and third control clutches as a reduction rotation output member of the gear reduction device, and the carrier and the ring gear of the planetary gear device for reduction and An automatic transmission, wherein the rotation state switching means is constituted by first and second rotation control clutches which are detachably connected to an input shaft. 10. The automatic transmission according to claim 1, further comprising a sun gear, a carrier that supports a pinion that meshes with the sun gear, and a ring gear that is connected to the input shaft and meshes with the pinion. A rotation configured to constitute the gear reduction device with a planetary gear device for reduction, to connect the carrier to the first and third control clutches as a reduction rotation output member of the gear reduction device, and to selectively restrict rotation of the sun gear; An automatic transmission, wherein the rotation state switching means is constituted by a control brake. 11. The automatic transmission according to claim 1, wherein a sun gear whose rotation is restricted,
A reduction planetary gear device comprising a carrier supporting a pinion meshing with the sun gear and a ring gear connected to the input shaft and meshing with the pinion; and a rotation of the carrier rotatably provided concentrically with the reduction planetary gear device. And the reduced speed output member, to which the gear is selectively transmitted, constitutes the gear reduction device. The reduced speed output member is connected to the first and third control clutches, and the carrier and the reduced speed output member are connected. An automatic transmission, wherein the rotation state switching means is constituted by a rotation control clutch detachably connected. 12. The automatic transmission according to claim 1, wherein the sun gear is restricted in rotation.
The reduction gear planetary gear device includes a carrier that supports a pinion that meshes with the sun gear and a ring gear that meshes with the pinion, and the gear reduction device includes the carrier as a reduction rotation output member of the reduction planetary gear device. An automatic transmission, wherein the rotation state switching means is constituted by a rotation control clutch connected to first and third control clutches and removably connecting a ring gear of the planetary gear unit for reduction and the input shaft. . 13. The automatic transmission according to claim 1, wherein the plurality of gears fixed to an input shaft and the gearbox are rotatably supported concentrically with the double planetary gear device for shifting. A deceleration gear train including a plurality of gears that mesh with a plurality of gears to generate input rotation and deceleration rotation, and the deceleration rotation selectively provided to be rotatable concentrically with the dual gear planetary gear device for transmission. And a reduced-speed rotation output member configured to form the gear reduction device, the reduced-speed rotation output member is connected to the first and third control clutches, and the reduced-speed rotation output member is configured to generate reduced-speed rotation of the gear train. An automatic transmission, wherein said rotation state switching means is constituted by a rotation control clutch removably connected to said automatic transmission. 14. The automatic transmission according to claim 1, wherein at least one of two sets of planetary gear mechanisms constituting said double gear planetary gear unit for shifting is a double pinion type planetary gear mechanism. Wherein the third element is a ring gear. 15. The automatic transmission according to claim 1, wherein the first and second sun gears mesh directly with the first sun gear and mesh with the second sun gear via an intermediate pinion. And a carrier that supports the intermediate pinion, and a ring gear that meshes with the long pinion and is connected to the output shaft to constitute the double planetary gear device for speed change, wherein the first element is the first sun gear and the second sun gear. 2 elements as carrier, 3rd element
An automatic transmission, wherein the element is a ring gear, and the fourth element is a second sun gear.