JP3521958B2 - Gear train for automatic transmission - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a gear train for a planetary gear type automatic transmission used in a multi-stage automatic transmission such as an automobile or a railway vehicle.

[0002]

2. Description of the Related Art As a conventional multi-stage automatic transmission, for example, many four-forward automatic transmissions have been installed in passenger cars. In recent years, various forward five-speed automatic transmissions have been proposed in order to further increase the number of gear stages depending on the vehicle model, particularly for the purpose of improving fuel consumption performance. For example, JP-A-47-19268 and JP-A-50-64660.
The publication discloses an integral type automatic transmission gear train for forward fifth speed using three sets of planetary gears.

[0003]

However, in such a conventional gear train for an automatic transmission, since two or more shafts or hollow shafts are arranged on the inner diameter side of the sun gear, the diameter of the sun gear is reduced relative to the total length. However, there is a problem in that it becomes large in size as a whole and interferes with surrounding units, the vehicle body, and the like when mounted on a vehicle or the like. The present invention has been made in view of such conventional problems, and an object of the present invention is to provide a gear train for an automatic transmission that can have a compact structure as a whole.

[0004]

Therefore, the present invention according to claim 1 is provided with a first, a second, and a third planetary gear device in the transmission case between the input shaft and the output shaft in order. In a gear train for an automatic transmission that obtains at least a fifth forward speed by selecting a plurality of fastening elements,
The planetary gear device is a double pinion type planetary gear device,
The second planetary gear device is a single pinion type planetary gear device in which the sun gear is divided and the carrier can be output from the middle to the inner diameter side, and the pinion that meshes with the sun gear is a long pinion, which is a third planetary gear device. Is a single pinion type planetary gear device, the ring gear of the first planetary gear device and the ring gear of the third planetary gear device are connected to form a first rotating member, and the carrier of the first planetary gear device and the ring gear of the second planetary gear device are connected. To form a second rotating member, connect the sun gear of the first planetary gear device, the sun gear of the second planetary gear device, and the sun gear of the third planetary gear device to form a third rotating member of the third planetary gear device. The carrier serves as a fourth rotating member, and the first rotating member can be coupled to the input shaft by the first fastening element and can be fixed by the fourth fastening element. The member can be coupled to the input shaft by the second fastening element, the third rotating member can be coupled to the input shaft by the third fastening element, and can be fixed by the fifth fastening element, and the fourth rotating member can be the sixth fastening member. The elements can be fixed, and the carrier of the second planetary gear unit is connected to the output shaft.

Further, in the invention described in claim 2, in addition to the above construction, a gear for extracting power is further provided between the first, second and third fastening elements and the input shaft. In addition,
The first, second and third fastening elements are clutches,
The fourth fastening element may be a one-way clutch and a brake that are provided in parallel with each other, and the fifth and sixth fastening elements may be brakes.

[0006]

First, when the second fastening element and the fourth fastening element are fastened, the rotation of the input shaft is transmitted to the second rotary member as it is, and the first rotary member is fixed. As a result, the sun gear of the first planetary gear device rotates in the reverse direction, so that the ring gear to which the rotation of the input shaft is input and the sun gear in the second planetary gear device rotate in reverse, and the rotation reduced from the carrier of the second planetary gear device. Is output to obtain the first forward speed.

Next, when the fourth fastening element is released and the sixth fastening element is fastened, the rotation of the input shaft is transmitted to the second rotary member and the fourth rotary member is fixed. As a result, the sun gear and the ring gear of the third planetary gear device are in a reverse rotation relationship, but the degree of reverse rotation of the sun gear in the second planetary gear device is less than in the first speed, and the forward second speed is set from the carrier. can get.

When the sixth fastening element is further opened and the fifth fastening element is fastened, the rotation of the input shaft is transmitted to the second rotary member and the third rotary member is fixed. As a result, the second planetary gear device operates, the reduced rotation is output, and the third forward speed is obtained. Next, when the fifth fastening element is released and the first fastening element is fastened, the rotation of the input shaft between the ring gear and the carrier of the first planetary gear device is transmitted. As a result, the first rotating member, the second rotating member, and the third rotating member rotate in the same direction as the input shaft, and the carrier of the first planetary gear device also rotates integrally.
The fourth forward speed with a reduction ratio of 1 is obtained on the output shaft.

From the above state, the second fastening element is released,
When the fifth fastening element is fastened, the rotation of the input shaft is transmitted to the first rotary member and the third rotary member is fixed. As a result, in the double pinion type first planetary gear device, the speed of the carrier is increased from that of the ring gear (first rotating member) and the speed of the second rotating member is increased. Then, from the carrier of the second planetary gear device in which the sun gear is fixed and the ring gear is accelerated, the fifth forward speed, which is accelerated by the rotation of the input shaft, is obtained on the output shaft.

When the third fastening element and the fourth fastening element are fastened, the rotation of the input shaft is transmitted to the third rotary member, and the first rotary member is fixed. As a result, in the double-pinion type first planetary gear device, the carrier (second rotating member) of the double pinion type first planetary gear device is reversely rotated at a higher speed than the rotation of the input shaft. As a result, the decelerated reverse rotation is output from the carrier of the second planetary gear device, and the reverse speed is obtained on the output shaft.

[0011]

1 is a skeleton diagram showing a first embodiment of the present invention. A first planetary gear device 4, a second planetary gear device 5, and a third planetary gear device 6 are provided in order from the input shaft 2 side along an axis connecting the input shaft 2 and the output shaft 3 supported by the transmission case 1. Has been. In addition,
In the figure, since each member is configured symmetrically with respect to the axis, the lower half of the axis is omitted from the drawing. The first planetary gear device 4 is a double pinion type planetary gear device, and includes a first sun gear 4s, a first carrier 4c, a first ring gear 4r,
And a first pinion 4p rotatably supported by the first carrier 4c. The first pinion 4p is a gear 4p
1 and the gear 4p2, and the gear 4p1 is the first ring gear 4
r and the gear 4p2 mesh with the first sun gear 4s, respectively.

The second planetary gear unit 5 includes a second sun gear 5
s, the second carrier 5c, the second ring gear 5r, and the second pinion 5 rotatably supported by the second carrier 5c.
It consists of p. The second sun gear 5s is the front sun gear 5s.
It is divided into F and rear sun gear 5sR, and the second carrier 5c can be output from the middle to the inner diameter side.
The second pinion 5p is formed into a long long pinion,
On the one hand, it meshes with the second ring gear 5r, and on the other hand, it meshes with the divided front sun gear 5sF and rear sun gear 5sR of the second sun gear 5s. The front sun gear 5sF and the rear sun gear 5sR rotate in the same way via the second pinion 5p.

The third planetary gear unit 6 is a known single pinion type, and includes a third sun gear 6s and a third pinion 6.
p, a third carrier 6c and a third ring gear 6r, the third pinion 6p is rotatably supported by the third carrier 6c, and the third sun gear 6s and the third ring gear 6r.
Located between and meshed with each.

First to third clutches C1 to C3 are disposed on the input shaft 2 side of the first planetary gear unit 4, and a first clutch C1 and a first planetary gear unit 4 are provided with a first clutch C1 to C3. Brake B
1 and a one-way clutch 7 are provided. Further, second and third brakes B2 and B3 are arranged on the output shaft extraction side of the third planetary gear device 6.

The first ring gear 4r of the first planetary gear unit 4
And the third ring gear 6r of the third planetary gear device 6 are integrally connected by the connecting member a to form the first rotating member M1, and the first clutch C1 is connected via the connecting member b extending from the connecting member a. Is connectable to the input shaft 2. In addition, the first rotating member M1 includes the first brake B1 and the one-way clutch 7 for the transmission case 1
It can be fixed to. Further, the first carrier 4c of the first planetary gear device 4 and the ring gear 5r of the second planetary gear device 5 are integrally connected by the connecting member c to form the second rotating member M2, and the connecting member d is interposed. Second clutch C2
Is connectable to the input shaft 2.

The first sun gear 4s of the first planetary gear device, the second sun gear 5s of the second planetary gear device 5 and the third sun gear 6s of the third planetary gear device 6 are integrally connected by connecting members e and e '. Constitutes a third rotating member M3 and can be connected to the input shaft 2 by a third clutch C3 via a connecting member f. The third rotating member M3 can be fixed to the transmission case 1 by the second brake B2 via the connecting member h. The third carrier 6c of the third planetary gear device 6 constitutes a fourth rotating member M4 and can be fixed to the transmission case 1 by a third brake B3 via a connecting member g. Then, the second carrier 5p of the second planetary gear device 5 is connected to the output shaft 3
Are linked to.

In the above structure, the first fastening element
As shown in Table 1, normally, two of the third clutches C1 to C3, the one-way clutch 7 and the first to third brakes B1 to B3 are engaged to obtain the fifth forward speed and the first reverse speed. In the table, ○ indicates a fastening element to be fastened. In the table, D is the D range, 3, 2, 1 is 3, respectively.
The first brake B1 shown by the broken lines and showing the respective shift speeds in the 2nd and 1st ranges is operated so as to overlap the one-way clutch 7 when engine braking is required.

[Table 1]

Next, an outline of the speed change operation in the above configuration will be described. First, when selecting the first forward speed, the second clutch C2 is engaged as shown in FIG. In the figure, the operating planetary gear device, clutches and brakes that are fastening elements, and rotating members are shown by thick solid lines.
The same applies to subsequent figures. This allows the input shaft 2
Is transmitted to the second rotating member M2 as it is. That is, the rotation of the input shaft 2 is directly transmitted from the first carrier 4c of the first planetary gear device 4 to the second ring gear 5r of the second planetary gear 5. Here, since the one-way clutch 7 blocks the rotation of the first rotating member M1 in the reverse direction, the third rotating member M3 rotates in the direction opposite to the input shaft 2. Therefore, the output shaft 3 connected to the second carrier 5c of the second planetary gear device 2 can obtain the first speed that is decelerated with respect to the rotation of the second ring gear 5r.

Next, in selecting the second forward speed,
From the first speed state, as shown in FIG. 3, the third brake B3 is further engaged. As a result, the rotation of the input shaft 2 is transmitted to the second rotation member M2 as it is and the rotation of the third rotation member M2 is transmitted.
The third carrier 6c (that is, the fourth rotation member M4) of the planetary gear device 6 is fixed. Therefore, the third sun gear 6s of the third planetary gear device 6, that is, the third rotating member M3.
And the third ring gear 6r are in a reverse rotation relationship, the one-way clutch 7 does not operate, and the ring gear 4r (first rotating member M1) of the first planetary gear device rotates in the same direction as the input shaft. Therefore, the degree of reverse rotation of the first sun gear 4s is weakened, and the second carrier 5c of the second planetary gear device 5 connected to the output shaft 3 rotates at a reduction ratio smaller than that at the first speed,
The second speed is obtained.

When selecting the third forward speed, the third brake B3 is released from the second speed state to set the second brake B.
Conclude 2. As a result, as shown in FIG. 4, the second rotary member M2 rotates in the same rotation as the input shaft 2, while the third rotary member M3 is fixed, so that in the second planetary gear device 2, the second carrier 5c is provided. The third speed reduced with respect to the rotation of the second ring gear 5r is obtained.

For the fourth forward speed, the second brake B2 is released and the first clutch C1 is engaged from the third speed state. As a result, as shown in FIG.
The first and second rotating members M2, that is, the first ring gear 4r and the first carrier 4c of the first planetary gear device rotate integrally with the input shaft 2, and the third rotating member M3 also rotates in the same manner.
Therefore, the second carrier 5c of the second planetary gear device 5 also rotates at the same speed as the input shaft 2, and the fourth speed with a reduction ratio of 1 is obtained on the output shaft.

In selecting the fifth forward speed, the second clutch C2 is released from the fourth state, and as shown in FIG.
Engage the second brake B2. As a result, the rotation of the input shaft 2 is maintained as it is in the first ring gear 4r (first rotating member M).
1), the third rotating member M3 is fixed to the transmission case 1. Therefore, in the double pinion type first planetary gear device, the speed of the first carrier 4c of the first planetary gear device is higher than that of the first rotary member M1, and thus the speed of the second rotary member M2 is increased. Then, the second planetary gear device 5
As a result, the fifth speed, which is faster than the rotation of the input shaft, is obtained on the output shaft 3.

When selecting the reverse drive, the third clutch C3 and the first brake B1 are engaged as shown in FIG. As a result, the rotation of the input shaft 2 remains unchanged and the third rotation member M
3 and the first rotary member M1 is fixed to the transmission case 1, so that the first double-pinion type first
Due to the operation of the planetary gear device 4, the second rotating member M2 is rotated at an increased speed in the direction opposite to the direction of the input shaft, and the second rotating member M2 of the second planetary gear device 2 is rotated.
A reverse speed stage can be obtained on the output shaft 3 connected to the carrier 5c.

FIG. 8 shows an alignment chart in the above gear train. Here, α1, α2, and α3 are respectively the first, second, and
The sun gear 4s of each of the third planetary gear units 4, 5, and 6,
5s, 6s and the gear ratio of the ring gears 4r, 5r, 6r, S, R, C are sun gears, ring gears and carriers,
The subscripts 1, 2, and 3 correspond to the first, second, and third planetary gear units, respectively. Based on this, the gear ratio of each gear is shown in Table 1 above. This embodiment is configured as described above,
By using the planetary gear device, the overall length is shortened, and since only one output shaft 3 is inserted on the inner diameter side of the sun gear, the overall diameter is also small, and the size is small and the mounting layout on a vehicle or the like is easy. Has the effect.

FIG. 9 is a skeleton diagram showing a second embodiment of the present invention. This embodiment is different from the first embodiment in that the installation positions of the first clutch C11, the second clutch C12, and the third clutch C13 are changed, and the first clutch C11, the second clutch C12, and the third clutch C13 are arranged at the same position in the axial direction so as to be overlapped in the radial direction. First to third clutch C11
A gear 8 for extracting power is arranged between C13 and the input shaft 2. According to this embodiment, the same effect as that of the first embodiment can be obtained, and the power from the input shaft 2 can be extracted and utilized.

In each embodiment, the engagement element is the clutch C.
1 to C3 or C11 to C13 and brakes B1 to B3
However, the present invention is not limited to the illustrated one, and a multi-disc clutch,
A band brake or a one-way clutch can be used in an appropriate combination. The positions where they are arranged can also be changed as necessary, and can be arbitrarily selected according to environmental conditions such as a mounting space in a vehicle or the like.

[0027]

As described above, according to the present invention, the double pinion type first planetary gear device is provided between the input shaft and the output shaft.
A single pinion type second planetary gear unit that uses a long pinion as a pinion that meshes with the sun gear while allowing the carrier to be output from the middle of the sun gear to the inner diameter side, and a simple single type third planetary gear unit Provided, the ring gear of the first planetary gear set and the ring gear of the third planetary gear set are connected to form a first rotating member, which can be coupled to the input shaft by the first fastening element and can be fixed by the fourth fastening element. And a carrier of the first planetary gear device and a ring gear of the second planetary gear device are connected to form a second rotating member, which can be coupled to the input shaft by a second fastening element.
The sun gear of the planetary gear device, the sun gear of the second planetary gear device, and the sun gear of the third planetary gear device are connected to form a third rotating member, which can be coupled to the input shaft by the third fastening element, and the fifth Since it can be fixed by a fastening element, the carrier of the third planetary gear device can be used as a fourth rotating member, and this can be fixed by a sixth fastening element, and the carrier of the second planetary gear device is connected to the output shaft. By selecting the two engagement elements, at least the fifth forward speed is obtained.

Since only one output shaft connected to the carrier of the second planetary gear device passes through the inside of the sun gear, the diameter of the sun gear can be reduced and the overall structure can be made compact. It has the effect that Furthermore, by providing a gear for taking out power between the first, second and third fastening elements and the input shaft,
Power can be taken out easily.

[Brief description of drawings]

FIG. 1 is a skeleton diagram showing a first embodiment of the present invention.

FIG. 2 is a diagram showing a rotation transmission path of a forward first speed gear according to the first embodiment.

FIG. 3 is a diagram showing a rotation transmission path of a second forward speed in the first embodiment.

FIG. 4 is a diagram showing a rotation transmission path of a third forward speed in the first embodiment.

FIG. 5 is a diagram showing a rotation transmission path of a fourth forward speed according to the first embodiment.

FIG. 6 is a diagram showing a rotation transmission path of a fifth forward speed in the first embodiment.

FIG. 7 is a diagram showing a rotation transmission path of a reverse gear in the first embodiment.

FIG. 8 is a collinear diagram of a gear train in the first embodiment.

FIG. 9 is a skeleton diagram showing a second embodiment of the present invention.

[Explanation of symbols]

1 transmission case 2 input axes 3 output axes 4 First planetary gear unit 4s 1st sun gear 4r 1st ring gear 4c 1st carrier 4p first pinion 4p1 1st gear 4p2 second gear 5 Second planetary gear unit 5s Second Sun Gear 5sF front sun gear 5sR Rear sun gear 5r 2nd ring gear 5c Second carrier 5p second pinion 6 Third planetary gear unit 6s Third Sun Gear 6r 3rd ring gear 6c Third carrier 6p 3rd pinion 7 one-way clutch 8 Gear for taking out power (PTO gear) C1 to C3 First clutch to third clutch B1 to B3 First brake to third brake M1 to M4 First rotating member to fourth rotating member ah connection member

─────────────────────────────────────────────────── --Continued from the front page (56) Reference JP-A-2-118241 (JP, A) JP-A-1-176835 (JP, A) JP-A 1-169156 (JP, A) JP-A-50- 64660 (JP, A) JP 47-19268 (JP, A) JP 62-4633 (JP, A) JP 1-316552 (JP, A) JP 3-96741 (JP, A) JP-A-2-248745 (JP, A) JP-A-2-245551 (JP, A) JP-A-54-132058 (JP, A) JP-A-47-23754 (JP, A) (JP, U) (58) Fields surveyed (Int.Cl. ⁷ , DB name) F16H 3/00-3/78

Claims (3)

(57) [Claims] 1. A transmission case is provided with first, second, and third planetary gear devices between an input shaft and an output shaft in order, and at least a fifth forward speed is established by a selective operation of a plurality of fastening elements. In the automatic transmission gear train to be obtained, the first planetary gear device is a double pinion type planetary gear device, the second planetary gear device divides a sun gear, and a carrier can be output from the middle to the inner diameter side. In addition, a single pinion type planetary gear device having a long pinion as a pinion that meshes with the sun gear is used, and the third planetary gear device is a single pinion type planetary gear device,
The ring gear of the first planetary gear device and the ring gear of the third planetary gear device are connected to form a first rotating member,
The carrier of the planetary gear device and the ring gear of the second planetary gear device are connected to form a second rotating member, and the sun gear of the first planetary gear device, the sun gear of the second planetary gear device, and the sun gear of the third planetary gear device are connected. And make it the third rotating member,
The carrier of the third planetary gear device is used as a fourth rotating member, the first rotating member is connectable to the input shaft with a first fastening element, and the fourth rotating element is fixable with the second rotating member. The second fastening element can be coupled to the input shaft, the third rotation member can be coupled to the input shaft by the third fastening element, and the third rotation member can be fixed by the fifth fastening element, and the fourth rotation member can be the sixth fastening member. A gear train for an automatic transmission, characterized in that it can be fixed by an element, and the carrier of the second planetary gear device is connected to an output shaft. 2. A transmission case is provided with first, second, and third planetary gear units between an input shaft and an output shaft in order, and at least a fifth forward speed is established by a selective operation of a plurality of fastening elements. In the automatic transmission gear train to be obtained, the first planetary gear device is a double pinion type planetary gear device, the second planetary gear device divides a sun gear, and a carrier can be output from the middle to the inner diameter side. In addition, a single pinion type planetary gear device having a long pinion as a pinion that meshes with the sun gear is used, and the third planetary gear device is a single pinion type planetary gear device,
The ring gear of the first planetary gear device and the ring gear of the third planetary gear device are connected to form a first rotating member,
The carrier of the planetary gear device and the ring gear of the second planetary gear device are connected to form a second rotating member, and the sun gear of the first planetary gear device, the sun gear of the second planetary gear device, and the sun gear of the third planetary gear device are connected. And make it the third rotating member,
The carrier of the third planetary gear device is used as a fourth rotating member, the first rotating member is connectable to the input shaft with a first fastening element, and the fourth rotating element is fixable with the second rotating member. The second fastening element can be coupled to the input shaft, the third rotation member can be coupled to the input shaft by the third fastening element, and the third rotation member can be fixed by the fifth fastening element, and the fourth rotation member can be the sixth fastening member. And a carrier for connecting the second planetary gear device to an output shaft, and a gear for extracting power is provided between the first, second and third fastening elements and the input shaft. Gear train for automatic transmission. 3. The first, second and third fastening elements are clutches, and the fourth fastening element is a one-way clutch and a brake which are provided in parallel with each other, and fifth and sixth fastening elements. 3. The gear train for an automatic transmission according to claim 1, wherein the element is a brake.