JP3329095B2 - Gear transmission - Google Patents

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 an automatic transmission having a main transmission portion comprising a pair of single pinion type planetary gear mechanisms in which a carrier and a ring gear are interconnected. The present invention relates to a gear transmission.

[0002]

2. Description of the Related Art It is well known that a plurality of sets of planetary gear mechanisms are used in a gear transmission of an automatic transmission for a vehicle. By changing the way of using this planetary gear mechanism, specifically the number and the connection relationship of each rotating element,
The number of shift stages that can be set, the gear ratio, and the like can be changed more variously, and the outer diameter and length of the entire gear transmission vary greatly depending on the arrangement.

It is desirable that the automatic transmission or the gear transmission used for the transmission is basically small and lightweight. Therefore, when two sets of single pinion type planetary gear mechanisms are used, for example, their carrier and ring gear are required. In the past, a so-called "CR-CR" bond configuration for interconnecting the two has been widely used. This is because the planetary gear mechanisms can be arranged close to each other, and there are advantages such that four forward speeds with a gear ratio suitable for practical use can be set. On the other hand, in order to improve the power performance of the vehicle as a whole, in some cases, it is required to increase the number of shift stages that can be set in the automatic transmission. Therefore, for example, Japanese Patent Laid-Open No. 3-56746 discloses this. In this invention, a single-pinion type third planetary gear mechanism is further added to the two sets of single-pinion type planetary gear mechanisms of the "CR-CR" connection, and a total of six forward steps and two reverse steps are set. It is configured as possible.

[0004]

The gear ratio set in a gear transmission using a plurality of sets of planetary gear mechanisms depends on the gear ratio of the planetary gear mechanism involved in shifting (the number of teeth of the sun gear and the number of teeth of the ring gear). In general, it is desired that each gear ratio has a relationship close to a geometric series in order to improve the power performance of the entire vehicle and facilitate gear shift control. . On the other hand, the gear ratio in the planetary gear mechanism is limited by the difference in the inner and outer diameters that can be manufactured and the allowable outer diameter.

However, in the conventional gear transmission described above, if the gear ratios of the six forward gears are set so as to have a relationship close to a geometric series that can be practically used,
Any one of the gear ratios of the respective planetary gear mechanisms determined based on the value is usually small enough not to be used. In order to reduce the gear ratio of the planetary gear mechanism, it is necessary to reduce the diameter of the sun gear or increase the diameter of the ring gear, but the inner diameter of the sun gear is such that the input shaft or intermediate shaft Due to the disposition of the ring gear, it cannot be reduced to a certain degree or more, and therefore, in order to reduce the gear ratio, the outer diameter of the ring gear must be increased. ,
In order to obtain a suitable gear ratio, there is a disadvantage that one of the planetary gear mechanisms has a large diameter and the entire gear transmission has a large size.

In order to avoid such inconvenience, assuming that a planetary gear mechanism having a small outer diameter and a gear ratio generally used is used, the gear ratio at any one of the gears is assumed. The value greatly deviates from the value, in other words, the step width of the gear ratio (the ratio between the gear ratios)
However, there is a large difference between any one of the gears and the other step widths.
Alternatively, there is a possibility that shift control becomes difficult.

[0007] The present invention has been made in view of the above circumstances, and can be made compact and lightweight by taking advantage of the "CR-CR" connection, and can reduce shift shock or improve power performance. It is an object to provide a gear transmission.

[0008]

SUMMARY OF THE INVENTION In order to achieve the above-mentioned object, the present invention provides a main transmission section comprising a pair of single-pinion type planetary gear mechanisms of "CR-CR" connection.
The double pinion type planetary gear mechanism is arranged on the same axis as the third planetary gear mechanism, and is configured such that six forward gears can be set as a whole. That is , the present invention
Between the sun gear and the ring gear arranged on concentric circles
Where the pinion held by the carrier is located
A pair of single pinion type planetary gear mechanisms are
And one single pinion type planetary gear
Carrier and other single pinion type planet in mechanism
The ring gear in the gear mechanism is connected and one of the
Ring gear in single pinion type planetary gear mechanism
Carry in the other single pinion type planetary gear mechanism
In the gear transmission having a main transmission portion Ya and is ing is connected, coaxially with the third sun gear with respect to the third sun gear
A double pinion type third including a third ring gear arranged on a circle and a third carrier arranged between the third sun gear and the third ring gear and rotatably holding at least a pair of pinions meshing with each other. a planetary gear mechanism which is arranged on the same axis as the main transmission section, along with the carrier of one of the single-pinion type Yu Review gear in the main transmission section is connected to the third ring gear, and these carrier and a third ring gear Is connected to the output element,
One single pinion type in the main transmission portion
The sun gear of the Yu star gear mechanism is connected to the third sun gear, further brake for selectively fixing said third carrier provided et al is, the output element of the main transmission section and one
Rotates independently of each other, except for rotating elements that rotate as a body
To selectively input power to the three rotating elements
Is to shall and Features that have been made.

[0009]

In the gear transmission according to the present invention, the four forward gears can be set only by the main transmission portion, and the third carrier is input to the sun gear in a state where the third carrier is fixed by the brake, so that the third planetary gear is provided. The gear stage can be set only by the mechanism, and the gear ratio is determined by the gear ratio of the third planetary gear mechanism of the double pinion type. However, since a smaller gear ratio can be selected as compared with the single pinion type planetary gear mechanism, A second speed is set, the width of which is not particularly different from other step widths. If the fixed element in the state where the highest speed is set in the main transmission portion is rotated in the reverse direction by fixing the carrier of the third planetary gear mechanism, the output element rotates forward at a higher speed. As a whole, six forward speeds can be set. Further, the step widths of the speed ratios of the forward gears are approximate values.

[0010]

Next, the present invention will be described more specifically based on embodiments. In FIG. 1, a first planetary gear mechanism G1 and a second planetary gear mechanism
The planetary gear mechanism G2 is disposed adjacent to each other on the same axis, and a double pinion type third planetary gear mechanism G3
Are arranged on the same axis with respect to the first and second planetary gear mechanisms G1 and G2. The arrangement order of these planetary gear mechanisms G1, G2, G3 is such that the third planetary gear mechanism G3, the first planetary gear mechanism G1, and the second planetary gear mechanism G2 are arranged from the torque converter TC side with the lock-up clutch.

The first planetary gear mechanism G1 comprises a carrier C rotatably holding a sun gear S1, a ring gear R1 concentrically arranged with respect to the sun gear S1, and a pinion P1 meshing with the sun gear S1 and the ring gear R1.
1 is the main rotating element. Similarly, the second planetary gear mechanism G2 includes a carrier C2 rotatably holding a sun gear S2, a ring gear R2 concentrically arranged with respect to the sun gear S2, and a pinion P2 meshing with the sun gear S2 and the ring gear R2. Are the main rotating elements. Then, the carrier C1 of the first planetary gear mechanism G1 and the ring gear R2 of the second planetary gear mechanism G2 are connected, and the ring gear R1 of the first planetary gear mechanism G1 and the carrier C2 of the second planetary gear mechanism G2 are connected. The first and second planetary gear mechanisms G1 and G2 constitute a main transmission.

The third planetary gear mechanism G3 has a sun gear S3, a ring gear R3, and a carrier C3 rotatably holding at least a pair of pinions P3 disposed therebetween as main rotating elements. The ring gear R3 is connected to the carrier C1 of the first planetary gear mechanism G1, and the ring gear R3 and the carrier C1 are connected.
Are connected to an output gear (counter gear) GO as an output element, and a sun gear S3 is connected to a sun gear S1 of the first planetary gear mechanism G1.

Next, the clutch means and the brake means will be described. The input shaft 1 to which power is transmitted from the turbine runner of the torque converter TC is arranged along the center axis of each of the planetary gear mechanisms G1, G2, G3. A first clutch K1, which is a multi-plate clutch, is disposed between the input shaft 1 and the sun gear S3 of the third planetary gear mechanism G3. The carrier C2 of the input shaft 1 and the second planetary gear mechanism G2 are connected to each other. A second clutch K2, which is a multi-plate clutch, is disposed between the two. Further, the input shaft 1 and the first
A third clutch K3, which is a multi-plate clutch, is arranged between the planetary gear mechanism G1 and the sun gear S1.

As a braking means, a second planetary gear mechanism G
A second brake B2 for selectively fixing the sun gear S2 of the first planetary gear mechanism G1, a ring gear R1 of the first planetary gear mechanism G1 and a carrier C2 of the second planetary gear mechanism G2, and a third planetary gear. A third brake B3 for selectively fixing the carrier C3 of the gear mechanism G3 is provided.

In the above-described gear transmission, by engaging the clutch and the brake as shown in FIG. 2, it is possible to set six forward speeds and one reverse speed. In FIG. 2, a circle indicates an engaged state, and a blank indicates a released state. In FIG. 2, the specific value of the gear ratio is obtained by setting the gear ratio ρ1 of the first planetary gear mechanism G1 to “0.4”.
8 "and the gear ratio ρ2 of the second planetary gear mechanism G2 is set to" 0.3
7 "and the gear ratio ρ3 of the third planetary gear mechanism G3 is set to" 0.4
3 is a nomographic chart of the gear transmission having the configuration shown in FIG. 1. Each shift speed will be briefly described below.

The first forward speed is set by engaging the first clutch K1 and the second brake B2. That is, the input is made to the first sun gear S1 and set by fixing the ring gear R1. Therefore, in the first planetary gear mechanism 1, the sun gear S3 is rotated together with the input shaft 1 with the ring gear R1 fixed, so that the carrier C1 and the output gear GO integrated therewith are greatly reduced with respect to the input shaft 1. As a result, the motor rotates forward (rotation in the same direction as the input shaft 1) and becomes the first speed having the largest gear ratio in the forward gear. Therefore, the first speed is set only by the first planetary gear mechanism G1 of the main transmission section.

The second speed is changed from the state of the first speed to the second speed.
The setting is made by engaging the third brake B3 instead of the brake B2. That is, the signal is input to the sun gear S3 of the third planetary gear mechanism G3 and the third planetary gear mechanism G3
Carrier C3 is fixed. Therefore, in the third planetary gear mechanism G3, with the carrier C3 fixed, the sun gear S
3 rotates together with the input shaft 1, so that the ring gear R3 and the output gear gear GO integrated therewith are connected to the third planetary gear mechanism G3.
The speed is reduced according to the gear ratio .rho.3 to make a forward rotation, and the speed is changed to the second speed, which is slightly smaller than the first speed. That is, this second
The speed is set only by the third planetary gear mechanism G3.

The third speed is set by engaging the first brake B1 instead of the third brake B3 from the state of the second speed. That is, the sun gear S of the first planetary gear mechanism G1
1 and fix the sun gear S2 of the second planetary gear mechanism G2. Accordingly, in the first planetary gear mechanism G1, the load from the output gear GO is applied to the carrier C1, so that the ring gear R1 tries to rotate in the reverse direction (rotation in the opposite direction to the input shaft 1), and accordingly, the second planetary gear In the mechanism G2, the carrier C2 attempts to rotate in the reverse direction while the load from the output gear GO is applied to the ring gear R2, so that the sun gear S2 attempts to rotate in the reverse direction. However, since the sun gear S2 is fixed by the first brake B1, the carrier C2 rotates forward and the ring gear R
2 and the output gear GO integrated therewith rotate forward at a higher speed than in the case of the first speed. That is, the third speed is set. Therefore, the third speed is set only by the main transmission.

In the fourth speed, the first clutch K1 and the second clutch K2 are engaged. As a result, in the first planetary gear mechanism G1, the sun gear S1 and the ring gear R1 are connected to the input shaft 1
The output gear GO rotates at the same speed as the input shaft 1 as a whole. That is, the fourth speed, which is the directly connected stage, is established. Also in this case, the fourth speed is set only by the main transmission portion.

The fifth speed is set by engaging the second clutch K2 and the first brake B1. That is, the input is made to the carrier C2 of the second planetary gear mechanism G2, and the sun gear S2 is fixed. As a result, the carrier C2 and the output gear GO connected to the carrier C2 rotate forward at a higher speed than the carrier C2 and the input shaft 1, and are in the fifth speed, which is an overdrive stage. Therefore, the fifth speed is also set only by the main transmission.

The sixth speed is set by engaging the third brake B3 instead of the first brake B1 from the state of the fifth speed. That is, in the fifth speed state, in the third planetary gear mechanism G3, the ring gear R3 rotates forward at high speed together with the output gear GO, and accordingly the sun gear S3 rotates forward at higher speed, while the carrier C3 is driven by the input shaft. It is rotating forward at a speed lower than 1. Therefore, if the carrier C3 is fixed by the third brake B3 from this state, the ring gear R
3 and sun gear S3 are further accelerated, so that the second
The sixth speed, which is the overdrive stage, is set.

The reverse gear will be described. The reverse gear is set by engaging the third clutch K3 and the second brake B2. That is, the second planetary gear mechanism G
2 is connected to the input shaft 1 while its carrier C2 is fixed. As a result, the ring gear R2
And the output gear GO integrated therewith is rotated in reverse with respect to the input shaft 1, and the reverse gear is set.

Also in the gear transmission shown in FIG. 1 described above, a one-way clutch can be appropriately added to facilitate gear shifting control, and an example is shown in FIG. That is, a fourth clutch K4 is arranged in series with the first brake B1, and a first clutch K2 is provided between the first brake B1 and the carrier C2 of the second planetary gear mechanism G2.
One-way clutches F1 are arranged in series. Further, a second one-way clutch F2 is arranged in parallel with the first brake B1. That is, the first one-way clutch F1 and the second one-way clutch F2 are arranged in series between the carrier C2 and the predetermined fixed portion in the second planetary gear mechanism G2.

FIG. 5 shows an engagement operation table for the gear transmission shown in FIG. In addition, in FIG.
Indicates engagement during engine braking. As described above, the first speed is set by the ring gear R of the first planetary gear mechanism G1.
1 and the carrier C2 of the second planetary gear mechanism G2 integral therewith are fixedly set. In the configuration shown in FIG. 4, the first one-way clutch F1 and the second one-way clutch F2
Engages to fix the ring gear R1 and the carrier C2. Therefore, at the time of engine braking, the second brake B2 is a multi-disc brake having no direction of torque transmission.
Will be engaged. In the third speed, the second
Since the sun gear S2 of the planetary gear mechanism G2 is fixedly set, the second one-way clutch F2 is engaged with the engagement of the fourth clutch K4 to fix the sun gear S2. In this case, when the direction of the torque acting on the second one-way clutch F2 is reversed, this one-way clutch F2 is released, so that the first brake which is in parallel with the second one-way clutch F2 during engine braking. B1
Is engaged. In the fourth speed, the first clutch K1 and the second clutch
The clutch K2 can be engaged to rotate the entire first planetary gear mechanism G1 integrally.
The engagement of the clutch K4 causes the entire second planetary gear mechanism G2 to rotate integrally, and the torque is transmitted from the ring gear R2 to the output gear GO. Therefore, the torque applied to the first planetary gear mechanism G1 can be reduced. The other gears can be set in the same manner as in the gear transmission shown in FIG.

FIG. 6 shows a more specific example of the gear transmission shown in FIG. In FIG. 6, the casing 2
An annular center support portion 3 is protruded toward the center so as to divide the inside into two parts at the substantially middle portion in the axial direction. This center support section 3
6, the main transmission portion is disposed on the left side (opposite side of the torque converter) in FIG. 6, and the output gear GO and the third planetary gear mechanism G3 are disposed on the right side (torque converter side) of the center support portion 3. ing. That is, the first planetary gear mechanism G1 is disposed adjacent to the left side of the center support portion 3, and the second planetary gear mechanism G2 is also adjacent to the first planetary gear mechanism G2.
Is arranged. The cylindrical portion of the ring gear R1 in the first planetary gear mechanism G1 extends to the outer peripheral side of the second planetary gear mechanism G2, and the distal end portion thereof extends to the second planetary gear mechanism G2.
The carrier C2 is connected so as to rotate integrally. The ring gear R2 of the second planetary gear mechanism G2 is located on the inner peripheral side of the cylindrical portion of the ring gear R1 in the first planetary gear mechanism G1, and its end is connected to the carrier C1 of the first planetary gear mechanism G1 so as to rotate integrally. Have been.

A sun gear shaft 4 and a first connection shaft 5 are rotatably arranged on the outer peripheral side of an input shaft (intermeet shaft) 1 arranged along the center axis.
The first connecting shaft 5 is disposed on the left side (the shaft end side) of FIG. 6 with respect to the sun gear shaft 4, and the carrier C2 of the second planetary gear mechanism G2 is spline-fitted to one end thereof. The other end of the first connecting shaft 5 is connected to the second clutch K2. A second connecting shaft 6 is rotatably arranged on the outer peripheral side of the first connecting shaft 5.
A sun gear S2 of the second planetary gear mechanism G2 is formed at one end of the second connection shaft 6, and the other end of the second connection shaft 6 is connected to the third clutch K3 and the fourth clutch K3.
It is connected to the clutch K4.

A sun gear S3 of the third planetary gear mechanism G3 is formed at one end of the sun gear shaft 4, and a sun gear S1 of the first planetary gear mechanism G1 is splined at the other end of the sun gear shaft 4. Mated. A cylindrical shaft portion of the carrier C1 of the first planetary gear mechanism G1 is rotatably fitted on the outer peripheral side of the sun gear shaft 4. A cylindrical shaft portion of the output gear GO is mounted on the outer peripheral side of the cylindrical shaft portion of the carrier C1. The part is spline-fitted. The cylindrical shaft of the output gear GO and the cylindrical shaft of the carrier C1 are rotatably supported by a pair of tapered roller bearings 7 arranged on the inner periphery of the center support 3.

A plurality of friction plates are spline-fitted to the outer peripheral surface of the ring gear R1 in the first planetary gear mechanism G1, and another friction plate alternately arranged with these friction plates is connected to the inner peripheral surface of the casing 2. Is splined to
Here, a second brake B2 is formed. The piston 8 for pressing the friction plate in the second brake B2 is accommodated in a cylinder formed on the side surface of the center support 3 so as to be able to move back and forth. A cylindrical brake hub 9 is integrally connected to the carrier C3 of the third planetary gear mechanism G3.
A plurality of friction plates are spline-fitted on the outer peripheral surface of the casing 2, and other friction plates alternately arranged with respect to these friction plates are spline-fitted on the inner peripheral surface of the casing 2; The brake B3 is formed. The piston 10 for pressing the friction plate in the third brake B3
Is accommodated in a cylinder formed on the side surface of the center support portion 3 so as to be movable back and forth.

Further, the end of the sun gear shaft 4 on the torque converter side extends outward in the radial direction to form the clutch hub 1.
1 and a clutch drum 12 arranged concentrically with the clutch hub 11 is spline-fitted to the input shaft 1. One of the plurality of friction plates alternately arranged in the axial direction is spline-fitted to the outer peripheral surface of the clutch hub 11, and the other is the clutch drum 12.
Is spline-fitted to the inner peripheral surface of the first clutch K1 to form a first clutch K1. The piston 13 pressing the friction plate in the first clutch K1 is
2 so as to be movable back and forth.

FIG. 7 shows a modification of the gear transmission shown in FIG. 1 in which the arrangement of each of the planetary gear mechanisms G1, G2, G3 is changed, and the one-way clutch is actuated in a shift between adjacent gears. 1 shows a configured gear transmission. That is, the second planetary gear mechanism G2, the first planetary gear mechanism G1, and the third planetary gear mechanism G3 are arranged in this order from the torque converter TC side, and the carrier C2 of the second planetary gear mechanism G2 is selectively fixed. A one-way clutch F3 is arranged in parallel with the second brake B2, and a fifth clutch K5 and a one-way clutch, which are a multi-plate clutch, are provided between the carrier C2 and the ring gear R1 of the first planetary gear mechanism G1. F4 are arranged in series. Further, a sixth clutch K6, which is a multi-plate clutch, is arranged in parallel with the fifth clutch K5 and the one-way clutch F4. On the other hand, the carrier C3 of the third planetary gear mechanism G3
The fourth brake B4, which is a multi-plate brake, and the one-way clutch F5, which are arranged in series with each other, are arranged in parallel with the third brake B3, which selectively locks the third brake B3. The sun gear S1 of the first planetary gear mechanism G1 and the sun gear S3 of the third planetary gear mechanism G3 are directly connected to the input shaft 1. The other configuration is the same as the configuration shown in FIG. 1, and therefore, the same reference numerals as in FIG. 1 are assigned to FIG. 7, and the description thereof will be omitted.

In the gear transmission shown in FIG.
One reverse gear can be set, and the alignment chart is shown in FIG. 8 and the engagement operation table is shown in FIG. In addition, in the engagement operation table of FIG. 9, a mark indicates that the engagement does not affect the transmission of torque.

As can be seen from these figures, the forward first
When the fifth clutch K5 is engaged, the one-way clutch F4 in series with the fifth clutch K5 is engaged, and the "CR-CR" connection between the first planetary gear mechanism G1 and the second planetary gear mechanism G2 is established. Is established, the third one-way clutch F3 is engaged, and the ring gear R1 of the first planetary gear mechanism G1 and the carrier C2 of the second planetary gear mechanism G2 are fixed. That is, in the first planetary gear mechanism G1, the sun gear S1 is rotated as an input element in a state where the ring gear R1 is fixed, so that the first speed is set as in the gear transmission shown in FIG.

When the fourth brake B4 is engaged from the state of the first speed, the fifth one-way clutch F5 arranged in series with the fourth brake B4 is engaged, and the carrier C3 of the third planetary gear mechanism G3 is fixed. As a result, the ring gear R1 of the first planetary gear mechanism G1 and the carrier C2 of the second planetary gear mechanism G2 rotate forward, thereby releasing the third one-way clutch F3 which fixed them. Even in this state, the fourth one-way clutch F4 is engaged and the "CR-C" of the first planetary gear mechanism G1 and the second planetary gear mechanism G2 is engaged.
Therefore, in the third planetary gear mechanism G3, since the sun gear S3 rotates as an input element with the carrier C3 fixed, the third planetary gear mechanism G3 has the same configuration as the gear transmission shown in FIG. The second forward speed is achieved, that is, the upshift from the first speed to the second speed is achieved by engaging the fourth brake B4.

The third speed shifts from the second speed state to the first brake B
1 is engaged to fix the sun gear S2 in the second planetary gear mechanism G2. Also in this case the first
"CR-" between the planetary gear mechanism G1 and the second planetary gear mechanism G2.
When the first brake B1 is engaged, the carrier C3 in the third planetary gear mechanism G3 starts to rotate forward, so that the one-way clutch F5 fixing the carrier C3 is released. As a result, a state is established in which the sun gear S1 of the first planetary gear mechanism G1 is used as an input element and the sun gear S2 of the second planetary gear mechanism G2 is fixed, as in the gear transmission shown in FIG. 3
Speed is set.

The fourth speed is a so-called direct connection stage, in which the first brake B1 is released from the third speed state and the second speed is engaged.
It is set by engaging the clutch K2. Also in this case, the "CR-CR" connection between the first planetary gear mechanism G1 and the second planetary gear mechanism G2 is established, and therefore the sun gear S
1 and the ring gear R1 are connected to the input shaft 1. As a result, the respective planetary gear mechanisms G1, G2, G3 rotate together with the input shaft 1 to form a directly connected stage.

The fifth forward speed is the first speed in the fourth speed state.
It is set by engaging the brake B1. Therefore, in the second planetary gear mechanism G2, the sun gear S2
Is fixed, the carrier C2 becomes an input element and rotates together with the input shaft 1, so that the ring gear R2 is accelerated with respect to the input shaft 1 and rotates forward. Since the ring gear R2 is connected to the carrier C1 of the first planetary gear mechanism G1, the sun gear S1 rotates together with the input shaft 1 in the first planetary gear mechanism G1 and the carrier C1 is accelerated faster than the input shaft 1. As a result, the ring gear R1 rotates forward at a higher speed than the carrier C2. As a result, the fourth one-way clutch F4 is released, and the connection between the ring gear R1 and the carrier C2 is released. Therefore, the output gear G connected to the carrier C1 of the first planetary gear mechanism G1 and the ring gear R2 of the second planetary gear mechanism G2.
0 is accelerated more than the input shaft 1 and rotates forward, and the fifth speed, which is an overdrive stage, is set.

The reverse speed is set by engaging the third clutch K3 and the second brake B2. Therefore, in the second planetary gear mechanism G2, the sun gear S2 is rotated together with the input shaft 1 while the carrier C2 is fixed, so that the ring gear R2 and the output gear G0 connected thereto are opposite to the input shaft 1. , The reverse gear is set. In this case, in the first planetary gear mechanism G1, the ring gear R1 reversely rotates at a higher speed than the output gear G0, but the fifth clutch K5 is released and the connection with the second planetary gear mechanism G2 is released.

In the gear transmission shown in FIG. 7, it is necessary to change both the engagement and disengagement states of the second clutch K2 and the first brake B1 during the shift between the third speed and the fourth speed. However, it can be configured to solve this, and an example is shown in FIG. That is, in the example shown in FIG. 10, a fifth brake B5, which is a multi-disc brake, and a one-way clutch F6 arranged in series with the fifth brake B5 are arranged in parallel with the first brake B1. The arrangement is changed to be suitable for an engine rear-wheel drive vehicle). Therefore, the torque converter TC is disposed on an axis parallel to the central axis of each of the planetary gear mechanisms G1, G2 G3, and the turbine runner and the input shaft 1 are connected by a transmission mechanism TF such as a silent chain. Other configurations are the same as those of the gear transmission shown in FIG. 7, and therefore, the same reference numerals as in FIG.

The alignment chart of the gear transmission shown in FIG. 10 is the same as that of FIG. 8, and the engagement operation table is shown in FIG. As is known from FIG. 11, in the gear transmission shown in FIG. 10, since the fifth brake B5 and the one-way clutch F6 are arranged in parallel with the first brake B1, when setting the third speed, the power is reduced. In the ON state, the one-way clutch F6 is engaged with the engagement of the fifth brake B5 to fix the sun gear S2 of the second planetary gear mechanism G2. When the second clutch K2 is engaged from this state, the second clutch
Because the sun gear S2 of the planetary gear mechanism G2 rotates forward,
The one-way clutch F6 is released. That is, when upshifting from the third speed to the fourth speed, the second clutch K2 may be engaged, and as a result, the one-way clutch is actuated in all the first to fifth speeds to change the speed. Can be performed. The control of engagement / disengagement of the friction engagement device when setting another shift speed is the same as that of the gear transmission shown in FIG. 7 described above.

It should be noted that the present invention is not limited to the above-described embodiment, and that a one-way clutch or a multi-plate type frictional engagement device can be further added, and each planetary gear mechanism is described above. The second planetary gear mechanism G2, the third planetary gear mechanism G3, and the first planetary gear mechanism G1 may be arranged in this order from the torque converter TC side.

[0041]

As described above, according to the present invention,
A double-pinion type third planetary gear mechanism is added to a main transmission section comprising a pair of single-pinion type planetary gear mechanisms in a so-called "CR-CR " connection , and the ring gear is connected to the output element and one of the main transmission section. connected to the carrier, and connecting the sun gear to one of the sun gear in the main transmission section, and the carrier of the third planetary gear mechanism selectively fixed by a brake, also another in the main transmission section
Of the rotating elements that rotate independently
Since it is configured you to enter the power into three rotary elements is not, even if set to a range of the gear ratio used the gear ratio of the planetary gear mechanism generally, the step width of the gear ratio of each shift speed As a result, according to the present invention, it is possible to obtain a small and lightweight gear transmission in which shift shock is small or shift control is easy.

[Brief description of the drawings]

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

FIG. 2 is a table showing an engagement operation table.

FIG. 3 is an alignment chart thereof.

FIG. 4 is a skeleton diagram showing another embodiment in which a one-way clutch is additionally installed.

FIG. 5 is a table showing an engagement operation table.

FIG. 6 is a partial sectional view more specifically showing the gear transmission shown in FIG. 4;

FIG. 7 is a skeleton diagram of an example in which the connection between the ring gear of the first planetary gear mechanism and the carrier of the second planetary gear mechanism can be selectively released.

FIG. 8 is an alignment chart of the gear transmission shown in FIG. 7;

FIG. 9 is a table showing the engagement operation table.

FIG. 10 is a skeleton diagram showing an example in which a one-way clutch is operated in all shifts between adjacent shift speeds.

FIG. 11 is a table showing an engagement operation table.

[Explanation of symbols]

 G1 First planetary gear mechanism G2 Second planetary gear mechanism G3 Third planetary gear mechanism S1, S2, S3 Sun gears C1, C2, C3 Carriers R1, R2, R3 Ring gear GO Output gear B3 Third brake

──────────────────────────────────────────────────続 き Continuation of the front page (56) References JP-A-2-102954 (JP, A) (58) Fields investigated (Int. Cl. ⁷ , DB name) F16H 3/00-3/78

Claims (1)

(57) [Claims] A sun gear disposed concentrically with each other;
Pinion held by carrier between ring gear
Single pinion type planetary gear mechanism
Are arranged on the same axis and one single
Carrier and the other thing in the nonion type planetary gear mechanism
Connects to ring gear in lupinion type planetary gear mechanism
And one single pinion type planetary gear mechanism
Ring gear and the other single pinion type planetary gear
In the gear transmission having a main transmission section and a carrier ing linked in structure, the third ring gear and of those which are distribution <br/> location coaxially yen to the third sun gear and the third sun gear A third pinion type planetary gear mechanism including a third carrier disposed between the third sun gear and the third ring gear and rotatably holding at least a pair of pinions meshing with each other, on the same axis as the main transmission portion. disposed along with the carrier of one of the single-pinion type Yu Review gear in the main transmission section is connected to the third ring gear, the carrier and the third ring gear is connected to the output element and said main transmission section One single in
Pinion type sun gear of the Yu star gear mechanism is connected to the third sun gear, rotated further said third carrier selectively fixed to brake provided et al is, together with the output element of the main transmission section
Three independent rotating elements other than rotating elements
The speed change gear shall be the feature that it is configured to selectively enter a power to the element.