JPH08105497A - Gear transmission - Google Patents

Abstract

(57) [Abstract] [Purpose] To provide a gear transmission that is compact and lightweight, and that can have multiple stages. [Structure] Sun gears S1 and S2, and carrier C1
, C2 are connected to each other, a single pinion type first planetary gear mechanism G1 and a double pinion type second planetary gear mechanism G2 are arranged, and a double pinion type third planetary gear mechanism G3 is arranged on the same axis. , First planetary gear mechanism G1
Sun gear S1 and ring gear R of the third planetary gear mechanism G3
3 and the carrier C of the first planetary gear mechanism G1.
1 is connected to the sun gear S3 of the third planetary gear mechanism G3,
Further, a brake B3 for selectively stopping the rotation of the ring gear R3 of the third planetary gear mechanism G3 is provided so that six forward gears can be set.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a gear transmission for a vehicle, and more particularly to a gear transmission for an automatic transmission suitable for an FF vehicle (front engine front wheel drive vehicle).

[0002]

2. Description of the Related Art As is well known, a gear transmission in an automatic transmission for a vehicle uses a plurality of sets of planetary gear mechanisms, connects their rotating elements appropriately, and uses a clutch and a brake to input elements. A plurality of shift speeds are set by appropriately changing the reaction force element and the output element. Since an automatic transmission mainly composed of such a gear transmission is mounted in a limited space of a vehicle body, it is required to be small in size, and in order to improve the power performance of the entire vehicle. It needs to be lightweight. On the other hand, in order to improve the running performance of the vehicle as a whole, it is desirable that there be more gear stages that can be set. Furthermore, the gear ratio of each gear stage enables good power performance and smooth gear shift. Therefore, it is desired that the relationship be close to a geometric series.

F developed in the background of such demands
An example of a gear transmission suitable for F cars is disclosed in Japanese Patent Laid-Open No. 2-1294.
No. 42 publication. This gear transmission is a double pinion type second planetary gear mechanism in which a single pinion type first planetary gear mechanism provided with a pinion meshing with a sun gear and a ring gear and a pair of pinion meshing with each other is provided between the sun gear and the ring gear. Are arranged on the same axis, the sun gears and the carriers are connected to each other, and the carrier is connected to a counter drive gear which is an output element.

In this conventional gear transmission, since the sun gears and the carriers are connected to each other, it is possible to eliminate the special connecting means and arrange the two planetary gear mechanisms close to each other. As a result, the size and weight can be reduced. Further, since the counter drive gear, which is an output element, can be arranged at an intermediate portion in the axial direction of the entire gear transmission, it is advantageous for the gear transmission in the automatic transmission for FF vehicles.

[0005]

In the above-mentioned conventional gear transmission, it is possible to set four forward gears and one reverse gear, but in order to improve the running performance of the vehicle,
The number of gears that can be set is insufficient, and it is desired to increase the number of gears. Therefore, conventionally, it is known that an additional shaft parallel to the central axis thereof is additionally arranged in the gear transmission described above, and a single-pinion type planetary gear mechanism is added on the auxiliary shaft, whereby multistages are realized. There is. However, in such a configuration, since it is necessary to provide a sub shaft, not only the outer diameter of the gear transmission or the automatic transmission as a whole becomes large, but also the weight increases. Further, even if a single-pinion type planetary gear mechanism is added on the counter shaft, the gears that can be set are limited to the five forward gears, and it is not always possible to sufficiently meet the demand for multiple gears.

The present invention has been made in view of the above-mentioned circumstances, and an object thereof is to provide a gear transmission for an automatic transmission which is not only capable of providing a higher number of stages but also small and lightweight. It is what

[0007]

In order to achieve the above object, the present invention provides a single pinion type planetary gear mechanism and a double pinion type planetary gear mechanism in which sun gears and carriers are connected to each other, and further a planetary gear. The mechanism is arranged on the same axis and configured so that six forward stages can be set. In other words, the invention according to claim 1 is a single pinion type first equipped with a sun gear, a ring gear concentrically arranged with respect to the sun gear, and a carrier that rotatably holds the sun gear and a pinion meshing with the ring gear. A planetary gear mechanism, a sun gear connected to the sun gear, a ring gear concentrically arranged with respect to the sun gear, and at least a pair of pinions rotatably arranged between the sun gear and the ring gear and meshed with each other. And a double pinion type second planetary gear mechanism including a carrier connected to the carrier and arranged on the same axis, and the carrier connected to each other is connected to an output element And a ring gear arranged concentrically with this sun gear and this A double pinion type third planetary gear mechanism, which is rotatably arranged between a sun gear and a ring gear and has at least a pair of pinion meshed with each other, and is arranged on the same axis as each planetary gear mechanism. And the first
The sun gear of the planetary gear mechanism and the ring gear of the third planetary gear mechanism are connected, the carrier of the first planetary gear mechanism and the sun gear of the third planetary gear mechanism are connected, and rotation of the ring gear of the third planetary gear mechanism is selected. It is characterized in that a brake for stopping the movement is provided.

The invention according to claim 2 is a single pinion equipped with a sun gear, a ring gear arranged concentrically with respect to the sun gear, and a carrier for rotatably holding the sun gear and a pinion meshing with the ring gear. Type first planetary gear mechanism, a sun gear connected to the sun gear, a ring gear concentrically arranged with respect to the sun gear, and at least a pair of rotatably arranged between the sun gear and the ring gear and meshed with each other. A double pinion type second planetary gear mechanism having a carrier that holds a pinion and that is connected to the carrier is arranged on the same axis, and the carrier connected to each other is connected to an output element. , The sun gear and the ring gear arranged concentrically to the sun gear. And a single pinion-type third planetary gear mechanism including a sun gear and a carrier that holds a pinion meshed with the ring gear, the third planetary gear mechanism being arranged on the same axis as each planetary gear mechanism, and the first planetary gear mechanism. Is connected to the ring gear of the third planetary gear mechanism, the carrier of the first planetary gear mechanism is connected to the sun gear of the third planetary gear mechanism, and the rotation of the carrier of the third planetary gear mechanism is selectively stopped. It is characterized in that a brake is provided.

Further, the invention according to claim 3 is a single pinion type equipped with a sun gear, a ring gear concentrically arranged with respect to the sun gear, and a carrier rotatably holding the sun gear and a pinion meshing with the ring gear. A first planetary gear mechanism, a sun gear connected to the sun gear, a ring gear concentrically arranged with respect to the sun gear, and at least a pair of pinions rotatably arranged between the sun gear and the ring gear and meshed with each other. And a double pinion type second planetary gear mechanism having a carrier connected to the carrier and arranged on the same axis, and the carrier connected to each other is connected to an output element. , A sun gear and a ring gear arranged concentrically to this sun gear And a third pinion type third planetary gear mechanism, which is rotatably arranged between the sun gear and the ring gear and holds at least a pair of pinions meshed with each other, on the same axis as the planetary gear mechanisms. And a ring gear of the second planetary gear mechanism and a ring gear of the third planetary gear mechanism are connected to each other, a carrier of the first planetary gear mechanism and a carrier of the third planetary gear mechanism are connected to each other, and A brake is provided to selectively stop the rotation of the sun gear of the planetary gear mechanism.

[0010]

The gear transmission according to the present invention is provided with the forward 4 equipped with a single pinion type planetary gear mechanism and a double pinion type planetary gear mechanism in which sun gears and carriers are connected to each other.
It is based on a gear transmission capable of setting a gear. In the invention described in claim 1, the third planetary gear mechanism of the double pinion type is installed on the same axis line, and the ring gear of the third planetary gear mechanism is changed from the state where the first speed is set. By changing the fixing element (reaction force element) by fixing the gear with a brake, the gear stage intermediate between the first speed and the second speed in the gear transmission as the base is set. Further, in the overdrive state of the base gear transmission, if the fixing element is changed by fixing the ring gear of the third planetary gear mechanism with a brake, the second overdrive stage having a smaller gear ratio can be set. You can That is, as a whole, 6 forward speeds can be set. Further, when the number of forward gears is increased to six, since the auxiliary shaft is not provided, the overall structure of the gear transmission is reduced in size and weight.

According to a second aspect of the present invention, a single pinion type third planetary gear mechanism is additionally installed on the same axis line in the gear transmission as the base, and the gear transmission as the base is provided. When the carrier of the third planetary gear mechanism is fixed by the brake and the fixing element is changed in the state where the first speed is set, the intermediate stage between the first speed and the second speed in the gear transmission of the base is changed. Can be set. Further, by performing the same operation in a state in which the overdrive stage is set in the gear transmission as the base, the second overdrive stage having a smaller gear ratio is set. Therefore, the forward six speeds can be set for the entire gear transmission. Further, also in the invention of claim 2, since the auxiliary shaft is not provided, the size and weight can be reduced.

Further, in the invention described in claim 3, a double pinion type third planetary gear mechanism is arranged on the same axis as the gear transmission as the base, and the carrier is the base of the gear transmission. Since the structure is such that it is connected to the carrier and the ring gear is connected to the ring gear of the double pinion type planetary gear mechanism in the gear transmission based on the ring gear, it is possible to arrange three planetary gear mechanisms close to each other, and It can be made smaller and lighter. Also, in the invention described in claim 3, in the state where the first speed is set, the sun gear of the third planetary gear mechanism is fixed by the brake and the fixing element is changed by the gear transmission as the base. With this, it is possible to set an intermediate stage between the first speed and the second speed by the gear transmission as the base. Further, similarly, by setting the overdrive speed by the gear transmission as the base, the sun gear of the third planetary gear mechanism is fixed by the brake and the fixing element is changed, so that the gear ratio is further reduced. Two overdrive stages can be set. That is, the gear transmission is capable of setting 6 forward gears.

[0013]

EXAMPLES Next, the present invention will be described more specifically based on examples. In FIG. 1, a single-pinion type first planetary gear mechanism G1, a double-pinion type second planetary gear mechanism G2, and a double-pinion type third planetary gear mechanism G3 are on the same axis as the lockup clutch torque converter TC. It is arranged. The arrangement order of these planetary gear mechanisms is from the torque converter TC side to the third planetary gear mechanism G3, the second planetary gear mechanism G2, and the first planetary gear mechanism G1.

The first planetary gear mechanism G1 includes a sun gear S1, a ring gear R1 concentrically arranged with respect to the sun gear S1, and a carrier C which rotatably holds a sun gear S1 and a pinion P1 meshing with the ring gear R1.
It is mainly composed of 1. Further, the second planetary gear mechanism G2 rotates a sun gear S2, a ring gear R2 concentrically arranged with respect to the sun gear S2, and at least a pair of pinions P2 arranged between the sun gear S2 and the ring gear R2 and meshing with each other. It is mainly composed of a carrier C2 which is freely held. Furthermore, the third
The planetary gear mechanism G3 is mainly composed of a sun gear S3, a ring gear R3, and a carrier C3 rotatably holding at least a pair of pinions P3 arranged between them, similarly to the second planetary gear mechanism G2.

The carrier C1 of the first planetary gear mechanism G1
And the carrier C2 of the second planetary gear mechanism G2 are connected to each other, and these carriers C1 and C2 are the third
It is connected to the sun gear S3 of the planetary gear train G3. Further, the sun gear S1 of the first planetary gear mechanism G1 and the sun gear S2 of the second planetary gear mechanism G2 are connected to each other, and these sun gears S1 and S2 are connected to the third planetary gear mechanism G.
It is connected to three carriers C3. An output gear GO, which is an output element, is arranged between the second planetary gear mechanism G2 and the third planetary gear mechanism G3, and is connected to the carrier C2 and the sun gear S3 so as to rotate integrally.

Explaining the clutch means and the braking means, the input shaft 1 to which power is transmitted from the turbine runner of the torque converter TC is arranged along the central axis of each planetary gear mechanism G1, G2, G3. The first clutch K1 which is a multi-plate clutch is arranged in series between the input shaft 1 and the ring gear R1 of the first planetary gear mechanism G1. A second clutch K2, which is a multi-plate clutch, is arranged between the input shaft 1 and the carrier C3 in the third planetary gear mechanism G3.
Further, a third clutch K, which is a multi-plate clutch, is provided between the input shaft 1 and the ring gear R2 of the second planetary gear mechanism G2.
3 are arranged.

As the braking means, the second planetary gear mechanism G is used.
The first brake B1 and the first brake B, which are multiple disc brakes for selectively fixing the ring gear R2 of the second brake B2.
There is provided a first one-way clutch F1 which is arranged in parallel to 1. Further, the second brake B2, which is a band brake that selectively fixes the carrier C3 in the third planetary gear mechanism G3, and the third brake, which is a multi-plate brake that selectively fixes the ring gear R3 in the third planetary gear mechanism G3. B3 is provided.

In the above-described gear transmission, by engaging the above-mentioned clutch and brake as shown in FIG. 2, it is possible to set a shift speed of 6 forward gears and 1 reverse gear. In FIG. 2, the mark ◯ indicates the engaged state, the mark ◎ indicates the engaged state during engine braking, and the blank indicates the released state. Hereinafter, each shift speed will be briefly described.

The first forward speed is set by engaging the one-way clutch F1 as the first clutch K1 is engaged. That is, the torque is transmitted from the input shaft 1 to the ring gear R1 of the first planetary gear mechanism G1 and the load from the output gear GO is applied to the carrier C1. Rotation in the direction opposite to the rotation direction of the input shaft 1). Therefore, the sun gear S2 in the second planetary gear mechanism G2 integrated with the sun gear S1 tends to rotate in the reverse direction, and the ring gear R2 tends to rotate in the reverse direction accordingly. Therefore, the one-way clutch F1 is engaged and the ring gear R2
Can be stopped from rotating. That is, a reaction torque is applied to the ring gear R2, and as a result, the carriers C1 and C2 and the output gear GO integrated with them rotate forward at a low speed. In that case, the sun gears S1 and S2 rotate in reverse. Further, since the reaction torque is applied by the one-way clutch F1 in the first speed, when the engine brake is applied, the first brake B1 in parallel with the one-way clutch F1 is engaged. Let

The second speed is set by engaging the first clutch K1 and the third brake B3. That is, the rotation state of the third planetary gear mechanism G3 at the first speed is the sun gear S
In the state where 3 rotates in the positive direction together with the output gear GO, and the carrier C3 rotates in the reverse direction together with the sun gears S1 and S2 of the first planetary gear mechanism G1 and the second planetary gear mechanism G2, and the ring gear R3 accordingly rotates in the reverse direction. is there. Therefore, when the rotation of the ring gear R3 is stopped by the third brake B3 in this state, the rotation speeds of the sun gear S3, the output gear GO integrated with the sun gear S3, and the carriers C1 and C2 of the first planetary gear mechanism G1 and the second planetary gear mechanism G2 are reduced. Is increased in the forward rotation direction, and the gear ratio is increased with respect to the first speed. In this case, since the ring gear R2 of the second planetary gear mechanism G2 is normally rotated, the one-way clutch F1 is released.

The third speed is set by engaging the second brake B2 instead of the third brake B3. That is, while inputting to the ring gear R1 in the first planetary gear mechanism G1, the sun gear S1 and the sun gear S2 and the third gear in the second planetary gear mechanism G2 integral with the sun gear S1 are combined.
The carrier C3 in the planetary gear mechanism G3 is fixed. Therefore, in the first planetary gear mechanism G1, the carrier C1 which is integral with the output gear GO makes a positive rotation at a lower speed than the ring gear R1, and as a result, the third gear state in which the gear ratio is slightly smaller than the second gear described above. Become.

The fourth speed is set by engaging the first clutch K1 and the third clutch K3. Therefore, at the fourth speed, the ring gear R in the first planetary gear mechanism G1 is
1 and the ring gear R2 in the second planetary gear mechanism G2 are connected to the input shaft 1, and these planetary gear mechanism G1
, G2, the sun gears S1 and S2 are connected to each other, so that the planetary gear mechanisms G1 and G2 rotate as a whole. As a result, the output gear GO connected to the carriers C1 and C2 in these planetary gear mechanisms G1 and G2 rotates at the same speed as the input shaft 1. That is, the fourth speed, which is the direct connection stage, is set.

The fifth speed is set by releasing the first clutch K1 and engaging the second brake B2 from the state of the fourth speed. That is, while the ring gear R2 of the second planetary gear mechanism G2 is connected to the input shaft 1 by the third clutch K3, the sun gear S2 is fixed by the second brake B2. As a result, the carrier C2, which is integrated with the output gear GO, rotates forward at a higher speed than the ring gear R2 which is an input member, and as a result, the fifth speed, which is an overdrive stage having a gear ratio smaller than "1", is set. .

The sixth speed is set by releasing the second brake B2 and engaging the third brake B3 from the state of the fifth speed. That is, in the state of the fifth speed, the ring gear R3 of the third planetary gear mechanism G3 is rotating normally, but if this is fixed by the third brake B3 and a reaction torque is given, the fixed carrier C3 is reversed. As the sun rotates, the sun gear S3 is further accelerated and rotates in the normal direction.
As a result, the rotation speed of the output gear G0 increases, and the sixth speed, which is an overdrive stage having a smaller gear ratio than the fifth speed, is set.

To explain the reverse gear further, the reverse gear is set by engaging the second clutch K2 and the first brake B1. That is, the second planetary gear mechanism G
The sun gear S2 in 2 is connected to the input shaft 1, while the ring gear R2 is fixed. As a result, carrier C2
And the output gear G0 integrated with this is rotated with respect to the input shaft 1 to rotate, and the reverse gear is established. For reference, a collinear diagram of the gear transmission shown in FIG. 1 is shown in FIG.

FIG. 4 is a cross-sectional view showing the above-described gear transmission in a more specific form. An endon cover 3 is attached to the end of the casing 2 (the left end in FIG. 4). The boss 4 is formed in the center of the inner surface of the cover 3.
Of the third clutch K3 on the outer peripheral side of the boss 4.
The clutch drum 5 is rotatably fitted.
The clutch drum 6 of the first clutch K1 is arranged concentrically on the inner peripheral side of the clutch drum 5.
The clutch drums 5 and 6 are spline-fitted to the outer peripheral portion of the input shaft 1. The clutch drum 6 of the first clutch K1 also serves as the clutch hub of the third clutch K3, and the friction plate is spline-fitted to the inner peripheral surface of the outer peripheral cylindrical portion of the clutch drum 5 of the third clutch K3. Another friction plate alternately arranged with respect to this friction plate is spline-fitted to the outer peripheral surface of the outer peripheral cylindrical portion of the clutch drum 6 of the first clutch K1. A piston 7 that presses these friction plates in the axial direction is arranged on the inner peripheral side of the clutch drum 5 of the third clutch K3 so as to move back and forth in the axial direction. Reference numeral 8 in FIG. 4 is a return spring, which elastically presses the piston 7 to the left in FIG.

A first planetary gear mechanism G1 is arranged on the inner peripheral side of the clutch drum 6 in the first clutch K1. The ring gear R1 is opposed to the outer peripheral side cylindrical portion of the clutch drum 6 in the radial direction, and the friction plates spline-fitted to the ring gear R1 are alternately arranged in the axial direction. And the piston 9 that presses these friction plates
Is housed in the inner peripheral portion of the clutch drum 6 of the first clutch K1 so as to move back and forth in the axial direction. Reference numeral 10 in FIG. 4 is a return spring for the piston 9.

A second planetary gear mechanism G2 is arranged adjacent to the first planetary gear mechanism G1. The sun gear S1 of the first planetary gear mechanism G1 and the sun gear S2 of the second planetary gear mechanism G2 are formed on the outer peripheral portion of a common sun gear shaft 11 rotatably fitted to the outer peripheral side of the input shaft 1.
The pinion pin of the pinion meshed with the sun gear S2 in the second planetary gear mechanism G2 is the first planetary gear mechanism G1.
Integrated with the pinion pin in and carrier C2
It is connected to. Further, a friction plate is spline-fitted to the outer peripheral surface of the ring gear R2 in the second planetary gear mechanism G2, and another friction plate alternately arranged with respect to these friction plates is provided on the inner peripheral surface of the casing 2. The first brake B1 is formed by spline fitting. The piston 12 for engaging the first brake B1 is
A center support portion 13 projecting toward the inner peripheral side is held at an intermediate portion in the axial direction of the casing 2 so as to move back and forth in the axial direction. Incidentally, in FIG. 4, the pinion P2 meshing with the ring gear R2 in the second planetary gear mechanism G2 is omitted.

An outer race 15 for a pair of tapered roller bearings 14 is spline-fitted to the inner peripheral portion of the center support portion 13. One end of the outer race 15 is shown in FIG.
One-way clutch F1 is provided on the outer peripheral portion of the protruding portion. The outer race of the one-way clutch F1 is integrated with the ring gear R2 of the second planetary gear mechanism G2.

The output gear GO is arranged on the opposite side of the one-way clutch F1 with the center support portion 13 interposed therebetween, and has a cylindrical shaft portion 16 on the inner peripheral side thereof. A pair of tapered roller bearings 1
The bearing 14 is rotatably held by being fitted to the inner peripheral side of the bearing 4. Further, another sun gear shaft 17 is arranged on the inner peripheral side of the cylindrical shaft portion 16, and the sun gear shaft 17 and the cylindrical shaft portion 16 are spline-fitted. The left end of the sun gear shaft 17 in FIG. 4 is connected to the carrier C2, and the sun gear S3 of the third planetary gear mechanism G3 is formed at the right end of FIG. That is, the output gear GO
A third planetary gear mechanism G3 is arranged on the side opposite to the center support portion 13 with the center pinion interposed therebetween.

A friction plate is spline-fitted to the outer peripheral surface of the ring gear R3 in the third planetary gear mechanism G3, and another friction plate alternately arranged with respect to these friction plates is provided on the inner peripheral surface of the casing 2. The spline is fitted. The piston 18 that presses these friction plates is held by a hollow annular holder 19 attached to the inner peripheral surface of the casing 2 so as to move back and forth in the axial direction. A seat 20 is attached to an end portion of the piston 18 on the left side in FIG. 4, and a return spring 21 is provided between the seat 20 and the center support portion 13.
Is arranged. That is, here is the third brake B3
Are formed. As shown in FIG. 4, the seat 20 is curved so as to cover the outer peripheral side of the output gear GO, and is configured to receive the lubricating oil scattered from the output gear GO. Further, the carrier C3 of the third planetary gear mechanism G3 is spline-fitted to one end of the common sun gear shaft 11 described above, while the outer peripheral end of the carrier C3 is spline-fitted to a predetermined position of the clutch drum 22 of the second clutch K2. are doing.

The clutch drum 22 of the second clutch K2
Is rotatably fitted to the outer periphery of the boss portion of the pump cover 23, and a clutch hub 24 arranged concentrically with the clutch drum 22 is integrally connected to the input shaft 1. Friction plates spline-fitted to the clutch drum 22 and friction plates spline-fitted to the outer peripheral surface of the clutch hub 24 are alternately arranged in the axial direction, and the second clutch K2 is formed therein. . A piston 25 for pressing these friction plates is housed in the outer peripheral portion of the clutch drum 22 so as to move back and forth in the axial direction. Reference numeral 26 is a return spring.

As is known from the configuration shown in FIG. 4, in the above-described gear transmission, the center support portion 13 is sandwiched between the main transmission portion mainly including the first planetary gear mechanism G1 and the second planetary gear mechanism G2. By arranging the sub-transmission unit consisting of the double pinion type planetary gear mechanism on the opposite side, it is possible to set 6 forward gears. Therefore, it is suitable for an automatic transmission for FF vehicles that is compact, lightweight and multi-staged. A gear transmission can be obtained.

Next, another embodiment of the present invention will be described. FIG. 5 shows a second embodiment of the present invention, which is constructed by adopting a single pinion type as the third planetary gear mechanism G30. That is, the third planetary gear mechanism G30 mainly includes a sun gear S30, a ring gear R30 arranged concentrically with respect to the sun gear S30, and a carrier C30 rotatably holding a pinion P30 meshing with these gears S30, R30. The sun gear S30 is connected to the output gear GO and the carriers C1 and C2 in the first and second planetary gear mechanisms G1 and G2. The third brake B3 is arranged so as to selectively fix the carrier C30. Further, a second clutch K2 is arranged between the ring gear R30 and the input shaft 1, and the second brake B2 is configured to selectively fix the ring gear R30. The other configurations are the same as those shown in FIG. 1, and therefore, the same reference numerals as those in FIG.

Therefore, in the gear transmission shown in FIG. 5, the third planetary gear mechanism in the gear transmission shown in FIG. 1 is changed from the double pinion type to the single pinion type.
Since the connection relationship is changed accordingly, by engaging each friction engagement device as shown in FIG. 2 described above, it is possible to set a shift speed of 6 forward gears and 1 reverse gear. . For reference, an alignment chart of the gear transmission shown in FIG. 5 is shown in FIG.

Further, a more specific example of the gear transmission shown in FIG. 5 is shown in FIG. 7 as a sectional view. As described above, in the gear transmission shown in FIG. 5, the third planetary gear mechanism in the gear transmission shown in FIG. 1 is changed to the single pinion type, and the connection relationship is changed accordingly. The specific structure shown in FIG. 7 is almost the same as the structure shown in FIG. 4 described above. The difference from FIG. 4 is that the rotating element fixed by the third brake B3 is the third planetary gear mechanism G.
This is that the carrier C30 in 30 and the rotary element connected to the clutch drum 22 of the second clutch K2 are the ring gear R30 in the third planetary gear mechanism G30. Other configurations are the same as the configurations shown in FIG. Therefore, also in the gear transmission shown in FIG. 5 or 7, it is possible to provide a gear transmission for an automatic transmission that is small and lightweight and is capable of setting six forward gears and is suitable for an FF vehicle.

FIG. 8 shows still another embodiment. In the gear transmission shown here, the third planetary gear mechanism G31 is a double pinion type, and its carrier C31 is first and second. The planet gears G1 and G2 are connected to the carriers C1 and C2, the ring gear 31 is connected to the ring gear R2 of the second planetary gear mechanism G2, the carrier C31 is connected to the output gear GO, and the third
The sun gear S31 is selectively fixed by the brake B3. Other configurations are the same as the configurations shown in FIG.

FIG. 9 shows an alignment chart in the gear transmission shown in FIG. As is known from this collinear chart, by engaging each friction engagement device as shown in FIG. 2 described above, it is possible to set a shift speed of 6 forward gears and 1 reverse gear, and FIG. With the structure shown in FIG. 3, the three carriers are integrally connected, and the ring gear R31 of the third planetary gear mechanism G31 is connected to the ring gear R2 of the second planetary gear mechanism G2.
These planetary gear mechanisms G1 are connected integrally with
, G2, G31 are arranged close to each other and no special connecting means is required, so that it is possible to obtain a lightweight and compact gear transmission in which the length in the axial direction is further shortened.

In each of the above-mentioned embodiments, the one-way clutch F1 is arranged in parallel with the first brake B1. However, the one-way clutch can be appropriately adopted. A one-way clutch may be arranged in parallel with the fourth clutch K4 between the first clutch K1 and the ring gear R1 of the first planetary gear mechanism G1. One example is shown in FIG. 10, in which a one-way clutch F2 is arranged in parallel with the first clutch K1.
A fourth clutch K4, which is a multi-plate clutch, is arranged in series between the one-way clutch F2 and the input shaft 1. The fourth clutch K4 is disengaged in the reverse gear to allow the ring gear R1 to rotate in the reverse direction.

[0040]

As described above, according to the present invention,
A gear transmission mainly composed of a single pinion type planetary gear mechanism and a double pinion type planetary gear mechanism in which sun gears and carriers are connected to each other, and a double pinion type or single pinion type third planetary gear mechanism on the same axis line. Since it is arranged so that 6 forward stages can be set, it is possible to achieve multiple stages without using a counter shaft, and moreover, the output element can be set at the central portion in the axial direction. According to this invention, it is small and lightweight,
Moreover, it is possible to obtain a gear transmission suitable for a multi-stage FF vehicle. Further, according to the present invention, the first planetary gear mechanism and the second planetary gear mechanism are not configured as the Ravigneaux type planetary gear mechanism but independent planetary gear mechanisms are used, so that the degree of freedom in setting the gear ratio is increased. As a result, it is possible to obtain a secondary effect such as easy setting of the gear ratio according to the vehicle characteristics.

[Brief description of drawings]

FIG. 1 is a skeleton diagram showing an embodiment of the invention described in claim 1. FIG.

FIG. 2 is a chart showing an engagement operation state of each engagement means for setting each shift speed.

FIG. 3 is a nomographic chart thereof.

FIG. 4 is a partial cross-sectional view of a more specific embodiment.

5 is a skeleton diagram showing an embodiment of the invention described in claim 2. FIG.

FIG. 6 is a nomographic chart thereof.

FIG. 7 is a partial cross-sectional view of an embodiment in which the invention described in claim 2 is more embodied.

FIG. 8 is a skeleton diagram showing an embodiment of the invention described in claim 3;

FIG. 9 is a nomographic chart thereof.

10 is a skeleton diagram showing an example in which a second one-way clutch and a fourth clutch are added to the gear transmission shown in FIG.

[Explanation of symbols]

 G1 First planetary gear mechanism G2 Second planetary gear mechanism G3, G30, G31 Third planetary gear mechanism S1, S2, S3, S30, S31 Sun gear C1, C2, C3, C30, C31 Carrier R1, R2, R3, R30, R31 Ring gear GO Output gear B3 Third brake

Claims (3)

[Claims] 1. A single pinion type first planetary gear mechanism comprising a sun gear, a ring gear concentrically arranged with respect to the sun gear, and a carrier rotatably holding a pinion meshing with the sun gear and the ring gear,
A sun gear connected to the sun gear, a ring gear concentrically arranged with respect to the sun gear, and at least a pair of pinions rotatably arranged between the sun gear and the ring gear and meshed with each other are held in the carrier. A double pinion type second planetary gear mechanism including a connected carrier is arranged on the same axis,
Further, in the gear transmission in which the carriers connected to each other are connected to the output element, a sun gear, a ring gear concentrically arranged with respect to the sun gear, and the sun gear and the ring gear are rotatably arranged between the sun gear and the ring gear. A double pinion type third planetary gear mechanism including a carrier that holds at least a pair of meshed pinions is arranged on the same axis as each of the planetary gear mechanisms, and a sun gear and a third planetary gear mechanism of the first planetary gear mechanism. A ring gear of the planetary gear mechanism is connected, a carrier of the first planetary gear mechanism and a sun gear of the third planetary gear mechanism are connected, and a brake that selectively stops rotation of the ring gear of the third planetary gear mechanism is provided. A gear transmission characterized in that 2. A single pinion type first planetary gear mechanism comprising a sun gear, a ring gear concentrically arranged with respect to the sun gear, and a carrier rotatably holding a pinion meshing with the sun gear and the ring gear,
A sun gear connected to the sun gear, a ring gear concentrically arranged with respect to the sun gear, and at least a pair of pinions rotatably arranged between the sun gear and the ring gear and meshed with each other are held in the carrier. A double pinion type second planetary gear mechanism including a connected carrier is arranged on the same axis,
Further, in a gear transmission in which the carriers connected to each other are connected to an output element, a sun gear, a ring gear concentrically arranged with respect to the sun gear, and a carrier holding a pinion meshed with the sun gear and the ring gear are provided. The provided single pinion type third planetary gear mechanism is arranged on the same axis as each of the planetary gear mechanisms, and the sun gear of the first planetary gear mechanism and the ring gear of the third planetary gear mechanism are connected to each other. A gear transmission characterized in that a carrier of a planetary gear mechanism and a sun gear of a third planetary gear mechanism are connected to each other, and a brake that selectively stops rotation of the carrier of the third planetary gear mechanism is provided. 3. A single pinion type first planetary gear mechanism comprising a sun gear, a ring gear concentrically arranged with respect to the sun gear, and a carrier rotatably holding a pinion meshing with the sun gear and the ring gear,
A sun gear connected to the sun gear, a ring gear concentrically arranged with respect to the sun gear, and at least a pair of pinions rotatably arranged between the sun gear and the ring gear and meshed with each other are held in the carrier. A double pinion type second planetary gear mechanism including a connected carrier is arranged on the same axis,
Further, in the gear transmission in which the carriers connected to each other are connected to the output element, a sun gear, a ring gear concentrically arranged with respect to the sun gear, and the sun gear and the ring gear are rotatably arranged between the sun gear and the ring gear. A double pinion-type third planetary gear mechanism including a carrier that holds at least a pair of meshed pinions is arranged on the same axis as each of the planetary gear mechanisms, and a ring gear and a third planetary gear mechanism of the second planetary gear mechanism. A ring gear of the planetary gear mechanism is connected, a carrier of the first planetary gear mechanism and a carrier of the third planetary gear mechanism are connected, and a brake that selectively stops rotation of the sun gear of the third planetary gear mechanism is provided. A gear transmission characterized in that