JP2003130149A - Automatic transmission for vehicle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a multi-stage gear train which has superior gear ratio steps by inputting a reduced rotation to a ravigneaux type four-element planetary gear set. SOLUTION: The automatic transmission for a vehicle has a ravigneaux type four element planetary gear set G1, a reduction planetary gear set G3, clutches C-1 and C-2 for controlling the ravigneaux type four-element planetary gear set G1 and the reduction planetary gear set G3, brakes B-1 and B-2, and a means B-3 for inputting the reduced rotation from the reduction planetary gear set G3 to the planetary gear set G1. A long pinion of the planetary gear set is a stepped pinion P1, P2, having a large diameter portion P1 for engaging with a ring gear R1 and a sun gear S1, and a small-diameter portion P2 for engaging with a short pinion P2' engaging with a sun gear S2. According to this method, the step of gear ratios between the reduction steps on both sides of the reduction stage, achieved by inputting the reduced rotation is widened, and a narrow interval in gear ratio steps between specific reduction stages is eliminated. As a result, the gear ratio steps among all the reduction stages become proper.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vehicle automatic transmission, and more particularly to a gear train structure for an automatic transmission that achieves multiple gears.

[0002]

2. Description of the Related Art Automatic transmissions for vehicles tend to have multiple stages because of demands for improved fuel economy and drivability. In the flow of such a technique, Japanese Patent No. 3102046 discloses a technique of adding a deceleration input planetary gear set to a four-element planetary gear set to achieve sixth forward speed. The four-element planetary gear set in this technology is a Ravigneaux type gear set that is often used to achieve a fourth speed gear.

In this gear train, input rotation is input to the small-diameter sun gear and carrier of the Ravigneaux type gear set via the first clutch, and reduced rotation is input to the large-diameter sun gear via the planetary gear set for deceleration input, and to the carrier. By adopting a configuration in which a large-diameter sun gear is appropriately locked in the case, a speed change rotation of each gear is output to the ring gear.

[0004]

By the way, in order to change the planetary gear set used in the fourth speed to the sixth speed according to the method of inputting the decelerated rotation as in the above-mentioned prior art, the second speed between the four speed steps is set. During the third speed, it is necessary to add two new gears between the third speed and the fourth speed. This
The operation will be described with reference to a velocity diagram (a diagram in which a velocity ratio is plotted in the vertical axis direction and lines representing the respective elements are arranged in the horizontal axis direction at intervals according to the gear ratio) that directly represents the operation of the gear train. Referring to the velocity diagram shown in FIG. 7, in the relationship between the Ravigneaux type gear set G2, which is the basis of the prior art, and the input / output thereto, the input rotation input by the engagement of the second clutch C2 with the third sun gear S3 is performed. On the other hand, by locking the double-row planet carrier PC2 with the third brake B3, the first speed (1st), and by locking the second sun gear S2 with the second brake B2, the second speed (2nd), the double-row The input rotation is input to the planet carrier PC2 by the engagement of the first clutch C1, and the third rotation (3rd) is directly connected, and the input rotation is input to the double-row planet carrier PC2 by the engagement of the first clutch C1. Second sun gear S2 to second brake B
4th speed (4th) of overdrive by locking at 2
Is achieved. On the other hand, in order to input the decelerated rotation and add the gear stage, as shown by the arrow in the figure, the second speed (2n
Two new gears will be added between d) and the third speed (3rd) and between the third speed (3rd) and the fourth speed (4th).

However, the planetary gear set used in the fourth speed has a gear ratio step suitable for the fourth speed by itself (see the speed ratio of each shift stage in FIG. 5).
If the gear stage (gear stage indicated by the arrow) is added in the form of interrupting between the second and third speeds and the third and fourth speeds as described above, the additional gear speed is added. And the gear ratio step between the gear steps that sandwich it and the gear ratio become clogged, and 6
There is a problem that the gear ratio step when speeding up is not likely to be good.

Therefore, the present invention provides an automatic transmission for a vehicle, which realizes a good multistep of gear ratio steps, while using a combination of a four-element planetary gear set and a reduction planetary gear set as in the prior art. With the goal.

[0007]

The above-mentioned object is defined in claim 1.
As described in 1, the first sun gear (S1), the ring gear (R1), the first pinion gear (P1) meshing with the first sun gear and the ring gear, and the first sun gear (P1) so as to rotate integrally with the first pinion gear. A second pinion gear (P2), which has a smaller diameter than the first pinion gear, and a third pinion gear (P3 ′) which meshes with the second pinion gear.
A second sun gear (S2) that meshes with the third pinion gear, a carrier (C) that supports the first to third pinion gears, and a reduction planetary gear set (G3) that decelerates and outputs the input rotation. And a first clutch (C-1) for transmitting input rotation to the first sun gear,
A second clutch (C-2) for transmitting the input rotation to the ring gear and a first brake (B-1) for locking the ring gear, and a second brake (B- for locking the second sun gear). 2) and means for transmitting the decelerated rotation output from the deceleration planetary gear set to the second sun gear (B-
3) and an output member (19) connected to the carrier.

In the above structure, the means for transmitting the decelerated rotation includes the input element (S3) for input rotation in the deceleration planetary gear set, as set forth in claim 2.
Reaction force element (C3) for deceleration rotation output element (R3)
Can be a third brake (B-3) that locks.

In this case, the reduction planetary gear set has a third sun gear (S3) as described in claim 3.
A second ring gear (R3), a fourth pinion gear (P3 ′) meshing with the third sun gear, and a fifth pinion gear (P3 ′) meshing with both the fourth pinion gear and the second ring gear (R3). P3) and a second carrier that supports the fourth and fifth pinion gears, and a double pinion gear set can be provided.

In each of the above-mentioned configurations, the automatic transmission for a vehicle has the following features: when the input rotation input to the first sun gear is caused by the engagement of the first clutch,
The first gear is engaged by engaging the ring gear to engage the first gear, the second brake is engaged to engage the second sun gear to engage the second gear, and the second gear is engaged by means for transmitting decelerated rotation. Third speed is achieved by inputting decelerated rotation to the sun gear, and fourth speed is achieved by inputting input rotation to the ring gear due to engagement of the second clutch, and input of input rotation to the ring gear due to engagement of the second clutch. In response to the input of the decelerated rotation to the second sun gear due to the engagement of the means for transmitting the decelerated rotation, the fifth speed, and the second due to the engagement of the second brake.
It is effective to have a configuration in which the sixth gear is achieved by locking the sun gear.

[0011]

In the structure of the present invention, by adopting the stepped pinion gear in which the first pinion gear and the second pinion gear as described above have a diameter difference,
Considering the 4th speed achieved by inputting only the input rotation to the planetary gear of the element, the 2nd speed is set to the low gear,
The fourth speed can be made high geared, and as a result, the gear ratio step between the second speed and the third speed of the fourth speed and the gear ratio step between the third speed and the fourth speed is increased. Then, since two gears are newly added thereto by the input of the decelerated rotation of the deceleration planetary gear set, the sixth speed can be achieved with well-balanced steps as a whole.

[0012]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Next, embodiments of the present invention will be described with reference to the drawings. As shown in FIG. 1 as a skeleton structure of a gear train of an automatic transmission for a vehicle, this gear train is composed of a four-element planetary gear set G1 arranged side by side on the outer circumference of an input shaft 11 and a reduction planetary gear set for inputting decelerated rotation thereto. G3 and two clutches (C-1, C-2) as engaging elements for controlling these,
An output member, which is composed of three brakes (B-1, B-2, B-3) and an additional one-way clutch (F-1) and is connected to the carrier C, is used as a parallel shaft output counter gear 19. , In the form of a horizontal transaxle.

The four-element planetary gear set G includes the first
Sun gear S1, ring gear R1, first sun gear S1 and first pinion gear P meshing with ring gear R1.
1, a second pinion gear P2 that is connected to the first pinion gear P1 so as to rotate integrally, and has a diameter smaller than that of the first pinion gear P1, a third pinion gear P2 ′ that meshes with the second pinion gear P2, and a third pinion gear P2 ′. Pinion gear P2 '
The second sun gear S2 that meshes with the carrier and the carrier C that supports the first to third pinion gears. In this embodiment, the deceleration planetary gear set G3 that decelerates and outputs the input rotation (in this specification, non-decelerated input rotation is simply referred to as input rotation) is the third sun gear S.
3, a second ring gear R3, a fourth pinion gear P3 ′ meshing with the third sun gear S3, a fifth pinion gear P3 ′ meshing with the second ring gear R3
The double pinion gear set including the pinion gear P3 and the second carrier C3 that supports the fourth and fifth pinion gears.

Regarding each engaging element, the first clutch (C-1) is a multi-plate clutch for transmitting the input rotation to the first sun gear S1, and the second clutch (C-2) is for the ring gear R1. The multi-plate clutch that transmits the input rotation and the first brake (B-1) connect the ring gear R1 to the transmission case 1
Multi-disc brake that locks to 0, second brake (B-2)
Is a multi-plate brake that locks the second sun gear S2 to the transmission case 10. Also, the second sun gear S2
In this embodiment, the means for transmitting the decelerated rotation output by the deceleration planetary gear set G3 to the third embodiment has a band-shaped third brake (B-3 that locks the second carrier C3 as a reaction element to the transmission case 10). It is said that.

In the case of this automatic transmission, the relationship between the engagement / release of each engagement element and the achieved shift speed is as shown in the engagement chart of FIG. In this table, the clutch, brake and one-way clutch engagement in each range P, R, N, D of automatic transmission is indicated by a circle (O in parentheses is an engagement for achieving engine braking).

FIG. 3 is a velocity diagram showing the relationship between the shift speed achieved by the engagement of each clutch, the brake and the one-way clutch and the rotational speed ratio of each shift element at that time. In this velocity diagram, the vertical axis represents the rotational speed ratio of each rotary element, and the horizontal axis represents the position of each rotary element corresponding to the gear ratio of the rotary elements that mesh with each other, and represents the behavior of each rotary element. In the array represented by the velocity diagram, each rotating element is
In the four-element planetary gear set G1, the first sun gear S1 is arranged at one end (left end in the drawing) of the horizontal axis, and from there (in the right direction in the drawing), the carrier C, the ring gear R1, and the second The sun gears S2 are arranged side by side, the first sun gear S1 is an input-only element for input rotation, the carrier C is an output element, the ring gear R1 is an input / reaction element for input rotation, and the second sun gear S2 is an input / reaction for decelerated rotation. It is considered to be a force element. Further, in the reduction planetary gear set G3, the second carrier C3 is arranged at one end (the left end in the drawing) of the horizontal axis, and from there (in the right direction in the drawing), the second ring gear R3, the third The sun gears S3 are arranged side by side, the carrier C3 is a reaction force element, the ring gear R3 is an output element, and the sun gear S3 is an input element.

As can be seen by referring to FIGS. 2 and 3 together, in this gear train, the first clutch (C-1) is used.
With respect to the input rotation input to the first sun gear S1 due to the engagement of the ring gear R, the one-way clutch (F-1) is locked instead of the engagement of the first brake (B-1).
The first brake (1st) and the second brake (B
-2) locks the second sun gear S2 to the second speed (2nd), and the third brake (B-3) engages the second sun gear S2 to input the decelerated rotation to the third speed. The fourth speed (4t) due to the input rotation input to the ring gear R1 due to the engagement of the second clutch (C-2) at the third speed (3rd).
h) is achieved, and in response to the input rotation input to the ring gear R1 due to the engagement of the second clutch (C-2), to the second sun gear S2 due to the engagement of the third brake (B-3). The fifth speed (5th) is achieved by the input of the decelerated rotation, and the sixth speed (6th) is achieved by the engagement of the second brake (B-2) to lock the second sun gear S2. The reverse (R) is the third brake (B-3) when the ring gear R1 is locked by the engagement of the first brake (B-1).
This is achieved by the input of the decelerated rotation to the second sun gear S2 by the engagement of.

The first speed (1s
In t), the lock of the one-way clutch (F-1) is used instead of the engagement of the first brake (B-1) because the first brake (B- during the 1-2 upshift).
In order to eliminate the release operation of 1) and the operation of exchanging the third brake engagement, the ring gear R1 is locked by receiving the reaction force in the reverse rotation direction in the driving state of the first speed, and automatically by the shift to the second speed. Free one-way clutch (F-
The operation of 1) is used, and in terms of achievement of the shift speed, it corresponds to the engagement of the first brake (B-1).

In the gear train having such a structure,
The number of teeth of the first sun gear S1 is Z _{S 1} , the number of teeth of the second sun gear S1 is
The number of teeth of 2 is Z _{S 2} , the number of teeth of the third sun gear S3 is Z _{S 3} , the number of teeth of the ring gear R1 is Z _{R 1} , the number of teeth of the second ring gear R3 is Z _{R 3} , and the first pinion gear P1. The number of teeth of Z _{P 1} , the number of teeth of the second pinion gear _{P 2} is Z _{P 2} ,
Let Z _{P 3 be the} number of teeth of the fifth pinion gear _{P 3} , and Z _{P 1}
/ Z _{S 1} = A, Z _{P 1} / Z _{R 1} = B, Z _{P 2} / Z _{S 2} =
Assuming that C and Z _{S 3} / Z _{R 3} = D, the gear ratio of each gear is as follows: 1st speed (1st): (A + B) / B = (Z _{R 1} /
Z _{S 1} ) +1, 2nd speed (2nd): (A + C) / C = (Z _{S 2} /
Z _{S 1} ) (Z _{P 1} / Z _{P 2} ) +1, 3rd speed (3rd): (C + A) / (C + AD) 4th speed (4th): 1, 5th speed (5th): (C-B) / (C-BD), 6th speed (6th): (C-B) / C = 1- (Z _{S 1} / Z
_{R 1} ) (Z _{P 1} / Z _{P 2} ), Rivalle (R) :( CB) / BD.

For example, Z _{S 1} = 38, Z _{S 2} = 32, Z
_{S 3} = 48, Z _{R 1} = 94, Z _{R 3} = 96, Z _{P 1} = 2
8, when Z _{P 2} = 22 and Z _{P 3} = 20, the gear ratio of each gear is 3.473 for the first speed, as shown in FIG.
The second speed is 2.072, the third speed is 1.349, the fourth speed is 1, the fifth speed is 0.723, the sixth speed is 0.567, the reverse is 2.616, and the gear ratio step is 1.68 between the 1st and 2nd speeds, 1.54 between the 2nd and 3rd speeds, 1.34 between the 3rd and 4th speeds, 1.38 between the 4th and 5th speeds, and between the 5th and 6th speeds Becomes 1.28.

The operation of each gear stage of this gear train is such that, at the first speed, the ring gear R1 has a fixed speed ratio of 0 with respect to the rotation of the first sun gear S1 at a speed ratio of 1, and an intermediate speed. Ratio (the reciprocal of the gear ratio according to the definition above,
The rotations (the same applies to other gears below) are output to the carrier C and transmitted to the counter gear 19. in this case,
The second sun gear S2 is decelerated and reversely rotated, and the second ring gear R3 connected thereto is also rotated at the same speed, so that the input shaft 11
The second carrier C3 rotates in the reverse direction at a high speed because of the relationship with the rotation at the speed ratio 1 of the third sun gear connected to.

Next, at the second speed, the second sun gear S2 has a fixed speed ratio of 0 with respect to the rotation of the first sun gear S1 at a speed ratio of 1, and the rotation of the intermediate speed ratio has a carrier C.
Is transmitted to the counter gear 19. In this case, the ring gear R1 is decelerated and rotated at a speed ratio intermediate between the second speed rotation and the speed ratio 0, and the second ring gear R3 connected to the second sun gear S2 is fixed and connected to the input shaft 11. Due to the relationship with the rotation of the sun gear of No. 3 at the speed ratio of 1, the second carrier C3 is reversely rotated at substantially the same speed as the input rotation.

At the third speed, the second sun gear S2 enters the decelerated rotation input state from the second ring gear R3 with respect to the rotation of the first sun gear S1 at the speed ratio 1, and the intermediate speed ratio The rotation is output to the carrier C and the counter gear 1
9 is transmitted. In this case, the ring gear R1 decelerates and rotates at a speed ratio intermediate between the third speed rotation of the carrier C and the decelerated rotation of the second sun gear S2, and the second carrier C3 supports reaction force for decelerated rotation output. The speed ratio in the fixed state is 0.

At the 4th speed, the ring gear R1 also rotates at the speed ratio of 1 with respect to the rotation of the first sun gear S1 at the speed ratio of 1, so that in the four-element planetary gear set, all transmission elements rotate at the same speed. Then, the rotation having the speed ratio of 1 is output to the carrier C and transmitted to the counter gear 19. In this case, the second ring gear R3 connected to the second sun gear S2 also rotates at a speed ratio of 1 and has the same speed as the third sun gear S3, so the reduction planetary gear set G3.
Also, the three elements are in a direct connection state with the same speed rotation.

At the 5th speed, the ring gear R1 is rotated at a speed ratio of 1 instead of the first sun gear S1 and the second sun gear S2 is rotated at a speed ratio of deceleration rotation, so that the carrier C is accelerated. This rotation is transmitted to the counter gear 19. In this case, the first sun gear S1 idles at a speed ratio further increased than that of the carrier C. The deceleration planetary gear side is the same as in the third speed.

At the 6th speed, since the second sun gear S2 is fixed at the speed ratio 0 with respect to the rotation of the ring gear R1 at the speed ratio 1 as in the 5th speed, the carrier C is at the 5th speed. The rotation speed is further increased, and this rotation is transmitted to the counter gear 19. In this case, the first sun gear S1 idles at a higher speed ratio that is further increased than that of the carrier C. The deceleration planetary gear side is the same as in the second speed.

During reverse, the second sun gear S2
Rotates at a speed ratio of decelerated rotation, the ring gear R1 rotates at a fixed speed ratio of 0, and the carrier C becomes reverse rotation of deceleration, and this rotation is transmitted to the counter gear 19. In this case, the first sun gear S1 idles at a speed ratio increased by the carrier C. The deceleration planetary gear side is the same as in the third speed and the fifth speed.

As can be seen from the above description of the operation, in this gear train, the first sun gear S1 is extremely high at the time of idling at the fifth speed and the sixth speed where the first sun gear S1 does not participate in power transmission, especially at the sixth speed which is the highest speed. It will rotate at a speed ratio. Referring to the skeleton in FIG. 1 in this state, the first clutch (C-1) for transmitting the input rotation to the first sun gear S1.
Means that the speed ratio on the clutch hub side connected to the first sun gear S1 side is several times higher than the rotation of the speed ratio 1 on the clutch drum side connected to the input shaft 11 in the released state. To do. In such a state, the lubricating oil is spattered outward by the centrifugal force on the clutch hub side, which may cause insufficient lubrication of the friction material when the clutch is engaged. So, in this form,
Measures are taken to prevent insufficient lubrication when the clutch is engaged due to oil scattering.

Referring to the cross section shown in FIG. 4, as a countermeasure, the first sun gear S of the first clutch (C-1) is used.
The outer periphery of the hub 13 connected to 1 and the inner periphery of the drum 12 connected to the input shaft 11 are frictionally supported by the drum 12 on the side of the friction material disk 14 of the members constituting the frictional engagement member spline-engaged and coupled. The separator plate 15 side is engaged with and supported by the hub 13. This arrangement is the reverse of the normal clutch friction engagement member arrangement in which the separator plate is supported on the drum and the friction material disc is supported on the hub. By adopting such a configuration, the speed ratio on the friction material disk 14 side that needs to retain lubricating oil can be maintained at the speed ratio 1 of the input rotation even when the clutch is released. Can be resolved.

Further, in order to cope with the high speed rotation of the first sun gear S1 as described above, the first sun gear S1 is connected to the input shaft 1
As for the bearing 16 supported by No. 1, a bearing having a high supporting force that enables high-load support is also arranged. Since the other members shown in FIG. 4 are not particularly related to the features of the present invention, the members corresponding to the members shown by the skeleton in FIG.

As described in detail above, the first embodiment
According to the gear train, the first pinion gear P1 and the second pinion gear P1
Stepped pinion gear with a diameter difference from the pinion gear 2 of
By adopting the ears, a four-element planetary gear set
4th speed achieved by inputting only input rotation to G1
, The second gear is changed to the low gear (the first gear according to the definition above).
Second gear ratio formula (Z_{S 2}/ Z_{S 1}) (Z_{P 1}/ Z_{P 2})
(Z in +1_{P 1}/ Z _{P 2}) Term in Z_{P 1}> Z_{P 2}age
To increase the gear ratio by increasing the
High geared (similar to the sixth gear ratio according to the previous definition)
Formula 1- (Z_{S 1}/ Z_{R 1}) (Z_{P 1}/ Z_{P 2}) In (Z
_{P 1}/ Z_{P 2}) Term in Z_{P 1}> Z_{P 2}As big
It is possible to reduce the gear ratio), and as a result,
The gear ratio step between the second speed and the third speed and between the third speed and the fourth speed.
Spreads. And there, a new deceleration planetary
Two gears are set by input of decelerated rotation of gear set G3.
Since it is an additional configuration, it has a good balance as a whole.
You can achieve 6th gear with a step.

In the first embodiment, the reduction planetary gear set G3 is a double pinion gear set, but the reduction planetary gear set G3 may be a simple planetary gear set. FIG. 5 is a skeleton showing the gear train of the second embodiment having such a configuration.

As shown in the figure, the reduction planetary gear set G3 in this embodiment includes a third sun gear S3 and a second sun gear S3.
Is a simple planetary gear set in which the fifth pinion gear P3 meshes with the ring gear R3. In the configuration using this simple planetary gear set, various connection relationships can be adopted depending on which of the three elements is used as the input element, the output element, or the reaction element.
Similar to the first embodiment, the reduction planetary gear set G
Under the premise that the input and output of 3 are rotated in the same direction and the third sun gear S3 is an input element that is always connected to the input shaft 11, contrary to the first embodiment, the second carrier C3 is connected to the second carrier C3. It is rational to adopt a connection relationship in which the output element connected to the sun gear S2 and the second ring gear R3 are reaction force elements that can be locked to the transmission case 10 via the third brake (B-3). .

Even if such a simple planetary gear set is used as a reduction planetary gear set G3,
By setting the gear ratio of the third sun gear S3 and the second ring gear R3, it is possible to achieve the same reduction gear ratio as in the first embodiment. Therefore, the favorable setting of the gear ratio step between the 6th speed shift stages, which is achieved by the 4-element planetary gear set G1, is possible as in the case of the first embodiment.

Further, in the structure in which the reduction planetary gear set G3 is a double planetary gear set as in the first embodiment, the means for transmitting the decelerated rotation output by the reduction planetary gear set G3 to the second sun gear S2 may be changed. It is possible. FIG. 6 shows a gear train of a third embodiment exemplifying such a configuration with a skeleton similar to that of FIG.

In this embodiment, the means for transmitting the decelerated rotation is a third clutch (C-3) instead of the third brake (B-3) of the first embodiment. In this way, when the input of the decelerated rotation to the second sun gear S2 is controlled by the clutch, the deceleration planetary gear set G3 can be disengaged by the clutch, so that the second carrier C can be disengaged.
3 is fixed to the transmission case 10 at all times. As a matter of course, the second brake (B-2) that locks the second sun gear S2 to the transmission case 10 includes the third clutch (C-
3) so that the second sun gear S2 can be fixed at the time of release, the third clutch (C-
3) It is arranged on the downstream side.

Although the present invention has been described in detail above with reference to a typical embodiment in a specific gear train, the idea of the present invention is not limited to the illustrated gear train, but a planetary gear composed of four elements. It is widely applicable to a gear train that inputs decelerated rotation to a set.

[Brief description of drawings]

FIG. 1 is a skeleton diagram showing a gear train of an automatic transmission for a vehicle according to a first exemplary embodiment of the present invention.

FIG. 2 is an engagement chart showing an engagement / disengagement relationship between each shift stage and each engagement element achieved by the gear train of the first embodiment.

FIG. 3 is a velocity diagram of the gear train of the first embodiment.

FIG. 4 is a partial cross-sectional view of the gear train of the first embodiment.

FIG. 5 is a skeleton diagram showing a gear train of an automatic transmission for a vehicle according to a second exemplary embodiment of the present invention.

FIG. 6 is a skeleton diagram showing a gear train of an automatic transmission for a vehicle according to a third exemplary embodiment of the present invention.

FIG. 7 is a velocity diagram of a prior art gear train.

[Explanation of symbols]

S1 first sun gear S2 Second Sun Gear S3 Third Sun Gear P1 First pinion gear P2 Second pinion gear P2 'Third pinion gear P3 'Fourth pinion gear P3 Fifth pinion gear C carrier C3 second career R1 ring gear R3 second ring gear G3 deceleration planetary gear set C-1 First clutch C-2 Second clutch B-1 First brake B-2 Second brake B-3 Third brake (means for transmitting decelerated rotation) 19 Output member

   ─────────────────────────────────────────────────── ─── Continued front page    (72) Inventor Yoshikazu Sakaguchi             2-2 Midorigahama, Tahara-cho, Atsumi-gun, Aichi Prefecture             Within Ishin AW Precision Co., Ltd. F term (reference) 3J027 FA19 FB01 GA01 GB02 GC14                       GC25 GD04 GD08 GD12

Claims (4)

[Claims] 1. A first sun gear (S1), a ring gear (R1), a first pinion gear (P1) meshing with the first sun gear and the ring gear, and a first pinion gear so as to rotate integrally with the first pinion gear. Connected,
A second pinion gear having a smaller diameter than the first pinion gear (P
2), a third pinion gear (P2 ′) that meshes with the second pinion gear, a second sun gear (S2) that meshes with the third pinion gear, and supports the first to third pinion gears. A carrier (C), a deceleration planetary gear set (G3) that decelerates and outputs the input rotation, a first clutch (C-1) that transmits the input rotation to the first sun gear, and an input rotation to the ring gear. And a second brake (B-) that locks the second sun gear and a second clutch (C-1) that locks the ring gear.
2) and a second sun gear, an automatic transmission for a vehicle comprising a means (B-3) for transmitting the decelerated rotation output from the deceleration planetary gear set, and an output member (19) connected to the carrier. 2. The means for transmitting decelerated rotation is an input element (S) for input rotation in a decelerated planetary gear set.
3) and a third brake (B-3) for locking the reaction force element (C3) for the decelerated rotation output element (R3).
The automatic transmission for vehicles according to claim 1. 3. The reduction planetary gear set comprises a third
The sun gear (S3), the second ring gear (R3),
A fourth pinion gear (P
3 ') and a fifth pinion gear (P3) that meshes with the fourth pinion gear and the second ring gear (R3).
The automatic transmission for vehicles according to claim 1 or 2, which is a double pinion gear set comprising: a second carrier (C3) supporting the fourth and fifth pinion gears. 4. The automatic transmission for a vehicle according to claim 1, wherein a ring gear is locked by engagement of a first brake with respect to an input rotation input to a first sun gear by engagement of a first clutch. Speed, second speed by engagement of the second sun gear by engagement of the second brake, third speed by input of decelerated rotation to the second sun gear by engagement of means for transmitting decelerated rotation, The fourth speed is achieved by the input rotation input to the ring gear due to the engagement of the clutch, and the fourth speed is achieved by the engagement of the means for transmitting the decelerated rotation with respect to the input rotation input to the ring gear due to the engagement of the second clutch. 5. The automatic gear shift for a vehicle according to claim 1, 2 or 3, wherein the fifth speed is achieved by inputting decelerated rotation to the second sun gear, and the sixth speed is achieved by engaging the second sun gear by engaging the second brake. Machine.