JPH06323377A - Planetary gear train for vehicular transmission - Google Patents

Abstract

PURPOSE:To improve power transmission efficiency by providing a member, fixed to a stationary part at the first forward gear speed time and the reversing time in the planetary gear train of a transmission obtaining a change gear ratio among four forward stages or more, in such a way as to be fixable to the stationary part through a friction clutch and a dog clutch. CONSTITUTION:A planetary gear train having a change gear ratio among six forward stages and one backward stage is provided with a first and a second planetary gear sets 10, 20, and a first sun gear 12 is connected to a second carrier 28 and can be fixed to a stationary part 64 by a second brake 52 through the second carrier 28. A first ring gear 16 fixed to an output shaft 62 can be connected to a second ring gear 26 by a first clutch 40. A first carrier 18 is provided in such a way as to be selectively connectable as a first gear speed member to the stationary part 64 or an input shaft 60 through a second clutch (friction clutch) 42 and a dog clutch 66 and also to be fixable to the stationary part 64 through a one-way clutch 46. All the planetary gears can be thereby integrated to obtain the change gear ratio of 1:1.

Description

Detailed Description of the Invention

[0001]

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

[0002]

2. Description of the Related Art As a conventional planetary gear train for a vehicle transmission, for example, one described in US Pat. No. 4,070,927 shown in FIG. 25 is known. This planetary gear train includes three sets of first to third planetary gear sets 10, 20, and 30 which are simple planetary gears, and two first and second clutches 4.
0, 42 and three first to third brakes 50, 52, 5
It is composed of 4.

The first sun gear 12 of the first planetary gear set 10 is connected to the input shaft 60, the first ring gear 16 can be fixed to the stationary portion 64 via the first brake 50, and the first carrier 18 can be fixed to the second portion. The second ring gear 26 of the planetary gear set 20
Connected to. The second ring gear 26 is the second brake 52.
Can be fixed to the stationary portion 64 via the second sun gear 2
2 is connected to the third sun gear and the first clutch 4
0 is connectable to the input shaft 60, the second carrier 28 is connectable to the input shaft 60 via the second clutch 42, and the third ring gear 3 of the third planetary gear set 30 is connected.
6 is connected. The third ring gear 36 is the third brake 5
The third carrier 38 can be fixed to the stationary portion 64 via the shaft 4, and the third carrier 38 is connected to the output shaft 62.

The planetary gear train constructed in this way is shown in FIG.
As shown in FIG. 6, the gear ratios of 6 forward gears and 1 reverse gear are obtained by combining the engagement and release of each friction element.

[0005]

In such a conventional planetary gear train, a gear ratio is obtained by engaging two friction elements at each gear. The remaining friction elements are then released and they are deactivated during operation. That is, taking the fourth speed as an example, the first speed
The clutch 40 and the second clutch 42 are engaged, and the first
Brake 50, second brake 52 and third brake 5
4 is inactive because it is released. Since each of these non-actuated friction elements has a drag resistance due to the difference in rotation between friction parts, the drag resistance causes a loss in power transmission and reduces power transmission efficiency.

Of the non-actuated friction elements in the frequently used high speed stage, the brake (third brake 54 in FIG. 25) that operates at the first forward speed and the reverse speed is
Since the transmission torque during operation is large, the capacity as a brake is large, and the drag resistance when not operating is also large. Therefore, it is a major factor that deteriorates the fuel consumption rate of automobiles.

[0007] Generally, in order to improve the fuel consumption rate of an automobile, it is desirable that the automatic transmission has multiple stages as in the above-mentioned conventional example, but if the multiple stages are used, the number of friction elements such as clutches and brakes increases. There are many examples, and there is a problem that the drag resistance reduces the power transmission efficiency, and the fuel consumption reduction effect due to the multistage is reduced. The present invention has been made in view of such conventional problems, and an object of the present invention is to improve power transmission efficiency by reducing drag resistance due to a non-actuated friction element.

[0008]

In order to achieve the above object, the present invention provides a planetary gear train of a transmission in which a plurality of planetary gears are combined to obtain a gear ratio of four or more forward gears. It is characterized in that the member fixed to the stationary portion when retracted can be fixed to the stationary portion via the friction clutch and the dog clutch.

Further, according to the present invention, the member can be selectively connected to the stationary portion and the input shaft via the friction clutch and the switchable dog clutch, and can be fixed to the stationary portion via the one-way clutch. It is characterized by having done. Further, the present invention provides a planetary gear train including a first planetary gear set that is a simple planetary gear and a double pinion type double-row second planetary gear set that includes a long pinion. A long pinion that meshes with the second ring gear meshes with the third sun gear, the first sun gear and the second carrier can be coupled to each other and can be fixed to a stationary portion, and the first ring gear can be coupled to the output shaft and the second ring gear. A second sun gear is connected to the input shaft, a third sun gear is fixable to a stationary part, and a first carrier is selectively connectable to the stationary part and the input shaft. To do.

The present invention is also a first planetary gear, which is a first planetary gear.
In a planetary gear train composed of a planetary gear set and a double pinion type double-row second planetary gear set including a long pinion, a long pinion meshing with a second sun gear of the second planetary gear set meshes with a third ring gear. The first sun gear and the second carrier are connected to each other and can be fixed to the stationary portion, and the first ring gear is connected to the output shaft and the second ring gear.
The sun gear is connected to the input shaft, the third ring gear can be fixed to the stationary part, and the first carrier can be selectively connected to the stationary part and the input shaft.

Further, according to the present invention, in a planetary gear train of a vehicle transmission constituted by two sets of a simple planetary gear set and a parallel shaft gear set, the first sun gear can be connected to the input shaft, and the first ring gear. Is connected to the second sun gear and can be fixed to the stationary part, and is also connectable to the input shaft via a parallel shaft gear set, the second ring gear is connected to the output shaft, and the first carrier is connected to the second carrier. It is characterized in that it can be selectively connected to the stationary part and the input shaft.

Further, according to the present invention, in a gear train of a vehicle transmission composed of a double-row planetary gear set and a simple planetary gear set, the first carrier of the double-row planetary gear set and the output shaft can be connected. Yes, the first sun gear is connected to the input shaft, and the second
The sun gear can be connected to the third carrier and can be fixed to the stationary portion, the third ring gear can be connected to the output shaft, the third sun gear can be fixed to the stationary portion, and the first ring gear can be the stationary portion and the input shaft. It is characterized in that it can be selectively connected with.

Further, according to the present invention, in a planetary gear train of a vehicle transmission comprising a double-row planetary gear set and a simple planetary gear set, the second ring gear of the double-row planetary gear set and the output shaft can be connected. And the first sun gear is connected to the input shaft,
The first ring gear is connected to the third carrier and can be fixed to the stationary part, the third ring gear is connected to the output shaft, the third sun gear can be fixed to the stationary part, and the first carrier is the stationary part and the input part. It is characterized in that it can be selectively connected to the shaft.

Further, according to the present invention, in a planetary gear train of a vehicle transmission composed of two sets of simple planetary gear sets, one pinion of one first planetary gear set has two sun gears, a first sun gear and a second sun gear. The second sun gear and the third sun gear are connected to each other and can be fixed to the stationary portion, the first carrier and the second ring gear can be connected to the output shaft, and the first sun gear and the first ring gear are respectively input. The second carrier is connectable to the shaft, and the second carrier is selectively connectable to the stationary part and the input shaft.

[0015]

According to the planetary gear train of the vehicle transmission of the present invention having such a structure, the member (hereinafter referred to as the 1st speed member) fixed to the stationary portion at the first forward speed and the reverse speed,
Since it is selectively fixable or connectable to the stationary part or the input shaft via the friction clutch and the dog clutch, that is, the first speed member is usually fixed to the friction clutch and the stationary part for connecting to the input shaft. Although it has two friction elements of the brake, in general, a one-way clutch is provided for the first speed member, and it is noted that this one-way clutch has a function of fixing the first speed member to a stationary portion in the normal D range driving. By combining the friction element with only one friction clutch and a dog clutch that can be switched, the necessary function can be satisfied, so the first speed member with the largest drag resistance at high speed can be selected. The brake that is fixed to the stationary part is virtually the same as when it is lost, increasing transmission efficiency. It is possible to improve on.

As a result, the fuel consumption rate can be reduced.

[0017]

Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 shows a first embodiment of the present invention and is a skeleton diagram of a planetary gear train having a gear ratio of 6 forward gears and 1 reverse gear. In FIG. 1, reference numeral 10 denotes a first planetary gear set which is a simple planetary gear, and the first planetary gear set 10 is a first sun gear 1
2, having a first ring gear 16 and a first carrier 18. Reference numeral 20 denotes a double-pinion type double-row second planetary gear set, and the second planetary gear set 20 includes a second sun gear 22, a long pinion 24, a pinion 24A, a second ring gear 26,
It has a second carrier 29 and a third sun gear 32.

The first sun gear 12 is connected to the second carrier 28 and can be fixed to the stationary portion 64 by the second brake 52 via the second carrier 28. First ring gear 16
Is connected to the output shaft 62, and the first clutch 40
Can be connected to the second ring gear 26. The first carrier 18 can be selectively fixed or connected to the stationary portion 64 or the input shaft 60 via the second clutch 42 and the dog clutch 66 as a first speed member, and
It can be fixed to the stationary portion 64 via the one-way clutch 46.

The second sun gear 22 is connected to the input shaft 60, and the long pinion 2 is connected via the pinion 24A.
4 is engaged. As described above, the second carrier 28 is connected to the first sun gear 12 and can be fixed to the stationary portion 64 by the second brake 52. A second clutch connectable to the first ring gear 16 via the first clutch 40.
The ring gear 26 meshes with the long pinion 24, and the long pinion 24 meshes with the third sun gear 32. The third sun gear 32 can be fixed to the stationary portion 64 by the first brake 50.

Next, the operation will be described. Figure 2 shows each friction element
By operating as described above, a gear ratio of 6 forward gears and 1 reverse gear is obtained. The circles in FIG. 2 indicate the operation (fastening, etc.) of each element. Further, the arrow of the dog clutch 66 represents the meshing direction of the dog clutch 66. That is,
The fourth, fifth, and sixth speeds mesh with the input shaft 60 (the left side in FIG. 1), and the values in parentheses indicate that they are not related to power transmission.
It can be seen that no switching is required in the "D" range.

The mark * indicates that the dog clutch 66 can be switched in either direction. "L" represents a range used when the engine is braked, etc., and in many cases, the position of the operation lever is usually displayed as a number such as "2" or "1". It meshes with the stationary portion 64 (on the right side in FIG. 1) when the vehicle is in the 1st speed of the “L” range and the reverse of the “R” range.

Next, the D ranges 4, 5, which are frequently used,
6th power transmission will be described. In the fourth speed in the D range, the first clutch 40 and the second clutch 42 are engaged. Second clutch 42 and dog clutch 66
When is fastened, the entire planetary gear is integrated, so 1:
A gear ratio of 1 is obtained. Next, in the case of the fifth speed in the D range, the second clutch 42 and the first brake 50 are engaged.

Second clutch 42 and dog clutch 6
When 6 is fastened, the input shaft 60 is connected to the first carrier 18, and the first carrier 18 is rotationally driven by the input shaft 60. When the first brake 50 is engaged, the third sun gear 32 is fixed to the stationary portion 64 by the first brake 50, so that the second carrier 28 connected to the long pinion 24 is decelerated and the first sun gear 12 is also decelerated. To do. By decelerating the first sun gear 12 and rotationally driving the first carrier 18, the first ring gear 16 is accelerated and the output shaft 62 is accelerated from the input speed of the input shaft 60.

Next, in the sixth speed in the D range, the second clutch 42 and the second brake 52 are engaged. When the second clutch 42 and the dog clutch 66 are engaged, the input shaft 60 is connected to the first carrier 18, and the first carrier 18 is rotationally driven by the input shaft 66.

When the second brake 52 is engaged, the second carrier 28 is fixed to the stationary portion 64 by the second brake 52, and the first sun gear 12 is fixed. Therefore, the speed of the first ring gear 16 is increased as compared with the case of the fifth speed, and the output shaft 6
2 is also faster than in the case of 5th speed. In this embodiment, the drag resistance was large in the high-speed stage that was frequently used.
Since there is substantially no brake for fixing the first carrier 18, which is a speed member, the power loss due to the drag resistance is greatly reduced, so that the transmission efficiency of the transmission can be improved and, as a result, the automobile. It can be expected to contribute to the reduction of fuel consumption rate.

In addition, since the one-way clutch 46 serves to fix the first speed member in the normal D range traveling, it is not necessary to switch the dog clutch 66 in the D range. It can be said that the difficulty is small. That is, "first speed in the L range" that requires engine braking
Since it suffices to operate the dog clutch 66 only when switching between "reverse" and "reverse", it is not particularly difficult to control the operation timing and the like.

Further, since the operation frequency of the "first speed in the L range" and the "reverse" is generally low, it is easy to ensure the durability of the dog clutch 66 and the accompanying synchronization mechanism and operation mechanism. is there. Note that FIG. 27 is a skeleton diagram of the planetary gear train that is the base of the first embodiment, and its operation is similar to that of the conventional example, and is shown in FIG.

Next, FIGS. 3 to 8 show a second embodiment of the present invention.
The seventh embodiment shows a planetary gear train having six forward gears and one reverse gear, though the configurations are different, and the operation can be represented in FIG. 2 as in the first embodiment. In the second embodiment shown in FIG. 3, the second sun gear 22 of the second planetary gear set 20 is used.
Meshes with the long pinion 24, and the long pinion 24 meshes with the third ring gear 36. The second ring gear 26 meshes with the long pinion 24 via the pinion 24A. The third ring gear 36 can be fixed to the stationary portion 64 by the first brake 50. The first carrier 18 has a function of a first speed member. In this embodiment, the same effect as that of the above embodiment can be obtained.

In the third embodiment shown in FIG. 4, the first to third planetary gear sets 10, 20, which are three simple planetary gears, are used.
2 is performed by using the configuration of FIG. The first carrier 18 has a function as a first speed member. In this embodiment, the same effect as that of the above embodiment can be obtained.
In the fourth embodiment shown in FIG. 5, the double pinion type double-row first planetary gear set 10 and the second planetary gear set 20 that is a simple planetary gear are used, and the operation of FIG. 2 is performed by the configuration of FIG. .

The first ring gear 16 has a function as a first speed member. In this embodiment, the same effect as that of the above embodiment can be obtained. In the fifth embodiment shown in FIG. 6, the double pinion type double-row first planetary gear set 10 and the second planetary gear set 20 that is a double pinion planetary gear set 20 are used, and the operation of FIG. To do.

The third ring gear 36 has a function as a first speed member. In this embodiment, the same effect as that of the above embodiment can be obtained. In the sixth embodiment shown in FIG. 7, 2
First and second planetary gear sets 10, 2 which are two simple planetary gears
0 and a double pinion planetary gear set 30,
With the above configuration, the operation of FIG. 2 is performed.

The third ring gear 36 has a function as a first speed member. In this embodiment, the same effect as that of the above embodiment can be obtained. In the seventh embodiment shown in FIG. 8, the first planetary gear set 10 which is a double pinion planet tooth and the second and third planetary gear sets 20 and 30 which are simple planetary gears are used, and the configuration of FIG. Perform the operation of 2.

The third carrier 38 functions as a first speed member. In this embodiment, the same effect as that of the above embodiment can be obtained. Next, FIG. 9 shows an eighth embodiment of the present invention, FIG. 11 shows a ninth embodiment of the present invention, and FIG. 12 shows a tenth embodiment of the present invention. The example is a combination of two simple planetary gear sets and a parallel shaft gear set. The operation of the eighth and ninth embodiments is shown in FIG.
0, the operation of the tenth embodiment is such that the arrow indicating the transmission direction of the dog clutch 66 in FIG. 10 is opposite.

In the eighth embodiment shown in FIG. 9, the first sun gear 12 is connectable to the input shaft 60 via the first clutch 40, and the first ring gear 16 is the second sun gear 22.
It can be connected to the input shaft 60 via the parallel shaft gear set 70 and can be fixed by the brake 50. The second ring gear 26 is connected to the output shaft 62.
The first carrier 18 is connected to the second carrier 28, and
The carrier 18 can be fixed or connected to the stationary portion 64 or the input shaft 60 via the second clutch 42 and the dog clutch 66, and the second carrier 28 can be fixed to the stationary portion 64 via the one-way clutch 46. First
The carrier 18 has a function as a first speed member. Operation is shown in FIG. In this embodiment, the same effect as that of the above embodiment can be obtained.

In the ninth embodiment shown in FIG. 11, the first and second planetary gear sets 10 and 20, which are simple planetary gears, and the parallel shaft gear set 70 are used, and the operation of FIG. To do. The first carrier 18 has a function as a first speed member. In this embodiment, the same effect as that of the above embodiment can be obtained. In the tenth embodiment shown in FIG. 12, the first and second planetary gear sets 10 and 20, which are simple planetary gears, and the parallel shaft gear set 70 are used, and the operation of FIG. 10 is performed with the configuration of FIG. The operation of the tenth embodiment is shown in FIG.
The arrow indicating the transmission direction of the dog clutch 66 is opposite. The second carrier 28 has a function as a first speed member. In this embodiment, the same effect as that of the above embodiment can be obtained.

Next, FIG. 13 shows an eleventh embodiment of the present invention, and FIGS. 15 to 18 show twelfth to fifteenth embodiments of the present invention, respectively. The operation shown in FIG. Obtain the gear ratio of one reverse speed. In the eleventh embodiment shown in FIG. 13, the first carrier 18 of the double-pinion type double-row first planetary gear set 10 has an output shaft 62 through a first clutch 40.
The first sun gear 12 is connected to the input shaft 60, the second sun gear 22 is connected to the third carrier 38 of the second planetary gear set 20, which is a simple planetary gear, and the second brake 52 is used. It can be fixed to the stationary portion 64. The second sun gear 22 meshes with the long pinion 14. The third ring gear 36 is connected to the output shaft 62,
The third sun gear 32 has a stationary portion 64 by the first brake 50.
Can be fixed to.

The first ring gear 16 can be fixed to the stationary portion 64 via the one-way clutch 46, and can be connected or fixed to the input shaft 60 or the stationary portion 64 via the second clutch 42 and the dog clutch 66. . The first ring gear 16 has a function as a first speed member. Operation is shown in FIG. In this embodiment, the same effect as that of the above embodiment can be obtained.

In the twelfth embodiment shown in FIG. 15, a double pinion type double-row first planetary gear set 10 and a second planetary gear set 20 which is a simple planetary gear are used, and the configuration of FIG. The first carrier 18, which operates, has a function as a first speed member. In this embodiment, the same effect as that of the above embodiment can be obtained. In the thirteenth embodiment shown in FIG. 16, the first planetary gear set 10 which is a simple planetary gear and the double pinion type double row second planetary gear set 20 are used, and the operation of FIG. 14 is performed by the configuration of FIG. . The first carrier 18 has a function as a first speed member. Also in this embodiment, the same effect as that of the above embodiment can be obtained.

In the fourteenth embodiment shown in FIG. 17, 3
First to third planetary gear sets 10, 2 which are two simple planetary gears
The operation of FIG. 14 is performed by using the components 0 and 30 and the configuration of FIG. The first carrier 18 has a function as a first speed member. In this embodiment, the same effect as that of the above embodiment can be obtained. In the fifteenth embodiment shown in FIG. 18, the first planetary gear set 10 which is a simple planetary gear and the second planetary gear set 20 of the double pinion type double row are used and the configuration of FIG.
The operation of FIG. 14 is performed. The first carrier 18 has a function as a first speed member. In this embodiment, the same effect as that of the above embodiment can be obtained.

Next, FIG. 19 shows a sixteenth embodiment of the present invention, and FIGS. 21 to 23 show a seventeenth embodiment to a nineteenth embodiment of the present invention, respectively, to show the operation of these embodiments. It shows in FIG. However, in the case of the eighteenth embodiment, FIG.
In, the arrow indicating the transmission direction of the dog clutch 66 is opposite. In the sixteenth embodiment shown in FIG. 19, there are two simple planetary gears, the first and second planetary gear sets 10 and 20.
And two dog clutches 66 and 68 are used. The pinion 14A of the first planetary gear set 10 is the first and second sun gears 1.
The second sun gear 22 is meshed with the second sun gear 22 and is connected to the third sun gear of the second planetary gear set 20, and can be fixed to the stationary portion 64 by the first brake 50.

The first sun gear 12 is connectable to the input shaft 60 via the dog clutch 68, and the first ring gear 1
6 can be connected to the input shaft 60 via the first clutch 40. The second carrier 28 can be fixed to the stationary portion 64 via the one-way clutch 46, and can also be fixed or connectable to the stationary portion 64 or the input shaft 60 via the second clutch 42 and the dog clutch 66. The operation is shown in FIG.

The second carrier 28 has a function as a first speed member. Also in this embodiment, the same effect as that of the above embodiment can be obtained. In the seventeenth embodiment shown in FIG. 21, a double pinion type double row planetary gear set 10 and two dog clutches 66 and 68 are used, and the configuration of FIG.
The operation of FIG. 20 is performed.

The second ring gear 26 has a function as a first speed member. In this embodiment, the same effect as that of the above embodiment can be obtained. In the eighteenth embodiment shown in FIG. 22, the double pinion type double row planetary gear set 10 and the two dog clutches 66 and 68 are used, and the configuration of FIG.
The operation of FIG. 20 is performed.

In this case, in FIG. 20, the arrow indicating the operating direction of the dog clutch 66 is opposite. The first carrier 18 has a function as a first speed member. In this embodiment, the same effect as that of the above embodiment can be obtained. The nineteenth embodiment shown in FIG. 23 uses the first and second planetary gear sets 10 and 20 which are simple planetary gears and two dog clutches 66 and 68 to perform the operation of FIG. 20 with the configuration of FIG. .

The first carrier 18 has a function as a first speed member. In this embodiment, the same effect as that of the above embodiment can be obtained. Next, FIG. 24 shows a twentieth embodiment of the present invention. The twentieth embodiment is an application of the planetary gear train of FIG. 1, in which a final reduction planetary gear set 76 and a differential gear device 80 are added to the planetary gear train for speed change and output to the left and right axles 82 and 84. This allows it to be placed coaxially with the axle.

[0046]

As described above, according to the present invention, the member fixed to the stationary portion at the first forward speed and the backward movement can be connected to the stationary portion or the input shaft via the clutch and the dog clutch. The friction element can be minimized, the drag resistance due to the non-actuated friction element can be reduced, and the power transmission efficiency can be improved. As a result, the fuel consumption rate can be reduced.

[Brief description of drawings]

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

[Fig. 2] Operation explanatory diagram

FIG. 3 is a skeleton diagram showing a second embodiment of the present invention.

FIG. 4 is a skeleton diagram showing a third embodiment of the present invention.

FIG. 5 is a skeleton diagram showing a fourth embodiment of the present invention.

FIG. 6 is a skeleton diagram showing a fifth embodiment of the present invention.

FIG. 7 is a skeleton diagram showing a sixth embodiment of the present invention.

FIG. 8 is a skeleton diagram showing a seventh embodiment of the present invention.

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

FIG. 10 is an operation explanatory diagram.

FIG. 11 is a skeleton diagram showing a ninth embodiment of the present invention.

FIG. 12 is a skeleton diagram showing a tenth embodiment of the present invention.

FIG. 13 is a skeleton diagram showing an eleventh embodiment of the present invention.

FIG. 14 is an operation explanatory diagram

FIG. 15 is a skeleton diagram showing a twelfth embodiment of the present invention.

FIG. 16 is a skeleton diagram showing a thirteenth embodiment of the present invention.

FIG. 17 is a skeleton diagram showing a fourteenth embodiment of the present invention.

FIG. 18 is a skeleton diagram showing a fifteenth embodiment of the present invention.

FIG. 19 is a skeleton diagram showing a sixteenth embodiment of the present invention.

FIG. 20 is an operation explanatory diagram.

FIG. 21 is a skeleton diagram showing a seventeenth embodiment of the present invention.

FIG. 22 is a skeleton diagram showing the eighteenth embodiment of the present invention.

FIG. 23 is a skeleton diagram showing a nineteenth embodiment of the present invention.

FIG. 24 is a skeleton diagram showing a twentieth embodiment of the present invention.

FIG. 25 is a skeleton diagram showing a conventional example.

FIG. 26 is an operation explanatory view of a conventional example.

FIG. 27 is a skeleton diagram of the planetary gear train that is the base of the first embodiment.

[Explanation of symbols]

 10: 1st planetary gear set 12: 1st sun gear 14: Long pinion 14A: Pinion 16: 1st ring gear 18: 1st carrier 20: 2nd planetary gear set 22: 2nd sun gear 24: Long pinion 24A: Pinion 26: Second ring gear 28: Second carrier 30: Third planetary gear set 32: Third sun gear 32A: Fourth sun gear 34: Pinion 36: Third ring gear 38: Third carrier 40: First clutch 42: Second clutch 44: Third clutch 50: Brake or first brake 52: Second brake 54: Third brake 60: Input shaft 62: Output shaft 64: Stationary part 66, 68: Dog clutch 70: Parallel shaft gear set 76: Final reduction planetary gear Set 80: Differential gear device 82, 84: Axle

Claims (8)

[Claims] 1. A planetary gear train of a transmission, wherein a plurality of planetary gears are combined to obtain a gear ratio of four or more forward gears. A member fixed to a stationary portion at a first forward speed and a reverse gear is provided with a friction clutch and a dog clutch. A planetary gear train of a transmission for a vehicle, wherein the planetary gear train can be fixed to a stationary portion via 2. The member can be selectively connected to a stationary portion and an input shaft via a friction clutch and a switchable dog clutch, and can be fixed to the stationary portion via a one-way clutch. The planetary gear train of the transmission for vehicles according to claim 1. 3. A planetary gear train comprising a first planetary gear set which is a simple planetary gear and a double pinion type double-row second planetary gear set including a long pinion, wherein the second planetary gear set is a second planetary gear set. A long pinion that meshes with the ring gear meshes with the third sun gear, the first sun gear and the second carrier can be coupled to each other and can be fixed to a stationary portion, and the first ring gear can be coupled to the output shaft and the second ring gear. The second sun gear is connected to the input shaft, the third sun gear can be fixed to the stationary part, and the first carrier is selectively connectable to the stationary part and the input shaft. Planetary gear train for vehicle transmissions. 4. A planetary gear train comprising a first planetary gear set which is a simple planetary gear and a double pinion type double-row second planetary gear set including a long pinion, wherein the second planetary gear set is a second planetary gear set. A long pinion that meshes with the sun gear meshes with the third ring gear, the first sun gear and the second carrier can be coupled to each other and can be fixed to a stationary portion, and the first ring gear can be coupled to the output shaft and the second ring gear. The second sun gear is connected to the input shaft, the third ring gear is fixable to the stationary part, and the first carrier is selectively connectable to the stationary part and the input shaft. Planetary gear train for vehicle transmissions. 5. In a planetary gear train of a vehicle transmission comprising two sets of a simple planetary gear set and a parallel shaft gear set, a first sun gear is connectable to an input shaft, and a first ring gear is a second sun gear. The second ring gear is connected to the output shaft, the first carrier is connected to the second carrier and is stationary. A planetary gear train for a vehicle transmission, wherein the planetary gear train is selectively connectable to a shaft and an input shaft. 6. A gear train of a vehicle transmission comprising a double-row planetary gear set and a simple planetary gear set, wherein a first carrier and an output shaft of the double-row planetary gear set are connectable to each other. The sun gear is connected to the input shaft, the second sun gear is connectable to the third carrier and can be fixed to the stationary part, and the third ring gear is connected to the output shaft,
The planetary gear train of a transmission for a vehicle, wherein the third sun gear can be fixed to the stationary portion, and the first ring gear can be selectively coupled to the stationary portion and the input shaft. 7. A planetary gear train of a vehicle transmission comprising a double-row planetary gear set and a simple planetary gear set, wherein a second ring gear of the double-row planetary gear set and an output shaft are connectable, The first sun gear is connected to the input shaft, the first ring gear is connected to the third carrier and can be fixed to the stationary portion, and the third ring gear is connected to the output shaft.
The planetary gear train for a vehicle transmission, wherein the third sun gear can be fixed to the stationary portion, and the first carrier can be selectively coupled to the stationary portion and the input shaft. 8. A planetary gear train for a vehicle transmission comprising two sets of simple planetary gear sets, wherein a pinion of one of the first planetary gear sets meshes with two sun gears, a first and a second sun gear. The second sun gear and the third sun gear can be connected and can be fixed to the stationary portion, and the first carrier and the second ring gear can be connected to the output shaft.
The planetary gear train for a vehicle transmission, wherein the sun gear and the first ring gear are respectively connectable to the input shaft, and the second carrier is selectively connectable to the stationary part and the input shaft.