JPH0949553A - Planetary gear device for automatic transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To ensure degree of freedom in designing gear ratio and decrease axial dimension, in a planetary gear device for automatic transmission wherein axial adjacent member is disposed at an adjacent position in the axial direction of a planetary gear train disposed on a rotary shaft, by eliminating an effect by raising a spline or interference with an adjacent member and forming a structure which surely receives thrust generated by a sun gear on the rotary shaft. SOLUTION: A sun gear (a) is spline-fitted onto a rotary shaft (d), and a bearing member (g) is disposed between the side surface on the opposite side to the axial adjacent member (f) of the sun gear (a) and the first carrier plate c1. On the axial adjacent member (f) side of the sun gear (a), a middle member (h) is disposed, whose one side surface facing the sun gear (a) almost meets the side surface outer diameter of the sun gear (a) and other side surface faces the stepped part d3 of the rotary shaft (d), on the slender shaft part d2 of the rotary shaft (d).

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a planetary gear device for an automatic transmission, and more particularly to a sun gear rotary shaft setting technique for widening a gear ratio of a planetary gear set to secure a degree of freedom.

[0002]

2. Description of the Related Art Conventionally, as a rotary shaft setting technique of a sun gear in a planetary gear device of an automatic transmission, a rotary shaft having a sun gear formed on the rotary shaft is disclosed in, for example, Japanese Patent Laid-Open No. 231505/1993. An integral type is known.

[0003]

However, in the above-described conventional rotary shaft-integrated sun gear, when the bearing lock nut is provided adjacent to the sun gear, the inner diameter of the nut is set to the outer diameter of the rotary shaft. Since it is necessary to pass through the shaft, it is limited even if the outer diameter of the rotating shaft (= outer diameter of the sun gear) is increased, and this limitation limits the setting of the number of teeth of the sun gear. Cannot be achieved.

Therefore, in order to achieve a wide gear ratio, it is necessary to adopt a method in which the sun gear and the rotary shaft are separated from each other and the sun gear is provided by spline fitting with respect to the rotary shaft.

However, when the sun gear is spline-fitted, the diameter of the sun gear must be increased so that the surface that receives the thrust force must be increased in diameter.
As described in the drawing of Japanese Patent No. 5 publication, when an attempt is made to receive a thrust force by the snap ring, when a large thrust force is generated, the snap ring having a weak supporting force may come off.

Therefore, for example, Japanese Patent Laid-Open No. 63-14584.
As described in Japanese Patent Laid-Open No. 7-76, it is conceivable to form a ridge portion integrally with the rotary shaft and receive the thrust force generated by the sun gear by the ridge portion.

However, when a spline for fitting the rotary shaft and the sun gear is formed, the spline cutter causes a cut-up. Therefore, when the axial position of the ridge is predetermined, the ridge has a large diameter. I can't.

That is, as shown in FIG. 8 and FIG. 9, if a ridge portion is provided in the vicinity of the spline, the escape portion of the cutter at the time of spline processing, so-called "cut-up", must be taken into consideration. If the diameter of the ridge cannot be increased and the sun gear has a large diameter, the thrust force cannot be reliably received. In Japanese Patent Laid-Open No. 63-145847, the reason why the small-diameter ridge portion can be applied is that the sun gear has a small diameter.

Further, in consideration of the "cut-up", if an attempt is made to provide a large-diameter ridge portion with a sufficient axial length from the spline, as described in Japanese Patent Laid-Open No. 5-231505. In the case of a structure where a bearing lock nut whose inner diameter is slightly larger than the rotating shaft is arranged as an adjacent member, the ridge and the bearing lock nut will interfere, so take the axial length to form the ridge. Even if set
Due to interference, it is not possible to increase the diameter of the ridge, so rather,
This leads to extension of the axial dimension of the automatic transmission.

The present invention has been made in view of the above problems. A first object of the present invention is to provide an axially adjacent member at a position adjacent to an axial direction of a planetary gear set arranged on a rotating shaft. In the planetary gear unit of the automatic transmission that is arranged, the gear ratio is set by a structure that eliminates the effects of rising splines and interference with adjacent members, and reliably receives the thrust force generated by the sun gear on the rotating shaft. It is to secure the degree of freedom and shorten the axial dimension.

A second object is to further reduce the axial dimension of the automatic transmission.

[0012]

In order to achieve the first object, a planetary gear device for an automatic transmission according to claim 1,
As shown in the claim correspondence diagram of FIG. 1 (a), the sun gear a
And a pinion gear b that meshes with the sun gear a and is axially supported by the pinion shaft i, and first and second carrier plates c1 and c2 that support one end side and the other end side of the pinion shaft i, A planetary gear set e arranged on the rotation axis d and the planetary gear set e are arranged adjacent to each other in the axial direction, the rotation axis d penetrates through, and an inner cylindrical shape having a smaller diameter than the outer diameter of the sun gear a. Axial adjacent member f having a portion f1
In the planetary gear device for an automatic transmission including :, the rotation shaft d has a spline portion d fitted to the sun gear a.
1, a thin shaft portion d2 formed on the axially adjacent member f side of the spline portion d1, a stepped portion d3 extending radially outward with the outer diameter of the thin shaft portion d2 being the lower end, and the stepped portion. a thick shaft portion d4 having an outer diameter at the upper end of d3, and the sun gear a
A bearing member g is arranged between the first carrier plate c1 and a side surface of the first carrier plate c1 opposite to the axially adjacent member f.
On the axially adjacent member f side of the sun gear a, one side surface facing the sun gear a substantially matches the side surface outer diameter of the sun gear a, and the other side surface is on the thin shaft portion d2 of the rotating shaft d. An intermediate member h facing the stepped portion d3 of the rotating shaft d is arranged.

In order to achieve the above-mentioned second object, the planetary gear device for an automatic transmission according to a second aspect of the present invention, as shown in the claim correspondence diagram of FIG. In the gear device, the axially adjacent member f is formed by denting an orthogonal corner portion connecting the side wall f2 facing the second carrier plate c2 supporting the other end side of the pinion shaft i and the inner cylindrical portion f1. A member having the interference avoidance connecting portion f3 is provided, and at least a part of the intermediate member h is arranged on the inner peripheral side of the interference avoiding connecting portion f3 of the axially adjacent member f.

[0014]

The operation of the first invention will be described.

The thrust force generated by the sun gear a on the side opposite to the axially adjacent member f is transmitted to the first carrier plate c1 via the bearing member g, and the thrust force toward the axially adjacent member f is generated. , The stepped portion d via the intermediate member h
3 is transmitted to the rotating shaft d.

Therefore, when the thrust force generated by the sun gear is applied to the conventional snap ring, the snap ring may come off when a large thrust force is generated, but the intermediate member h is securely attached to the stepped portion d3. Is supported by the intermediate member h even when a large thrust force is generated.
There is no danger of it coming off.

When the thrust portion directly formed on the shaft is directly subjected to the thrust force as in the prior art, it is necessary to consider the rise of the spline when forming the protrusion portion.
Since the intermediate member h is a separate body, it is not necessary to consider the rise of the spline when determining the outer diameter of the intermediate member h.

Further, in the case where the thrust portion directly formed on the shaft is directly subjected to the thrust force as in the conventional case, a sufficient distance from the spline is taken into consideration in order to make the protrusion portion have a large diameter by taking up the rising. In such a case, the outer diameter of the ridge portion is limited due to the interference with the adjacent member, but the intermediate member h can be set in the axial position independently of the spline, so that the interference with the axially adjacent member f is prevented. As long as the intermediate member h is set at the avoiding position, the axially adjacent member f does not serve as a factor that limits the outer diameter of the intermediate member h.

As a result, the diameter of the sun gear a can be increased, the degree of freedom in setting the number of teeth of the sun gear a increases, and the degree of freedom in setting the gear ratio of the planetary gear set e determined by the number of teeth of the sun gear a can be secured. .

The operation of the second invention will be described.

The axially adjacent member f is a member having an interference avoiding connecting portion f3 in which an orthogonal corner portion connecting the side wall f2 facing the second carrier plate c2 and the inner cylindrical portion f1 is recessed, and the intermediate member h. Since at least a part of the above is arranged on the inner peripheral side of the interference avoidance connecting portion f3 of the axially adjacent member f,
The axially adjacent member f and the intermediate member h overlap in the axial direction, and the axial size of the automatic transmission can be shortened.

[0022]

Embodiments of the present invention will be described below with reference to the drawings.

(First Embodiment) First, the structure will be described.

FIG. 2 is a skeleton diagram showing a power transmission mechanism of an automatic transmission to which the planetary gear device of the first embodiment corresponding to the inventions according to claims 1, 2 and 3 is applied.

This power transmission mechanism is used in the torque converter 1
0, a main transmission mechanism 1, an auxiliary transmission mechanism 2, and a final drive mechanism 3.

The torque converter 10 transmits the rotational force from the engine output shaft 12 to the input shaft 13.

The main transmission mechanism 1 is a torque converter 1
The input shaft 13 and the auxiliary transmission mechanism 2 to which the rotational force from 0 is transmitted
The intermediate output shaft 14 for transmitting the driving force to the first planetary gear set 1
5, a second planetary gear set 16, a front clutch 20, a rear clutch 22, a low and reverse brake 26, a band brake 28, and a low one-way clutch 30. The first planetary gear set 15 includes a sun gear S1, a ring gear R1, and a pinion carrier PC1 that supports a pinion gear P1 that meshes with both gears S1 and R1, and the second planetary gear set 16 includes , A sun gear S2, a ring gear R2, and a pinion carrier PC2 that supports a pinion gear P2 that meshes with both gears S2 and R2 at the same time. Each component is connected as shown. The band brake 28 has a servo apply pressure chamber SA for engaging it and a servo release pressure chamber SR for releasing it.

The subtransmission mechanism 2 includes a third planetary gear set 31.
(Planetary gear set e), a direct clutch 32 and a reduction brake 33. The third planetary gear set 31 meshes with the sun gear S3 (sun gear a), the ring gear R3, and both gears S3 and R3 at the same time, and is supported by the pinion shaft 55 (pinion shaft i) as a pinion gear P3 (pinion b). And the pinion shaft 55
Of the first carrier plate PC31 (first
Carrier plate c1) and second carrier plate PC
32 (second carrier plate c2) and a pinion carrier PC3. Ring gear R3
Can transmit the rotational force via the intermediate output shaft 14 and the gears 37 and 38. The sun gear S3 can be connected to the pinion carrier PC3 via the direct clutch 32 and can be fixed to the stationary portion by the reduction brake 33. A one-way clutch 36 is provided in parallel with the reduction brake 33. The pinion carrier PC3 is always connected to the output shaft 35.

The final drive mechanism 3 includes a drive pinion gear 39 provided on the output shaft 35, and a final drive gear 4 that meshes with the pinion gear 39.
0.

FIG. 3 is a diagram showing an operation logic table of each fastening element. The power transmission mechanism includes clutches 20, 22 and 3
2 and the brakes 26, 28 and 33 are operated in various combinations to operate the planetary gear sets 15, 16 and 3
The rotation state of each element of No. 1 can be changed, and thus the rotation speed of the output shaft 35 with respect to the rotation speed of the input shaft 13 can be changed. Clutch 20, 22 and 32
By operating the brakes 26, 28 and 33 and the one-way clutches 30 and 36 in a combination as shown in FIG. 3, it is possible to obtain the fourth forward speed and the first reverse speed.
The circle marks in FIG. 3 indicate the operating clutches and brakes.

FIG. 4 is a sectional view specifically showing the structure of the auxiliary transmission mechanism of the first embodiment. In FIG. 4, 31 is a third planetary gear set, 32 is a direct clutch, 33 is a reduction brake, and 35 is an output. Axis, 36 is a one-way clutch,
38 is a gear, 41 is a reduction shaft (rotating shaft d), 42
Is a bearing lock nut (adjacent member f in the axial direction), 43
Is a thrust bearing (bearing member g), 44 is a ring member (intermediate member h), 45 is a side cover, 46 is a casing member, 47 is a gear bearing, 48 is a transmission case, and 49 is a hub plate.

The bearing lock nut 42 has a third
The inner cylindrical portion 42a (inner cylindrical portion f1), which is arranged axially adjacent to the planetary gear set 31 and penetrates the reduction shaft 41 and has a diameter smaller than the outer diameter of the sun gear S3, faces the second carrier plate PC32. Side wall 42b (side wall f2)
And a concave portion 42c (interference avoidance connecting portion f3) which is formed by denting the orthogonal corner portion connecting the both 42a and 42b. A ring member 44 is provided on the inner peripheral side of the recess 42c.
Is arranged.

The reduction shaft 41 is a sun gear S3.
Spline part 41a (spline part d1) fitted with
And the bearing lock nut 4 of the spline portion 41a
The thin shaft portion 41b (thin shaft portion d2) formed on the second side, the stepped portion 41c (stepped portion d3) that extends radially outward with the outer diameter of the thin shaft portion 41b as the lower end, and the stepped portion It is configured to have a thick shaft portion 41d (thick shaft portion d4) whose outer diameter is the upper end of 41c.

In the sun gear S3, a thin shaft portion 41b of the reduction shaft 41 projects axially from the second carrier PC32 (second carrier c2) facing the bearing lock nut 42 toward the bearing lock nut 42 side.
Is formed with a cylindrical portion S31 (cylindrical portion a1).

On the opposite side of the sun gear S3 from the bearing lock nut 42, a first carrier plate PC31 extending through the thrust bearing 43 to the vicinity of the inner diameter of the sun gear S3 is arranged.

The ring member 44 is a reduction shaft 41 on the bearing lock nut 42 side of the sun gear S3.
The axial movement of the member is restricted by the contact between the stepped portion 41c and the sun gear facing side surface having a side surface outer diameter that substantially fits the side surface outer diameter of the sun gear S3. And a side surface facing the stepped portion.

Next, the operation will be described.

[Total End Play Adjustment] The ring member 44 is selected from among a plurality of ring members having different thicknesses in a plurality of stages in conformity with the measurement value regarding the total end play (a total end gap). It is a selected part.

The total end play adjustment will be described with reference to FIG.

First, the one-way clutch 36, the reduction brake 33, and the reduction shaft 41 having the hub plate 49 are assembled to the side cover 45 (B portion), and the joint surface A with the case 48 of the side cover 45 and the reduction. The distance L1 between the shaft 41 and the stepped portion 41c is measured.

On the other hand, when the case 48 is assembled up to the sun gear S3 (portion D), the distance L2 between the joint surface A of the side cover 45 with the case 48 and the thrust force transmitting surface of the sun gear S3 is measured.

Then, when the thickness of the ring member 44 is T, the thickness T of the ring member 44 is selected so that L2-L1-T = predetermined range.

After that, the gear 3 connected to the ring gear R3
8 is fixed to the casing member 46 by the bearing lock nut 42 via the gear bearing 47 (C portion), and after this C portion is press-fitted into the side cover 45,
The selected ring member 44 is arranged on the thin shaft portion 41b of the reduction shaft 41 and assembled to the case 48.

In this total end play adjustment,
Since the base point is set at the stepped portion 41c of the reduction shaft 41, the total end play can be easily measured.

[Transmission of Thrust Force Generated by Sun Gear] The sun gear S3 is spline fitted to the spline portion 41a of the reduction shaft 41. As shown in FIG. 6, this spline fitting includes large diameter matching and tooth surface matching, but in either case, the fitting is such that the sun gear S3 is allowed to move in the thrust direction.

The thrust force generated by the sun gear S3 making a leftward stroke in FIG. 4 is transmitted from the ring member 44 to the reduction shaft 41 via the stepped portion 41c, and further, the hub plate 49 and the one-way clutch 36. Via the side cover 45.

On the other hand, the thrust force generated by the sun gear S3 making a rightward stroke in FIG. 4 is transmitted to the first carrier plate PC31 via the thrust bearing 43, and further the direct clutch 32 → the output shaft 3 is transmitted.
5 → The case 48 receives it through a ball bearing (not shown).

The ring member 44 not only contributes to the transmission of the thrust force generated by the sun gear S3, but also when the thrust force is not acting on the sun gear S3, the gap amount set by the total end play adjustment is set. The axial movement of the reduction shaft 41 beyond the limit (rightward in FIG. 4) is restricted. Due to the axial movement restricting action of the reduction shaft 41, the interference between the hub plate 49 and the casing member 46 is prevented.

[Axial Layout of Third Planetary Gear Set] The bearing lock nut 42 forms a recess 42c in which an orthogonal corner connecting the inner cylindrical portion 42a and the side wall 42b is recessed. Since the ring member 44 is arranged on the circumferential side, the bearing lock nut 42 and the ring member 44 have an axially overlapping layout, and the axial dimension of the third planetary gear set 31 can be shortened.

Specifically, in this embodiment, Japanese Patent Laid-Open No. 5-231 is used.
No. 505, the reduction shaft 41 is spline-fitted with a separate sun gear S3 while keeping the same axial dimension as that of the third planetary gear set in which the sun gear is integrally formed on the reduction shaft. Changed to 3 planetary gear set 31. As a result, the degree of freedom in setting the gear ratio of the third planetary gear set 31 can be ensured, and the design change and component change of the auxiliary transmission mechanism 2 can be minimized.

Next, the effects will be described.

(1) In the planetary gear device of the automatic transmission in which the bearing lock nut 42 having the inner cylindrical portion 42a having a diameter smaller than the outer diameter of the sun gear S3 is arranged adjacent to the sun gear S3, the sun gear S3 is the reduction shaft 41. The first carrier plate PC31 is disposed on the side opposite to the bearing lock nut 42 of the sun gear S3 via the thrust bearing 43, and the reduction shaft 41 of the reduction shaft 41 is disposed on the side of the bearing lock nut 42 of the sun gear S3. On the thin shaft portion 41b, one side surface facing the sun gear S3 substantially coincides with the side surface outer diameter of the sun gear S3, and the other side surface is the stepped portion 41c of the reduction shaft 41.
Since the ring member 44 facing each other is arranged, the influence of rising of the spline and the interference with the bearing lock nut 42 is eliminated, and the reduction shaft 41 reliably receives the thrust force generated by the sun gear S3. Thus, it is possible to secure the freedom of setting the gear ratio and shorten the axial dimension.

The features of the structure in which the ring member 44 receives the thrust force generated by the sun gear S3 will be described in detail below.

When the conventional snap ring receives the thrust force generated by the sun gear, the snap ring may come off when a large thrust force is generated, but the ring member 44 is surely supported by the stepped portion 41c. Therefore, even if a large thrust force is generated, the ring member 44 does not come off.

When the thrust portion directly formed on the shaft is directly subjected to the thrust force as in the prior art, it is necessary to consider the rise of the spline when forming the protrusion portion, but the ring member 44 is a separate member. Therefore, when determining the outer diameter of the ring member 44, it is not necessary to consider the rise of the spline.

In the case where the thrust portion directly formed on the shaft is directly subjected to the thrust force as in the conventional case, a sufficient distance from the spline is taken in consideration of the upsurge so that the protrusion portion has a large diameter. In this case, the outer diameter of the ridge is limited due to the interference with the adjacent member, but the ring member 44 can be set in the axial direction independently of the spline, so that the ring member 44 can be set at the position where the interference with the bearing lock nut 42 is avoided. As long as the ring member 44 is set, the bearing lock nut 42 does not become a factor that limits the outer diameter of the ring member 44.

As a result, the diameter of the sun gear S3 can be increased, the degree of freedom in setting the number of teeth of the sun gear S3 is increased, and the third planetary gear set 31 is determined by the number of teeth of the sun gear S3 and the number of teeth of the ring gear R3. The degree of freedom in setting the gear ratio can be secured.

(2) The bearing lock nut 42 is a member having a recess 42c for avoiding interference with the ring member 44, and the ring member 44 is the bearing lock nut 4
Since it is arranged on the inner peripheral side of the second concave portion 42c, the auxiliary transmission mechanism 2
It is possible to reduce the axial dimension of the.

(Second Embodiment) FIG. 7 is a sectional view specifically showing the structure of the auxiliary transmission mechanism of the second embodiment.

In the auxiliary transmission mechanism of the second embodiment, the axial oil passage 50 provided in the reduction shaft 41, the inner cylindrical portion S31 of the sun gear S3 and the thin shaft portion 41b of the reduction shaft 41 are provided. The oil sump 51 provided and the oil sump 51
A radial oil passage 52 is provided that communicates with the axial oil passage 50. Further, the inner cylindrical portion S3 of the sun gear S3
1 includes a pinion gear P3 and a second carrier plate PC
A washer 53 between the two and 32 is provided with a through hole 54 through which the oil in the oil sump 51 is discharged.

In addition, the sun gear S3 is provided with helical teeth having a tooth axis direction for transmitting the thrust force to the ring member 44 side during drive traveling and transmitting the thrust force to the thrust bearing 43 side during coasting traveling. There is.

Since the other structures are the same as those of the first embodiment (FIG. 4), the same reference numerals are given to the corresponding structures and the description thereof will be omitted.

Next, the operation will be described.

[Lubrication] The oil supplied from the axial oil passage 50 of the reduction shaft 41 is discharged to the oil sump 51 via the radial oil passage 52.

During coasting, Sun Gear S3
Transmits the thrust force to the thrust bearing 43 and moves to the thrust bearing 43 side (the state of FIG. 8), the oil in the oil sump 51 slightly leaks from the gap between the sun gear S3 and the ring member 44. However, the remaining oil is discharged from the through hole 54 toward the washer 53 to lubricate the washer 53.

On the other hand, when driving, the sun gear S3
Transmits the thrust force to the ring member 44 and moves to the ring member 44 side, there is no gap between the sun gear S3 and the ring member 44, and more oil is discharged toward the washer 53. Lubricate the washer 53.

The other operation is the same as that of the first embodiment, and the description thereof is omitted.

Next, the effect will be described.

In addition to the effects of the first embodiment device, the following effects are achieved.

(3) The washer lubrication structure having the axial oil passage 50, the oil sump 51, the radial oil passage 52, and the through hole 54 is employed, and the sun gear S3 has the ring member 4 when driving.
The thrust force is transmitted to the 4 side, and the helical teeth are set so as to transmit the thrust force to the thrust bearing 43 side during coasting. Therefore, the oil released to the inner circumference of the inner cylindrical portion S31 of the sun gear S3 is caught. It is possible to supply a larger amount of oil to the washer 53 during drive traveling, which is particularly frequently used, without providing a weir or the like to increase the cooling effect.

Although the embodiments have been described with reference to the drawings, the specific configuration is not limited to the embodiments, and modifications and additions within the scope of the present invention are included in the present invention. Be done.

For example, in the embodiment, the third transmission of the auxiliary transmission mechanism 2 is used.
Applies to planetary gear set 31, bearing lock nut 42
However, the application range is not limited to the embodiment as long as it is an automatic transmission in which a planetary gear device is used and some members are arranged at positions adjacent to each other in the axial direction.

In the embodiment, an example of the ring member 44 having a rectangular cross section is shown as the intermediate member, but as shown in FIG.
It may be an intermediate member having an L-shaped cross section or an intermediate member having another cross-sectional shape.

[0074]

According to the first invention of claim 1,
In a planetary gear device of an automatic transmission in which an axially adjacent member is arranged at a position adjacent to an axial direction of a planetary gear set arranged on a rotary shaft, a sun gear is spline-fitted to a rotary shaft, and the sun gear is axially adjacent. The side opposite to the member and the first
A bearing member is arranged between the carrier plate and
On the side adjacent to the sun gear in the axial direction, on the thin shaft portion of the rotary shaft, one side surface facing the sun gear substantially matches the outer diameter of the side surface of the sun gear, and the other side surface faces the stepped portion of the rotary shaft. Since the intermediate member is installed, the influence of rising splines and interference with adjacent members is eliminated, and the thrust force generated by the sun gear is reliably received by the rotating shaft. The effect that the degree of freedom can be secured and the axial dimension can be shortened can be obtained.

According to a second aspect of the present invention, in the planetary gear device of the automatic transmission according to the first aspect, the second carrier plate for supporting the axially adjacent member on the other end side of the pinion shaft. A member having an interference avoidance connecting part in which an orthogonal corner connecting the side wall and the inner cylindrical part facing each other is recessed, and at least a part of the intermediate member is an inner peripheral side of the interference avoiding connecting part of the axially adjacent member. In addition to the effect of the first aspect of the invention, the axial size of the automatic transmission can be further shortened.

[Brief description of drawings]

FIG. 1 is a claim correspondence diagram showing a planetary gear device of an automatic transmission according to the present invention.

FIG. 2 is a skeleton diagram showing a power transmission mechanism of an automatic transmission to which the planetary gear device of the first embodiment is applied.

FIG. 3 is a diagram showing an engagement logic table for obtaining a forward four-speed reverse one-speed shift in the automatic transmission according to the first embodiment.

FIG. 4 is a sectional view specifically showing a configuration of an auxiliary transmission mechanism of the first embodiment.

FIG. 5 is a diagram illustrating total end play adjustment for selecting a ring member in the auxiliary transmission mechanism of the automatic transmission according to the first embodiment.

6A and 6B are diagrams showing two modes in the case of spline-fitting a gear.

FIG. 7 is a sectional view specifically showing a configuration of an auxiliary transmission mechanism of a second embodiment.

FIG. 8 is a diagram showing a structure that receives a thrust force generated in a conventional sun gear.

FIG. 9 is a diagram illustrating a state in which the outer diameter of a protruding portion integrally formed with a conventional rotary shaft is limited by the cutting up of a spline cutter.

[Explanation of symbols]

 a sun gear a1 cylindrical part b pinion gear c1 first carrier plate c2 second carrier plate d rotary shaft d1 spline part d2 thin shaft part d3 stepped part d4 thick shaft part e planetary gear set f axial direction adjacent member f1 inner cylindrical shape Part f2 Side wall f3 Interference avoidance connecting part g Bearing member h Intermediate member i Pinion shaft

Claims (2)

[Claims] 1. A sun gear, a pinion gear that meshes with the sun gear and is axially supported by a pinion shaft, and first and second ends that support one end side and the other end side of the pinion shaft.
A planetary gear set having a carrier plate and arranged on a rotation shaft, and the planetary gear set are arranged adjacent to each other in the axial direction, the rotation shaft penetrates, and an inner diameter smaller than the outer diameter of the sun gear. In a planetary gear device of an automatic transmission including an axially adjacent member having a cylindrical portion, the rotating shaft is formed on a spline portion fitted to the sun gear, and on the axially adjacent member side of the spline portion. A thin shaft portion, a stepped portion that extends radially outward with an outer diameter of the thin shaft portion as a lower end, and a thick shaft portion having an outer diameter at the upper end of the stepped portion, the axial direction of the sun gear A bearing member is disposed between the first carrier plate and the side surface on the side opposite to the adjacent member, and on the adjacent member side in the axial direction of the sun gear, on the thin shaft portion of the rotary shaft, on the sun gear. One of the opposite sides is approximately the same as the outside diameter of the sun gear. A planetary gear device for an automatic transmission the other side, characterized in that the intermediate member facing the stepped portion of the rotary shaft is disposed. 2. The planetary gear device for an automatic transmission according to claim 1, wherein the axially adjacent member faces the second carrier plate that supports the other end of the pinion shaft, and the inner cylindrical portion. And a member having an interference avoidance connecting part in which an orthogonal corner part connecting with is recessed, and at least a part of the intermediate member is arranged on an inner peripheral side of the interference avoiding connecting part of the axially adjacent member. Characteristic automatic transmission planetary gear device.