JP2002349647A - Planetary gear equipment of automatic transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve flexibility of setting the gear ratio of a planetary gear, by making small the diameter of sun gear arranged on the circumference of rotor shaft. SOLUTION: The planetary gear G1 of the automatic transmission consists of a sun gear S1, a ring gear R1, a pinion gear P1 brought into contact with these gears and a carrier C1 supporting the pinion gear P1 in free rotation. The sun gear is formed as a unit in the stator shaft 14 for supporting the sun gear S1 into the hole along the shaft direction of the transmission gear case 10, making the shaft 11 penetrate. Thereby, the inside diameter of the sun gear can be made small with respect to the external diameter of the rotor shaft and the setting range for tooth number of the sun gear to the tooth number of the ring gear is expanded and the flexibility of setting gear ratio of the planetary gear is improved.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an automatic transmission, and more particularly, to a planetary gear device constituting a transmission mechanism thereof.

[0002]

2. Description of the Related Art A planetary gear device constituting a transmission mechanism of an automatic transmission is generally disposed between an input shaft connected to a turbine output shaft of a torque converter and an output shaft connected to an output member of the transmission mechanism. It is often arranged on the outer periphery of a rotating shaft such as an input shaft or an output shaft that runs through the entire length of the transmission, or an intermediate shaft that connects them (these shafts may be multiple shafts that overlap in the radial direction). Due to such an arrangement, the sun gear of the planetary gear device has its inner diameter restricted to the outer diameter of the rotating shaft passing therethrough (this outer diameter is naturally determined by the torque transmitted by the shaft). Also, in automatic transmissions, frictional members of clutches and brakes are often superposed on the outer peripheral side of the planetary gear device in view of shortening the shaft length. In such an arrangement, the outer diameter of the planetary gear device is small. The outer diameter of the planetary gear device is desired to be as small as possible because it leads to a reduction in the diameter of the friction member disposed on the outer peripheral side, which also leads to a reduction in the diameter of the entire automatic transmission.

In general, reducing the meshing diameter of the sun gear is the most effective way to reduce the diameter of the planetary gear device, because it also reduces the diameter of the other two gears. However, since the inner diameter is regulated for the above reasons,
There is naturally a limit to reducing the sun gear meshing diameter. Also,
Although there is no way to reduce the outer diameter of the ring gear by reducing the meshing diameter of the pinion gear and thereby reducing the meshing diameter of the ring gear meshing with the pinion gear,
Since a reduction in the diameter of the pinion gear leads to a reduction in the wall thickness, there is naturally a limit in terms of maintaining strength against transmission torque. Under these circumstances, reducing the diameter of the planetary gear device is a difficult problem.

[0004]

Therefore, the applicant assumed the arrangement shown in FIG. 4 as the arrangement of the planetary gear device for minimizing the meshing diameter of the sun gear. In this arrangement,
The sun gear S1 which should be fixed to the transmission case 10 because it becomes a fixed reaction force element,
Stator shaft 1 fixed by serration fitting to 0
4 is extended into the transmission case 10 and fixed to the outer periphery of the end by spline engagement, whereby the sun gear S
1 is substantially reduced from the outer diameter of the transmission case boss to the outer diameter of the stator shaft 14, whereby the rotating shaft 1
The sun gear meshing diameter arranged on the outer periphery of the first gear 1 is reduced. However, even with such an arrangement, the sun gear S1 requires a wall thickness for maintaining strength and forming spline engagement teeth, and there is a limit in reducing the meshing diameter.

The present invention has been devised in view of the above circumstances, and an object of the present invention is to provide a planetary gear device for an automatic transmission in which the meshing diameter of a sun gear disposed around the rotating shaft can be reduced to a maximum. Aim.

[0006]

The above object is achieved by the present invention.
As described in the above, in a planetary gear device comprising a sun gear, a ring gear, a pinion gear meshing with them, and a carrier rotatably supporting the pinion gear, and arranged on an outer periphery of a rotation shaft of the automatic transmission, the sun gear is The transmission shaft is formed integrally with the stator shaft supported in the axial hole of the transmission case through the rotating shaft.

In the above construction, the stator shaft is shifted by the engagement between the inner and outer peripheral surfaces of the stator shaft and the axial hole by press fitting into the axial hole of the transmission case. It is effective to adopt a configuration in which rotation and axial movement are stopped in the machine case.

Further, in the above structure, as set forth in claim 3, the transmission case has a boss portion extending in the axial direction around the outer periphery of the axial hole, and the carrier is provided with:
It is effective to adopt a configuration rotatably supported on the outer periphery of the boss.

Further, in the above construction, a bearing arranged on the inner peripheral side of the sun gear forming portion between the stator shaft and the rotating shaft is formed on the outer periphery of the rotating shaft. It is effective to be configured to be fitted in the concave groove.

Further, in the above construction, the automatic transmission may have a first input path having a first speed ratio directly connected to the input shaft with respect to the rotation of the input shaft. And a second input path having a second speed ratio reduced from the first speed ratio, a four-element planetary gear set, and transmitting rotation from the second input path to the first element of the planetary gear set. And a third clutch for transmitting the rotation from the first input path to the third element of the planetary gear set, and a first brake for engaging the first element. And a second brake that locks the third element, and an output member connected to the fourth element, wherein the planetary gear device is a reduction planetary gear that reduces the rotation from the input shaft and outputs the reduced rotation. Through planetary gear Force path is placed in the second input path, the input path from the input shaft without passing through the speed reduction planetary gear that can adopt a configuration which is the first input path.

[0011]

According to the structure of the first aspect,
By integrally forming the sun gear with the stator shaft, the meshing diameter of the sun gear, which must be fitted to the outer periphery of the rotating shaft, can be reduced to the maximum possible limit of maintaining the strength that the sun gear originally requires. Therefore, with this configuration, the allowable range of reducing the diameter of the sun gear is expanded, and when the meshing diameter of the ring gear is fixed, the setting range of the gear ratio of the ring gear and the sun gear is increased, and the degree of freedom in setting the gear ratio of the planetary gear device is increased. In particular, since the influence of the change in the number of teeth of the sun gear on the gear ratio is much greater than the change in the number of teeth of the ring gear, it is easy to set the gear ratio in the direction of decreasing the gear ratio. When the gear ratio is fixed, the diameter of the ring gear can be easily reduced with the reduction in the diameter of the sun gear, and the size of the planetary gear device can be reduced. In addition, the number of components of the automatic transmission can be reduced by integrating the sun gear with the stator shaft.

Next, according to the second aspect of the present invention, in order to support the stator of the torque converter on the transmission case, the fixed portion of the stator shaft, which is detented and axially detented by the case, is usually removed. Since the gears can be used to support the thrust force applied to the sun gear by being formed of the tooth gears, it is not necessary to process the end surface of the boss portion of the case for supporting the thrust force, and the number of processing steps can be reduced.

Further, according to the third aspect of the present invention, only the boss portion of the transmission case is interposed between the carrier and the sun gear in the support relationship between the elements constituting the planetary gear device, so that the carrier and the sun gear can be connected to each other. The path between the supporting members is shortened, and the positional accuracy is improved because the rotating member does not intervene in the middle.

Further, according to the fourth aspect of the present invention, when a bearing arranged on the inner peripheral side of the sun gear between the stator shaft and the rotation shaft is fitted and supported on the stator shaft side, the bearing is inserted into the stator shaft. Due to the relationship of the fitting of the rotating shaft, while the inner diameter of the bearing cannot be made smaller than the outer diameter of the rotating shaft, by fitting the bearing into a groove formed on the outer periphery of the rotating shaft, Since the outer diameter of the bearing can be reduced to the outer diameter of the rotating shaft, the sun gear diameter can be more easily reduced even with this configuration.

Further, according to the fifth aspect of the present invention, the skipping gear is changed only by changing the setting for reducing the gear ratio of the reduction planetary gear without changing the setting of the gear ratio of the planetary gear set capable of achieving the sixth speed. When set, only the gear ratio step between the two gears sandwiching the skip gear can be reduced. As a result, when a good gear ratio step is set for the sixth gear ratio, the fifth gear can be achieved in a good gear ratio step while following the good gear ratio step, and the planetary gear set and each engagement element And the gear train can be shared by replacing the reduction planetary gears.

[0016]

Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is an axial sectional view showing a planetary gear device of an automatic transmission to which the present invention is applied together with related members. In the drawings, only the planetary gear device and members directly related to the planetary gear device are hatched to distinguish them from additional members.

First, a schematic configuration will be described. In this embodiment, the planetary gear device G1 is disposed on the outer periphery of the planetary gear device with the rotation shaft serving as the input shaft 11, and includes a sun gear S1, a ring gear R1, a pinion gear P1 meshing with them, and a pinion gear P1. And a carrier C1 that rotatably supports P1. Further, according to the feature of the present invention, the sun gear S1 is formed such that the input shaft 11 penetrates the shaft and the axial hole 1 of the oil pump body which forms the front wall of the transmission case 10.
0a is formed integrally with the stator shaft 14 supported by serration fitting. This stator shaft 14
Is a shaft connected via a one-way clutch to a stator of a torque converter housed in a converter housing in front of an oil pump body as a transmission case front wall, as is well known.

In this planetary gear device G1, the diameter of the sun gear S1 is reduced by integration with the stator shaft 17, and the arrangement pitch diameter of the pinion shaft 31 of the carrier C1 supporting the pinion gear P1 is also reduced. Is rotatably supported on the outer periphery of a boss 10b extending rearward around an axial hole 10a from an oil pump body as a transmission case. Further, since the stator shaft 14 is press-fitted into the axial hole 10a of the oil pump body and the inner and outer peripheral surfaces of the stator shaft and the axial hole are engaged with each other, the rotation and the axial movement of the stator shaft 14 are stopped by the oil pump body. In order to maintain the continuity of the meshing, the thrust force of the sun gear S1, which is usually formed as a helical gear, is supported by the engaging peripheral surface. Further, the stator shaft 14
A bearing 15 disposed on the inner peripheral side of the sun gear forming portion between the shaft 11 and the rotating shaft 11 is provided with a concave groove 11 formed on the outer periphery of the rotating shaft 11.
a.

Further, each part will be described sequentially. First,
Rotary shaft 11 penetrating the inner peripheral side of planetary gear device G1
Is an input shaft of a transmission mechanism integrated with a turbine output shaft of a torque converter (not shown), and has a flange portion 11b extending radially from the shaft periphery connected to a ring gear flange 32 of the planetary gear device G1. The bearing 15 that fits into the concave groove 11a formed on the outer periphery of the rotating shaft 11 is a split ring made of synthetic resin, and is configured to be fittable from the circumference of the shaft. A number of seal ring grooves are further formed on the outer periphery of the input shaft 11, and a communication portion between the oil passage of the stator shaft 14 and the in-shaft oil passage of the input shaft 11 is sealed in each of the grooves. A plurality of seal rings are also provided.

The stator shaft 14, which fits on the outer periphery of the input shaft 11 and the inner periphery of the boss 10b of the oil pump body, is formed with sun gear teeth on the outer periphery of the rear end of the shaft. The inner peripheral side of the portion where the sun gear teeth are formed on the outer periphery is slightly increased in diameter due to sliding contact with the outer periphery of the bearing 15. Except for the point described above, the inner and outer peripheral surfaces are smooth surfaces having a substantially uniform diameter.

The boss portion 10b of the oil pump body that supports the stator shaft 14 on the inner peripheral side has an inner peripheral side at the rearmost end of the inner peripheral surface having a uniform diameter, and is enlarged in diameter to secure an engagement area. The outer peripheral side is reduced in diameter in two stages toward the rear, the first-stage reduced diameter portion is an oil passage connection with the clutch hydraulic servo, The step reduced diameter portion serves as a support portion of the clutch hydraulic servo drum and a support portion of the carrier C1 of the planetary gear device G1 by bearing support via the bush fitted on the bush and the mating member.

The carrier C1 of the planetary gear device G1
Is composed of a carrier body 33 that supports the rear end side of the pinion shaft 31 and a carrier cover 34 that supports the front end side of the pinion shaft 31. Since the friction member of the clutch is arranged on the outer periphery of the planetary gear device G1. The outer peripheral side of the carrier cover 34 covers the outer periphery of the ring gear R1 and has a drum shape with a spline formed on the outer peripheral side, thereby constituting a clutch hub. Ring gear R1
Is a ring gear flange 3 having a simple cylindrical shape with inner peripheral teeth formed and having an outer peripheral spline engaged with its rear end.
2 is connected to the input shaft 11.

With the above-described connection and support relationship, the planetary gear device G1 becomes a sun gear S1 fixed, a ring gear R1 input, and a carrier C1 output, and constitutes a reduction gear that outputs reduced rotation to the carrier C1 with respect to the ring gear R1 input. ing. By adopting such a configuration, the sun gear S1 of the planetary gear device G1 is reduced in diameter to a meshing diameter substantially equal to the outer diameter of the stator shaft 14 while the inner diameter thereof is made equal to the outer diameter of the input shaft 11. .

In this embodiment, since the meshing diameter of the ring gear R1 is the same as that of the planetary gear device presupposed with reference to FIG. 4, the outer diameter of the planetary gear device G1 is reduced. However, when the meshing diameter of the sun gear S1 is made smaller than the meshing diameter of the ring gear R1, the gear ratio setting for making the gear ratio of the planetary gear device G1 extremely small can be easily performed.

An example of application to a transmission mechanism in which such a small gear ratio setting is effectively used will be described below. FIG.
The gear train shown by skeleton is an example of a vertical type automatic transmission for a front engine rear drive (FR) vehicle, and the gear train includes a three-element torque converter 2 with a lock-up clutch, And a transmission mechanism 1. The torque converter 2 includes a pump impeller 21, a turbine runner 22, and a stator 23. The turbine runner 22 of the torque converter 2 is connected to the input shaft 11 of the transmission mechanism 1.
Reference numeral 3 denotes a one-way rotation of the transmission case 10 (more specifically, an oil pump body which forms the front wall of the transmission case and separates the inside of the case from the inside of the converter housing) by the stator shaft 14 via the one-way clutch 24. Supported as possible.

The speed change mechanism 1 has a first input path T1 having a first speed ratio 1 directly connected to the input shaft 11 with respect to the rotation of the input shaft 11, and a second speed reduced from the first speed ratio. A second input path T2 having a ratio, a Ravigneaux type planetary gear set G, and a first clutch (C-) that transmits rotation from the second input path T2 to a small-diameter sun gear S3 as a first element of the planetary gear set G. 1) and a third clutch (C-C) transmitting to the large-diameter sun gear S2 as a second element.
3), a second clutch (C-2) for transmitting rotation from the first input path T1 to carriers C2 and C3 as third elements of the planetary gear set G, and a large-diameter sun gear S2 of the planetary gear set G. First brake (B
-1), a second brake (B-2) for locking the carriers C2 and C3, and an output shaft 19 as an output member connected to the ring gear R3 (R2).

In contrast to this gear train, the planetary gear device according to the present invention is applied as a deceleration planetary gear G1 that reduces the speed of rotation from the input shaft 11 and outputs the decelerated planetary gear. The input path T2 is an input path from the input shaft 11 that does not pass through the reduction planetary gear, and the input path is a first input path T1.

The planetary gear set G includes a large-diameter sun gear S2, a small-diameter sun gear S3, a long pinion gear P2 and a short pinion gear P3 which are circumscribed and meshed with each other.
Integrated carriers C2 and C3 supporting them,
The short pinion P3 is externally meshed with the small-diameter sun gear S3, and the long pinion P2 is externally meshed with the large-diameter sun gear S2 and is internally meshed with the ring gear R3.

As described above, the reduction planetary gear G1 comprises the sun gear S1, the ring gear R1, the pinion gear P1 meshing with the sun gear S1, and the carrier C1 rotatably supporting the pinion gear, and the pinion gear P1 is externally meshed with the sun gear S1. In addition, the internal gear meshes with the ring gear R1. Then, according to the above connection relationship, the gear R1 is connected to the input shaft 11 so that the ring gear R1 is used as an input element, and the carrier C1 is used as an output element to the second input path T2 by the first clutch (C-1). And the sun gear S1 is fixed to the transmission case 10 as a reaction force element.

The first clutch (C-1) has a multi-plate structure, and its hub side is connected to the reduction planetary gear G1 as described above.
And the third clutch (C-
3) The power transmission member 12 is connected to the drum
Through a small diameter sun gear S3.

The second clutch (C-2) also has a multi-plate construction, and its drum side is connected to the input shaft 11, and its hub side is connected to the carriers C2 and C3 of the planetary gear set G.

Similarly, the third clutch (C-3) has a multi-plate construction, and its drum side is connected to the carrier C1 of the reduction planetary gear G1 via the hub of the first clutch (C-1), and the hub side is the planetary gear. The large-diameter sun gear S2 of the set G is connected via a power transmission member 13.

The first brake (B-1) also has a multi-plate construction, and its hub side is connected to the large-diameter sun gear S2 of the planetary gear set G via the drum of the third clutch (C-3). From the connection relationship between C-3) and the planetary gear set G, the large-diameter sun gear S2 of the planetary gear set G is locked to the transmission case 10.

The second brake (B-2) is connected to the carriers C2 and C3 of the planetary gear set G via an inner race of a one-way clutch (F-1) described later on the hub side.
The carrier C2 and C3 of the planetary gear set G are locked to the transmission case 10 in parallel with the one-way clutch (F-1).

In the gear train shown in the figure, the one-way clutch (F) is arranged in parallel with the second brake (B-2).
-1), which avoids complicated hydraulic control for changing the gripping of the second brake (B-2) and the first brake (B-1) at the time of 1 → 2 shift. 2 brakes (B-
In order to simplify the release control of 2), the first brake (B-
The one-way clutch (F-1) having directionality in engagement and release with respect to the rotation direction in which the engagement force is naturally released with the engagement of 1) is used, and the second brake (B-
It is equivalent to 2).

In the case of an automatic transmission having such a configuration,
As shown in the engagement chart in FIG. 3, the six forward speeds and the first reverse speed are achieved in principle by the engagement and disengagement of each clutch and brake (indicated by the symbol ○, indicating disengagement). Although it is possible, in this example, 3.5 is not used during the forward gear and 5
Speeding up. The main reason for this is that, in this gear train, when all the sixth gears are used, the third and fourth gears are shown in the diagram.
Referring to the engagement / disengagement order of the third clutch (C-3) at the time of the speed, the third clutch for inputting the deceleration rotation is engaged at the third speed (3RD) during the upshift, and the third clutch is engaged. Speed (3.5T
H) disengagement, 4th speed (4TH) engagement, 5th speed (5T)
H) In contrast to the repetition operation of the time release, the shift is performed by skipping the 3.5th speed, which corresponds to the 4th speed in the 6th speed gear train, so that this repetition is eliminated, and the third clutch is engaged during the upshift. (C-3) is engaged in both the third and fourth speeds, so that the complicated engagement and disengagement operation of the third clutch (C-3) is eliminated, and the controllability of shifting is improved.

In the case where the non-use stage is configured as described above, reducing the gear ratio of the reduction planetary gear G1 is effective in improving the gear ratio steps between the respective shift stages. Specifically, by bringing the second speed ratio close to the first speed ratio, the gear ratio step between the gear stages (3rd to 4th speed) in which the skipped gear stage (3.5th speed) is interposed is performed. The gear ratio steps from the lowest gear to the highest gear can be prevented from becoming irregular.

In the case of this example, it is possible to set the gear ratios as illustrated in the table for each shift speed. The gear ratios in this table are the gear ratio λ ₁ = 0.333 between the sun gear S1 of the reduction planetary gear G1 and the ring gear R1, the large diameter sun gear S2 and the ring gear R of the planetary gear set G.
3 (R2), ie, gear ratio λ ₂ = 0.458 on the simple side,
This example illustrates a case in which the small-diameter sun gear S3 and the ring gear R3 (R2), that is, the double-side gear ratio λ ₃ = 0.375 are set. In this case, the input / output gear ratio is the first speed (1ST): (1 + λ ₁ ) / Λ ₃ = 3.556 Second speed (2ND): (1 + λ ₁ ) (λ ₂ + λ ₃ ) / λ ₃
(1 + λ ₂ ) = 2.032 Third speed (3RD): 1 + λ ₁ = 1.333 (3.5th speed (3.5TH): (1 + λ ₁ ) / (1 + λ)
₁₋ λ ₁ λ ₃ ) = 1.103) Fourth speed (4TH): (1 + λ ₁ ) / (1 + λ ₁ + λ ₁ λ)
₂ ) = 0.897 Fifth speed (5TH): 1 / (1 + λ ₂ ) = 0.686 Reverse (REV) :−( 1 + λ ₁ ) / λ ₂ = −2.909, and the total gear spread is 5.19. Becomes The gear ratio step is 1.75 between the first and second speeds,
1.52 for the 3rd gear, 1.49 for the 3rd to 4th gear, 4th gear
1.31 is obtained during the fifth speed, and there is no reverse rotation on the way, so that a very desirable gear ratio step that crosses toward the higher speed side can be obtained.

Furthermore, in this gear train, the gear ratio λ ₁ of the reduction planetary gear G1 is set to, for example, 0.556 from the case of using all the 6th gears to 0.3 as described above for the 5th speed.
33, without changing the setting of the gear ratios λ _{2 and} λ ₃ of the planetary gear set G, between the two gears (3rd-4th) sandwiching the skipping gear (3.5th). Only the gear ratio step can be reduced. as a result,
When a good gear ratio step is set for the sixth gear ratio, the fifth gear can be achieved in a good gear ratio step while following the good gear ratio step, and the planetary gear set G and each engaging element are shared. The gear train can be shared by exchanging the reduction planetary gear G1, and the gear ratio λ of the reduction planetary gear G1 according to the present invention can be obtained.
₁ The degree of freedom of setting works effectively.

As described above in detail, according to the planetary gear device of the above-described embodiment, the sun gear S1 is formed integrally with the stator shaft 14 so that the meshing diameter of the sun gear S1 which must be fitted to the outer periphery of the input shaft 11 is required. Can be reduced to the maximum extent that the sun gear S1 maintains the strength originally required. Therefore, with this configuration, the allowable range for reducing the diameter of the sun gear S1 is widened, and when the meshing diameter of the ring gear R1 is fixed, the setting range of the gear ratio of the ring gear R1 and the sun gear S1 becomes large, and the gear ratio setting of the planetary gear device G1 In particular, since the influence of the change in the number of teeth of the sun gear S1 on the gear ratio is much greater than the change in the number of teeth of the ring gear R1, the gear ratio can be easily set in the direction of decreasing the gear ratio. When the gear ratio is constant, the diameter of the ring gear R1 can be easily reduced along with the diameter of the sun gear S1, and the size of the planetary gear device G1 can be reduced. Moreover, the sun gear S1
The number of components of the automatic transmission can also be reduced by integrating the motor with the stator shaft 14.

Further, in order to support the stator of the torque converter in the transmission case, the fixed portion of the stator shaft 14 which is stopped by the case and stopped in the axial direction is used for supporting the thrust force applied to the sun gear S1. Therefore, the processing of the end face of the boss portion 10b of the case for supporting the thrust force is not required, and the number of processing steps can be reduced.

Further, in the support relationship between the elements constituting the planetary gear device G1, the carrier C1 and the sun gear S
1, only the boss portion 10b of the transmission case is interposed, the support member path between the carrier C1 and the sun gear S1 is shortened, and the position accuracy is improved because the rotating member is not interposed in the middle.

Further, the stator shaft 14 and the input shaft 11
Between the bearings 15 arranged on the inner peripheral side of the sun gear S1.
Is fitted and supported on the side of the stator shaft 14 as shown in FIG. 4, because of the fitting of the input shaft 11 inserted into the stator shaft 14 (fitting from the right side in the figure),
While the inner diameter of the bearing 15 cannot be made smaller than the outer diameter of the input shaft 11, by fitting the bearing 15 into a concave groove 11 a formed on the outer periphery of the input shaft 11 as shown in FIG. Since the outer diameter of the bearing 15 can be reduced to the outer diameter of the input shaft 11, more precisely, to the outer diameter of the seal ring fitted around the input shaft 11, this configuration also reduces the diameter of the sun gear. It can be easier.

The present invention has been described in detail with reference to an embodiment and an example of application to a transmission for an FR vehicle. However, the present invention is not limited to this embodiment and the application, but is applied to a transaxle. It is naturally applicable to an automatic transmission for a front engine / front drive (FF) vehicle or a rear engine / rear drive vehicle adopting the form of
The present invention can be embodied with various concrete configurations changed within the scope of the items described in the individual claims.

[Brief description of the drawings]

FIG. 1 is an axial sectional view showing a planetary gear device of an automatic transmission according to an embodiment of the present invention together with related members.

FIG. 2 is a skeleton diagram showing a gear train of the automatic transmission according to the embodiment of the present invention.

FIG. 3 is a table showing an example of a gear train operation and a gear ratio setting of the embodiment.

FIG. 4 is an axial sectional view showing a planetary gear device of an automatic transmission according to the prior art of the present invention together with related members.

[Explanation of symbols]

 G1 reduction planetary gear (planetary gear device) S1 sun gear R1 ring gear P1 pinion gear C1 carrier G planetary gear set S3 small diameter sun gear (first element) S2 large diameter sun gear (second element) C2, C3 carrier (third element) R2, R3 ring gear (secondary gear) 4 elements) T1 First input path T2 Second input path C-1 First clutch C-2 Second clutch C-3 Third clutch B-1 First brake B-2 Second brake 10 Transmission case 10a Axial hole 10b Boss portion 11 Input shaft (rotary shaft) 11a Groove 14 Stator shaft 15 Bearing 19 Output shaft (output member)

 ──────────────────────────────────────────────────の Continuing on the front page (72) Inventor Hiroshi Kato 10 Takane, Fujii-machi, Anjo, Aichi Prefecture Inside Aisin AW Co., Ltd. 3J028 EA07 EA25 EA30 EB07 EB13 EB31 EB35 EB37 EB54 FA13 FB03 FC13 FC17 FC24 FC62 FD01 FD23 3J063 AB12 AB43 AB53 AB62 AC04 BA01 BB41 BB50 CD02 CB03 CD14 CD17 CD43 XA05 XA37

Claims (5)

[Claims] 1. A planetary gear device comprising a sun gear, a ring gear, a pinion gear meshing with the sun gear, a carrier rotatably supporting the pinion gear, and disposed on an outer periphery of a rotation shaft of an automatic transmission. A planetary gear device for an automatic transmission, wherein the planetary gear device is formed integrally with a stator shaft supported in an axial hole of a transmission case through a rotation shaft. 2. The rotation of the stator shaft and the axial movement thereof are stopped by the engagement of the stator shaft and the inner and outer peripheral surfaces of the axial hole by press-fitting into the axial hole of the transmission case, The planetary gear device for an automatic transmission according to claim 1. 3. The transmission case has a boss extending in the axial direction around the outer periphery of the axial hole, and the carrier is rotatably supported on the outer periphery of the boss. 3. The planetary gear device of the automatic transmission according to 2. 4. Between the stator shaft and a rotating shaft,
The bearing arranged on the inner peripheral side of the sun gear forming portion is fitted into a concave groove formed on the outer periphery of the rotating shaft.
The planetary gear device of the automatic transmission according to the above. 5. The automatic transmission according to claim 1, further comprising: a first input path having a first speed ratio directly connected to the input shaft with respect to a rotation of the input shaft; and a second input path having a speed reduced from the first speed ratio. A second input path having a speed ratio, a four-element planetary gear set,
A first clutch for transmitting rotation from the second input path to the first element of the planetary gear set, a third clutch for transmitting rotation to the second element, and a third element of the planetary gear set for transmitting rotation from the first input path; A second clutch for transmitting to the
The planetary gear device includes a first brake that locks a first element, a second brake that locks a third element, and an output member connected to a fourth element, wherein the planetary gear device reduces rotation from an input shaft. 5. A reduction planetary gear that outputs the input gear through the reduction planetary gear, an input path passing through the reduction planetary gear is defined as a second input path, and an input path from an input shaft that does not pass through the reduction planetary gear is defined as a first input path. The planetary gear device for an automatic transmission according to any one of the preceding claims.