JP2890498B2 - Gearbox for automatic transmission - Google Patents

Description

Description: BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a gear transmission used in an automatic transmission for a vehicle, and in particular, to a gear transmission mainly composed of three sets of single pinion type planetary gear mechanisms. It concerns the device.

2. Description of the Related Art As is well known, a planetary gear mechanism has three elements of a sun gear, a ring gear, and a carrier that holds a pinion gear meshing with the sun gear, and any one of the elements is used as an input element and the other is output. By fixing the remaining elements as elements and further increasing the input rotation,
Alternatively, the output can be output with forward rotation reduction or reverse rotation reduction. Therefore, conventionally, generally, a plurality of planetary gear mechanisms are combined to constitute a gear transmission for an automatic transmission. In that case, how to combine the planetary gear mechanism, the value of the gear ratio of the planetary gear mechanism (ratio of the number of teeth between the sun gear and the ring gear), and use a single pinion type planetary gear mechanism or use a double pinion type planetary gear mechanism Depending on whether the gear ratio is obtained, the resulting gear ratio varies in various ways, but not all combinations are practical.From various conditions such as vehicle mountability, manufacturing potential, gear shifting characteristics, and required power performance, etc. The gear trains that are of practical use are limited. In other words, the gear train satisfies various conditions required for an automatic transmission for a vehicle because a huge number of configurations are possible depending on the combination of the planetary gear mechanism and the setting of the gear ratio. There is a great deal of difficulty in creating.

Conventionally, a number of gear transmissions devised under such a background have been proposed, and among them, a device using three sets of planetary gear mechanisms is disclosed in, for example, JP-A-60-88252 and JP-A-60-88252.
Nos. 1-48062 and 54-132058.

Problems to be Solved by the Invention The gear transmission described in the above-mentioned Japanese Patent Application Laid-Open No. 60-88252 discloses a combination of three sets of single pinion type planetary gear mechanisms to set five forward speeds and one reverse speed. It is configured to be able to do so. However, in this gear transmission,
If the gear ratio of each planetary gear mechanism is set such that the gear ratio of each gear is close to a geometric series in order to prevent a significant decrease in the driving force of the vehicle before and after the gear shift, the gear of any one of the planetary gear mechanisms is set. The ratio must be set to a significantly higher value,
As a result, there arises a problem that the outer diameter of the planetary gear mechanism is increased, and conversely, if the gear ratio of each planetary gear mechanism is set to such a degree that the outer diameter dimension does not particularly increase, the gear ratio of each speed step will be increased. There is a problem in that the relationship is not close to the geometric series, and the power performance of the vehicle is deteriorated.

Further, the gear transmission described in Japanese Patent Application Laid-Open No. 51-48062 is a combination of two sets of single pinion type planetary gear mechanisms and one set of double pinion type planetary gear mechanisms to provide five forward speeds and two reverse speeds. It is configured to be able to set the gear position. However, in this gear transmission, the two clutch means and the two brake means are used for shifting between the first forward speed and the second forward speed, and for shifting between the second and third speeds. It is necessary to change the engagement / disengagement state of the four engagement means in total, which causes a problem that the shift shock is deteriorated or complicated shift control is required.

Further, the gear transmission described in the above-mentioned Japanese Patent Application Laid-Open No. 54-132058 includes a set of a Ravigneaux type planetary gear mechanism and a set of a single pinion type planetary gear mechanism, or two sets of a single pinion type planetary gear mechanism. It is configured to be able to set five forward speeds and one reverse speed by combining with a set of double pinion type planetary gear mechanisms. However, in this gear transmission, a large load torque is applied to the sun gear of each planetary gear mechanism at the first and second forward speeds and the reverse speed, which is disadvantageous in terms of strength and durability. Since power circulation occurs, this is disadvantageous in terms of strength and durability, and also has a disadvantage that power transmission efficiency is deteriorated. Further, when three brake means are required and the number is reduced to two to simplify the configuration, the load torque of a predetermined clutch means is increased and its durability is reduced, or the clutch means is not used. In this case, the transmission capacity of the vehicle must be increased, and a double pinion type planetary gear mechanism is required.

The present invention has been made in view of the above circumstances,
It is an object of the present invention to provide a gear transmission capable of simplifying the configuration by reducing the number of engagement means required for shifting and simultaneously facilitating control.

Means for Solving the Problems In order to achieve the above object, the present invention provides three sets of single pinion type planetary gear mechanisms each having a sun gear, a ring gear, and a carrier holding a pinion gear meshing with the sun gear and the ring gear. The ring gear of the first planetary gear mechanism and the carrier of the second planetary gear mechanism are always connected or selectively connected via engaging means, and the carrier of the first planetary gear mechanism and the third planetary gear mechanism are connected to each other.
The ring gear of the planetary gear mechanism is always connected or selectively connected via an engaging means, and the sun gear of the first planetary gear mechanism and the carrier of the third planetary gear mechanism are always connected or via the engaging means. And the sun gear of the second planetary gear mechanism and the sun gear of the third planetary gear mechanism are always connected or selectively connected via engagement means. It is.

In the apparatus of the present invention, the ring gear of the first planetary gear mechanism and the carrier of the second planetary gear mechanism are integrated with each other or individually, and the carrier of the first planetary gear mechanism and the ring gear of the third planetary gear mechanism are mutually connected. The sun gear of the first planetary gear mechanism and the carrier of the third planetary gear mechanism may be integrated with or separately from each other, and may be integrated with each other or separately, and also the sun gear of the second planetary gear mechanism and the third planetary gear mechanism. The sun gears may be integral or separate from each other and serve as input or output elements or fixed elements, respectively, and independent elements such as the ring gear of the second planetary gear mechanism may be input or output elements or fixed elements. As a result, each of the planetary gear mechanisms integrally or independently performs the acceleration / deceleration action, and changes the speed of the rotation of the input shaft, or transmits the rotation of the input shaft to the output shaft as it is or in reverse.

Embodiment Next, an embodiment of the present invention will be described with reference to the drawings.

FIG. 1 is a schematic view showing the principle of an embodiment of the present invention. In the gear transmission shown here, first to third planetary gear mechanisms 1, 2, and 3 are formed by a single pinion type planetary gear mechanism. Each of these planetary gear mechanisms 1, 2, 3
Are connected as follows.
That is, each of the planetary gear mechanisms 1, 2, and 3 has a sun gear 1S, 2S, 3S
And ring gears 1R, 2R, 3R concentrically arranged with the sun gears 1S, 2S, 3S, and carriers 1C, 2C, which hold pinion gears meshing with the sun gears 1S, 2S, 3S and the ring gears 1R, 2R, 3R, It is configured with 3C as the main element. The ring gear 1R of the first planetary gear mechanism 1 and the carrier 2C of the second planetary gear mechanism 2 are connected so as to rotate integrally, and the carrier 1C of the first planetary gear mechanism 1 and the third planetary gear mechanism 3 And a ring gear 3R of the first planetary gear mechanism 1
And the carrier 3C of the third planetary gear mechanism 3 are connected so as to rotate integrally. On the other hand, the second planetary gear mechanism 2
A fourth clutch means K4 is provided between the sun gear 2S of the third planetary gear mechanism 3 and the sun gear 3S of the third planetary gear mechanism 3.
S and 3S are selectively connected to each other. Further, a second clutch means K2 is disposed between the sun gear 2S of the second planetary gear mechanism 2 and the carrier 3C of the third planetary gear mechanism 3, and the second clutch means K2 and the sun gear 2S of the second planetary gear mechanism 2 The third planetary gear mechanism 3 is selectively connected to a carrier 3C.

In addition, as a connection structure of the above-described components, a connection structure employed in a general automatic transmission such as a hollow shaft, a solid shaft, or an appropriate connecting drum can be employed.

The input shaft 4 is connected to an engine (not shown) via a power transmission means (not shown) such as a torque converter and a fluid coupling, and the input shaft 4 and the ring gear 2R of the second planetary gear mechanism 2 are connected to each other. In between, the first to selectively connect the two
A clutch means K1 is provided, and a third clutch means K3 for selectively connecting the input shaft 4 and the sun gear 2S of the second planetary gear mechanism 2 is provided between the input shaft 4 and the sun gear 2S.

The above-mentioned clutch means K1, K2, K3, K4 are, in effect, for selectively connecting and disconnecting the above-described members, and are generally used in conventional automatic transmissions such as a hydraulic servo mechanism. A wet multi-plate clutch that is engaged / disengaged by the adopted mechanism, a one-way clutch, or a configuration in which these wet multi-plate clutches and one-way clutches are arranged in series or in parallel are used as necessary. be able to. In practical use, there is a restriction on the arrangement of each component, so that an appropriate intermediate member such as a connecting drum can be interposed as a connecting member to each clutch means K1, K2, K3, K4.

A sun gear of the first planetary gear mechanism 1 connected to each other;
First brake means B1 for selectively preventing rotation of carrier 1C and carrier 3C of third planetary gear mechanism 3 includes carrier 3C and a transmission case (hereinafter simply referred to as a case) 6.
And is provided between them. Second brake means B2 for selectively preventing rotation of sun gear 3S of third planetary gear mechanism 3
Is provided between the sun gear 3S and the case 6. These brake means B1 and B2 are composed of a wet multi-plate brake or a band brake driven by a hydraulic servo mechanism or the like employed in a conventional general automatic transmission, a one-way clutch, or a combination thereof. And, in practice, these braking means
It goes without saying that an appropriate connecting member can be interposed between B1 and B2 and each element to be fixed by these brake means B1 and B2, or between the case 6 and B1.

An output shaft 5 for transmitting rotation to a propeller shaft and a counter gear (not shown) is connected to the carrier 1C of the first planetary gear mechanism 1 and the ring gear 3R of the third planetary gear mechanism 3 which are connected to each other. ing.

In the gear transmission configured as described above, five forward speeds and one reverse speed, or seven forward speeds and one reverse speed can be shifted.
1, K2, K3, K4 and the brake means B1, B2 are engaged as shown in Table 1. Table 1 also shows the gear ratios of the respective gears and their specific values, and the specific values are the gear ratios ρ1, of the planetary gear mechanisms 1, 2, and 3.
Let ρ2, ρ3 be ρ1 = 0.398, ρ2 = 0.456, ρ3 = 0.365
This is the value when In Table 1, a circle indicates that the vehicle is in the engaged state, and a cross indicates that the vehicle is in the released state. In the following, the case of setting five forward speeds and one reverse speed will be described first, and then two shift speeds that can be added to them will be described.

<< First Forward Speed >> The first clutch means K1, the fourth clutch means K4, and the first brake means B1 are engaged. That is, the ring gear 2R of the second planetary gear mechanism 2 is connected to the input shaft 4, the sun gear 2S of the second planetary gear mechanism 2 and the sun gear 3S of the third planetary gear mechanism 3 are connected by the fourth clutch means K4, and The sun gear 1S of the first planetary gear mechanism 1 and the carrier 3C of the third planetary gear mechanism 3 connected thereto are fixed. Therefore, in the second planetary gear mechanism 2, the ring gear 2R
Rotates together with the input shaft 4 to rotate the carrier 2C forward (rotation in the same direction as the input shaft 4; the same applies hereinafter) and rotate the sun gear 2S in reverse (rotation in the opposite direction to the input shaft 4; the same applies hereinafter). I do. As a result, in the first planetary gear mechanism 1, since the ring gear 1R is connected to the carrier 2C of the second planetary gear mechanism 2 and the sun gear 1S is fixed, the carrier 1C rotates forward at a lower speed than the ring gear 1R. In the third planetary gear mechanism 3, the sun gear 3S is connected to the sun gear 2S of the second planetary gear mechanism 2 and the carrier 3C is fixed, so that the ring gear 3R rotates forward. As a result, the output shaft 5 connected to the carrier 1C of the first planetary gear mechanism 1 and the ring gear 3R of the third planetary gear mechanism 3 is reduced in speed with respect to the input shaft 4 together with the carrier 1C and the ring gear 3R, and rotates forward. , The first speed having the largest gear ratio in the forward gear. Then, as shown in Table 1, the speed ratio is represented by (1 + ρ ₁ ) + ρ ₂ (1 + ρ ₃ + ρ ₁ ρ ₃ ) / ρ ₃ , and its specific value is 3.285. In this case, no power circulation occurs.

<< Second Forward Speed >> The first and second clutch means K1, K2 and the first brake means B1 are engaged. That is, in the first forward speed state, the second clutch means K2 is engaged instead of the fourth clutch means K4. In this case, the sun gear 2S of the second planetary gear mechanism 2 is connected to the sun gear 1S of the first planetary gear mechanism 1 and the carrier 3C of the third planetary gear mechanism 3 by the second clutch means K2. Since the first sun gear 1S and the carrier 3C of the third planetary gear mechanism 3 are fixed by the first brake means B1, the second clutch means K2 substantially acts as a brake, and the second planetary gear mechanism 2
Sun gear 2S is fixed. Accordingly, in the second planetary gear mechanism 2, the ring gear 2R rotates together with the input shaft 4 with the sun gear 2S fixed, so that the carrier 2C is reduced in speed with respect to the input shaft 4 and rotates forward.
Of the first planetary gear mechanism 1
In this case, since the ring gear 1R slowly rotates forward with the sun gear 1S fixed, the carrier 1C is decelerated relative to the ring gear 1R and rotates forward. As a result, the first
The output shaft 5 connected to the carrier 1C of the planetary gear mechanism 1 is decelerated with respect to the input shaft 4 and rotates forward to reach the second forward speed. In this case, the third planetary gear mechanism 3 includes a sun gear 3S
Is not connected to the sun gear 2S of the second planetary gear mechanism 2 and the case 6, so that no particular acceleration / deceleration action is performed. Therefore, the gear ratio in this case is represented by (1 + ρ ₁ ) (1 + ρ ₂ ) as shown in Table 1, and its specific value is 2.035. Also in this case, no power circulation occurs.

<< Third forward speed >> The first clutch means K1 and the third clutch means K3 and the first
The brake means B1 is engaged. That is, in the state of the second speed, the third clutch means K3 is engaged instead of the second clutch means K2. Therefore, the sun gear 1S of the first planetary gear mechanism 1
The carrier 3C of the third planetary gear mechanism 3 and the sun gear 2S of the second planetary gear mechanism 2 are disconnected from each other, and similarly, the sun gear 2S of the second planetary gear mechanism 2 and the third planetary gear mechanism 3
Is disconnected from the sun gear 3S. In the second planetary gear mechanism 2, the ring gear 2R and the sun gear 2S rotate together with the input shaft 4, so that the whole of the ring gear 2R and the sun gear 2S integrally rotates forward at the same speed as the input shaft 4, and accordingly, the second planetary gear mechanism 2 The ring gear 1R of the first planetary gear mechanism 1 connected to the second carrier 2C rotates forward at the same speed as the input shaft 4. In the first planetary gear mechanism 1, the sun gear
Since 1S is fixed, when the ring gear 1R rotates forward at the same speed as the input shaft 4, the carrier 1C is decelerated with respect to the input shaft 4 and rotates forward. In the third planetary gear mechanism 3, the sun gear 3S is the case 6 and the second
Since the sun gear 2S of the planetary gear mechanism 2 is not connected to the sun gear 2S, no particular acceleration / deceleration action is performed. Therefore, in this case, substantially only the first planetary gear mechanism 1 performs a deceleration operation, and reduces the rotation of the input shaft 4 and transmits the rotation to the output shaft 5. The transmission ratio is represented by (1 + ρ ₁ ) as shown in Table ₁ , and its specific value is 1.398. No power circulation occurs.

<< Fourth forward speed >> At least any three of the first to fourth clutch means K1, K2, K3, K4 are engaged, and the brake means B
Release 1, B2. That is, for example, in the state of the third speed, the first
Instead of the brake means B1, the second clutch means K2 is engaged or the fourth clutch means K4 is engaged. In this case, the first to third clutch means K1 to K3 are engaged,
Alternatively, the first, third and fourth clutch means K
If at least three clutch means such as 1, K3, and K4 are engaged, the entire gear train rotates together with the input shaft 4 and no speed-up or deceleration action occurs. It becomes “1”. Then, for example, by engaging the first to third clutch means K1, K2, K3, the driving force from the input shaft 4 can be transmitted to the output shaft 5 without causing power circulation.

<< Fifth Forward Speed >> The second and third clutch means K2, K3 and the second brake means B2 are engaged. That is, the first to third clutch means K1 to K3 are engaged in the fourth speed state, and the second brake means B2 is engaged in place of the first clutch means K1 in that state. Therefore, in the third planetary gear mechanism 3, the carrier 3C rotates together with the input shaft 4 with the sun gear 3S fixed, so that the speed of the ring gear 3R is increased with respect to the input shaft 4 to rotate forward. In this case, in the second planetary gear mechanism 2, the ring gear 2R is not connected to the input shaft 4, and the ring gear 1R of the first planetary gear mechanism 1 is connected to the carrier 2C. The first planetary gear mechanism 1 and the second planetary gear mechanism 2 particularly perform an acceleration / deceleration action. As a result, the rotation of the input shaft 4 is substantially increased in speed only by the third planetary gear mechanism 3 and transmitted to the output shaft 5, and the speed ratio is 1 / (1 + ρ ₃ ) as shown in Table 1. ), And its specific value is 0.733. Also in this case, no power circulation occurs.

<< Reverse >> The third and fourth clutch means K3, K4 are engaged with the first brake means B1. That is, the sun gear 3S of the third planetary gear mechanism 3 and the sun gear 2S of the second planetary gear mechanism 2 are connected to the input shaft 4, and the carrier 3C of the third planetary gear mechanism 3 and the sun gear 1S of the first planetary gear mechanism 1 are connected. Fix it. In this case, since the carrier 2C of the second planetary gear mechanism 2 is not connected to the input shaft 4,
As in the case of the speed, the second planetary gear mechanism 2 and the first planetary gear mechanism 1 do not particularly participate in the acceleration / deceleration action. In the third planetary gear mechanism 3, the sun gear 3S rotates together with the input shaft 4 with the carrier 3C fixed, so that the ring gear 3R rotates in reverse at a lower speed than the input shaft 4. That is, in this case, the rotation of the input shaft 4 is substantially decelerated and inverted by only the third planetary gear mechanism 3 and transmitted to the output shaft 5, and the reverse gear is set. The gear ratio in this case is represented by −1 / ρ _{3 as shown} in Table 1, and its specific value is −2.740. In this case, power circulation does not occur.

As is apparent from the above description of the first to fifth forward speeds and the reverse speed, the gear transmission shown in FIG. 1 requires five forward speeds and one reverse speed. Since the gear ratio in the forward gear can be set to a relationship close to a geometric series, there is no significant decrease in driving force before and after gear shifting, and the power performance of the vehicle can be improved. Since the gear ratio of the mechanisms 1, 2, and 3 can be set to an appropriate value of about 0.36 to 0.46, the diameter of the planetary gear mechanism does not increase, and three sets of single pinion type planetary gear mechanisms are mainly used. Since it can be configured, a compact gear transmission can be provided. Further, as described in the description of each gear, when shifting to another adjacent gear, it is only necessary to release any one of the engaging means and to engage the other engaging means. Since the shift in the gear can be performed by switching the two engagement means, the control for the shift is easy, and at the same time, it is possible to improve the shift shock. Furthermore, since there is no power circulation, the transmission efficiency of the driving force is good, and the relative rotation speed of the pinion gear with respect to the carrier is low, the load torque of each gear and each engagement means is small, and the rotation speed of each gear is low. Thus, a compact gear transmission having excellent durability can be provided. In addition, the gear ratio in the overdrive stage is set to about 0.733 to improve power performance, fuel consumption and quietness during high-speed driving, and the gear ratio in the reverse gear is set to about -2.740. As a result, a sufficient driving force can be secured. Since the input shaft 4 and the output shaft 5 can be arranged on the same axis, a gear transmission suitable for an FR vehicle (front-engine rear-wheel drive vehicle) can be provided.

Further, in the configuration shown in FIG. 1, two further gear stages can be set in addition to the above-described gear stages, and the value of the gear ratio of the two gear stages is between the second speed and the third speed. And the value between the third speed and the fourth speed, which are shown in the lower part of Table 1 as the 2.5th speed (2.5th) and the 3.5th speed (3.5th).

<< 2.5th forward speed >> This shift stage is a shift stage corresponding to between the second forward speed and the third forward speed described above, and includes the first clutch means K1 and the fourth forward speed.
The clutch means K4 and the second brake means B2 are engaged. Therefore, the sun gear 3S of the third planetary gear mechanism 3 is fixed by the second brake means B2, and the second planetary gear mechanism 2
The ring gear 2R of the second planetary gear mechanism 2 rotates together with the input shaft 4 in a state where the sun gear 2S is fixed by the second brake means B2 via the fourth clutch means K4. Therefore, in the second planetary gear mechanism 2, the carrier 2C rotates forward at a lower speed than the input shaft 4. On the other hand, in the first planetary gear mechanism 1, the ring gear 1R rotates forward at a lower speed than the input shaft 4 together with the carrier 2C of the second planetary gear mechanism 2, but the carrier 1C is rotated by the ring gear 3R of the third planetary gear mechanism 3. And the sun gear 1S is connected to the carrier 3C of the third planetary gear mechanism 3, and the sun gear 3S of the third planetary gear mechanism 3 is fixed. Planetary gear mechanism 1
Sun gear 1S rotates forward at a lower speed than ring gear 1R,
In addition, the carrier 1C rotates forward at an intermediate speed between the ring gear 1R and the sun gear 1S. In the third planetary gear mechanism 3, the ring gear 3R rotates forward at a lower speed than the input shaft 4, and the carrier 3C
Rotates forward at a lower speed. Eventually, in this case, the first to third planetary gear mechanisms 1, 2, and 3 cooperate to perform a deceleration operation, and reduce the rotation of the input shaft 4 and transmit it to the output shaft 5. As shown in Table 1, the value of the gear ratio is represented by (1 + ρ ₁ ) (1 + ρ ₃ + ρ ₁ ρ ₃ ) / (1 + ρ ₃ ), and its specific value is 1.611.

<< 3.5th forward speed >> This shift stage is a shift stage corresponding to between the third forward speed and the fourth forward speed described above, and includes first and third clutch means.
K1 and K3 are engaged with the second brake means B2. That is, the ring gear 2R and the sun gear 2S of the second planetary gear mechanism 2 are connected to the input shaft 4, and the sun gear 3S of the third planetary gear mechanism 3 is connected.
Is fixed. Therefore, since the two elements of the second planetary gear mechanism 2 rotate together with the input shaft 4, the whole element integrally rotates forward at the same speed as the input shaft 4, and accordingly, the ring gear 1 R of the first planetary gear mechanism 1 is rotated. It rotates forward at the same speed as the input shaft 4. The connected and fixed state of each element of the first planetary gear mechanism 1 and the third planetary gear mechanism 3 is the same as that of the above-described second.
This is the same as in the case of the fifth speed, so that each element of the first planetary gear mechanism 1 and the third planetary gear mechanism 3 has the forward
The third planetary gear mechanism 2 rotates slightly faster than the case of the fifth speed, in other words, the 3.5th forward speed is the same as the 2.5th forward speed described above.
Is in a state where the second planetary gear mechanism 2 is in an integrally rotating state without the deceleration action, and the speed ratio is expressed by (1 + ρ ₃ + ρ ₁ ρ ₃ ) / (1 + ρ ₃ ) as shown in Table 1. The specific value is 1.106.

By the way, in the embodiment shown in FIG. 1, each planetary gear mechanism 1,
Although 2 and 3 are arranged in order from the input shaft 4 side, these arrangements may be arbitrarily changed as long as the connected state of each element is maintained as described above. Examples are shown in FIG. 2 to FIG.

That is, in the example shown in FIG. 2, the second planetary gear mechanism 2 is disposed on the input shaft 4 side, and the first planetary gear mechanism 1
And the third planetary gear mechanism 3 are sequentially arranged, and the first and third clutch means K1 and K3 are arranged closer to the input shaft 4 than the second planetary gear mechanism 2, and the other clutch means K2 and K4 and the brake means B1 are arranged. , B2 are arranged on the opposite side of the input shaft 4 with respect to the gear train.

In the example shown in FIG. 3, the second planetary gear mechanism 2, the first planetary gear mechanism 1, and the third planetary gear mechanism 3 are arranged in this order from the input shaft 4 side, and the second and fourth clutch means K
2, K4 and brake means B1, B2 are disposed between the first planetary gear mechanism 1 and the third planetary gear mechanism 3, respectively.

Further, in the example shown in FIG. 4, the second planetary gear mechanism 2, the third planetary gear mechanism 3, and the first planetary gear mechanism 1
The fourth clutch means K4 and the brake means B1, B2 are arranged between the second planetary gear mechanism 2 and the third planetary gear mechanism 3, and the second clutch means K2 is connected to the third planetary gear mechanism 3.
It is arranged between the planetary gear mechanism 3 and the first planetary gear mechanism 1.

2, 3 and 4 as well as the gear transmission shown in FIG. 1 described above, five forward speeds, one reverse speed, or 2.5 forward speeds. In addition, it is possible to set seven forward speeds and one reverse speed in addition to the 3.5th speed.

In the gear transmission shown in FIGS. 1 to 4, the second planetary gear mechanism 2 is engaged by engaging the second clutch means K2 together with the first brake means B1 at the second forward speed. Since the sun gear 2S is fixed, a load is applied to the second clutch means K2. To eliminate the load on the second clutch means K2, the sun gear 2S of the second planetary gear mechanism 2 is driven at the second forward speed. What is necessary is just to install the brake which fixes the. An example is shown in FIG. In the example shown here, the third brake means B3 is additionally provided between the case 6 and the sun gear 2S of the second planetary gear mechanism 2 in the configuration shown in FIG. The operation table is
It is as shown in the table. In the following embodiments, the forward 5
It is possible to set the first to seventh shift speeds and the reverse one, and in the operation tables listed in Table 2 and thereafter, the forward 2.5th speed (2.5th) and the forward 3.5th speed (3.5
th) is displayed as a gear to be added to the case where the setting is based on the case where five forward gears and one reverse gear are set,
If it is a configuration that sets 7 forward steps and 1 reverse step, the second forward step.
The fifth speed corresponds to the third forward speed, and the third forward speed corresponds to the fifth forward speed. As can be seen from Table 2, in the device shown in FIG. 5, the second clutch is used for shifting between the first forward speed and the second forward speed and for shifting between the second and third speeds. means
While K2 is released, the third braking means B3
Can be shifted or engaged without using the second clutch means K2.

In the gear transmission having the configuration shown in FIGS. 1 to 5, the sun gear of the second planetary
Although the second gear 2S is connected to the input shaft 4, substantially only the third planetary gear mechanism 3 performs a speed reducing action. Therefore, in the present invention, the sun gear 3S of the third planetary gear mechanism 3 May be directly connected to the input shaft 4. An example thereof is shown in FIG. 6. In the example shown here, the fifth clutch means K5 is provided between the sun gear 3S of the third planetary gear mechanism 3 and the input shaft 4 in the configuration shown in FIG. It is configured by mounting. The operation table of the gear transmission shown in FIG. 6 is as shown in Table 3, in which five forward speeds and one reverse speed or seven forward speeds and one reverse speed can be set. Thus, the rotation speed of the sun gear 2S and the relative rotation speed of the pinion gear with respect to the carrier 2C in the second planetary gear mechanism 2 can be reduced, which is advantageous in terms of durability.

Although the above-described gear transmission uses three sets of planetary gear mechanisms, not all planetary gear mechanisms are always involved in torque transmission, and a planetary gear mechanism that simply idles at a predetermined speed is used. May be present. That is, in each configuration shown in FIG. 1 to FIG.
When the third forward speed is set by engaging the first and third clutch means K1 and K3 and the first brake means B1, the entire second planetary gear mechanism 2 rotates integrally as described above. On the other hand, in the third planetary gear mechanism 3, the carrier 3C
Is fixed, the ring gear 3R rotates forward at a lower speed than the input shaft 4, and the sun gear 3S rotates reversely. Therefore, the sun gear 2S and the third planetary gear mechanism 3 of the second planetary gear mechanism 2, which may be connected to each other by the fourth clutch means K4.
Relative to the sun gear 3S increases. as a result,
When a multi-plate clutch is used for the fourth clutch means K4, the relative rotation between the clutch disk and the clutch plate becomes large, so-called drag loss becomes large, and at the same time, it becomes disadvantageous in terms of durability. If used, the relative rotation speed between the inner race and the outer race increases at the third forward speed, which is disadvantageous in terms of durability. Therefore, for example, as shown in FIGS. 7 to 9, if a sixth clutch means K6 is additionally installed, the carrier 3C of the third planetary gear mechanism 3 and the sun gear 1S of the first planetary gear mechanism 1 can be provided at the third forward speed, for example. And the sun gear 3S of the third planetary gear mechanism 3 is connected to the input shaft 4 via the third and fourth clutch means K3, K4, so that the third planetary gear mechanism 3 and the second The sun gears 2S and 3S with the planetary gear mechanism 2 can be rotated at the same speed. At the same time, the relative rotation speed of the pinion gear in the third planetary gear mechanism 3 with respect to the carrier 3C can be reduced.

That is, in the example shown in FIG. 7, the sixth clutch means K6 is added between the sun gear 1S of the first planetary gear mechanism 1 and the carrier 3C of the third planetary gear mechanism 3 in the configuration shown in FIG. It was installed. The operation table is shown in Table 4.

In addition, the example shown in FIG. 8 is a fourth brake for preventing unnecessary rotation of the carrier 3C between the carrier 3C of the third planetary gear mechanism 3 and the case 6 in the configuration shown in FIG. Means B4 is additionally provided. Table 5
It is shown in the table.

Further, in the example shown in FIG. 9, third brake means B3 for preventing rotation of the sun gear 2S is interposed between the sun gear 2S of the second planetary gear mechanism 2 and the case 6 in the configuration shown in FIG. Things. The operation table is shown in Table 6.

Further, in the present invention, an appropriate one of the above-mentioned engaging means can be selected and used in combination, and examples thereof will be described below.

That is, the example shown in FIG.
The clutch means K5 is additionally provided so that the sun gear 3S of the third planetary gear mechanism 3 is directly connected to the input shaft 4. The operation table is shown in Table 7.

In the example shown in FIG. 11, the third brake means B3 is additionally installed in the configuration shown in FIG.
The brake means B4 is additionally installed to selectively fix the sun gear 2S of the second planetary gear mechanism 2 and the carrier 3C of the third planetary gear mechanism 3. The operation table is shown in Table 8.

The gear transmission having the configuration shown in FIG. 11 described above can have another configuration by changing the arrangement of its components, and an example is shown in FIG. That is, in the example shown in FIG. 12, the second planetary gear mechanism 2, the third planetary gear mechanism 3, and the first planetary gear mechanism 1 are arranged in this order from the input shaft 4 side, and accordingly, the sixth clutch means K6 is connected to the first planetary gear mechanism K6. It is arranged on the outer peripheral side from the planetary gear mechanism 1,
Further, at least the second and fourth clutch means K2, K4 and the second brake means B2 are arranged between the second planetary gear mechanism 2 and the third planetary gear mechanism 3. With such a configuration, restrictions on the outer diameter of the clutch means are greatly reduced. The operation table of the gear transmission having the structure shown in FIG. 12 is, of course, no different from the above-mentioned Table 8.

Further, another clutch means (tentatively referred to as ninth clutch means) K9 can be additionally provided to the gear transmission having the structure shown in FIG. An example thereof is shown in FIG. 13, in which a ninth clutch means K9 for selectively connecting the carrier 2C of the second planetary gear mechanism 2 and the ring gear 1R of the first planetary gear mechanism 1 is interposed. I have. Table 9 shows an operation table of the gear transmission having the structure shown in FIG.

As can be seen from Table 9, the third brake means B3
And the fourth brake means B4 can be eliminated depending on the manner of engagement / disengagement of other clutch means and brake means, and the first clutch means K1 is always engaged. The clutch means K1 may be eliminated and the ring gear 2R of the second planetary gear mechanism 2 may be always connected to the input shaft 4.

In the example shown in FIG. 14, a fourth brake means B4 is additionally provided in addition to the structure shown in FIG. 10, and the carrier 3C of the third planetary gear mechanism 3 is selectively fixed. The operation table is shown in Table 10.

The example shown in FIG. 15 is a seventh example in which the ring gear 3R of the third planetary gear mechanism 3 and the output shaft 5 or the carrier 1C of the first planetary gear mechanism 1 are selectively connected to the configuration shown in FIG. It is configured by additionally installing clutch means K7.
The operation table is shown in Table 11.

In the example shown in FIG. 16, an eighth clutch means K8 for selectively connecting the sun gear 1S of the first planetary gear mechanism 1 and the carrier 3C of the third planetary gear mechanism 3 is added to the configuration shown in FIG. It is constructed by additionally installing. Table 12 shows the operation table.

Here, the combination of engagement / disengagement of each clutch means and brake means for setting each gear position is described in the 17th.
These are shown together in the figure. In FIG. 17, a circle indicates engagement, a blank indicates release, and an asterisk indicates that the engagement may be performed. FIG. 17 is similar to FIG. 11 and FIG.
This is prepared as an operation table for the gear transmission having the configuration shown in FIG.

As is known from FIG. 17, the first brake means B1
And third brake means B3 and fourth brake means B4
Can be disengaged at any shift speed by a combination of engagement and disengagement of other clutch means and brake means.
Any one or two of B1, B3, B4 can be abolished. Further, the sixth clutch means K6 can be always engaged depending on the manner of engagement / disengagement of other clutch means or brake means. Therefore, the sixth clutch means K6 is abolished and the sun gear A configuration in which 1S and the carrier 3C of the third planetary gear mechanism 3 are always connected may be employed. Further, the same applies to the first clutch means K1, which may be omitted and the ring gear 2R of the second planetary gear mechanism 2 may be always connected to the input shaft 4. Thus, various modifications of the present invention can be easily inferred from FIG.

By the way, in each embodiment described above, each of the clutch means K1 to
K9 and each of the brake means B1 to B4 are indicated by a symbol of a multi-plate clutch or a multi-plate brake. An engagement means having one-way characteristics can be used. Here, the engagement means having a one-way characteristic includes a well-known one-way clutch having a rolling element such as a sprag, a band brake having a torque capacity different depending on a direction in which a load is applied, and the like. By using the engagement means alone or in combination with the multi-plate clutch or the multi-plate brake, the number of engagement means for performing the engagement / release switching control at the time of shifting can be reduced, and the load torque can be reduced. The shift shock is improved because the engaged / disengaged state is automatically switched by the change.
In order to produce such an effect, the elements connected to each other by the one-way engagement means rotate the same (including a stopped state) immediately before shifting, and relatively rotate after shifting, and It is necessary that the effecting element be involved in the transmission of the torque before shifting. In addition to the point where the one-way engaging means is interposed, besides between the two elements directly connected by the one-way engaging means, between the two elements connected via other elements which rotate the same before gear shifting. It may be. The position where the one-way engagement means is provided is
Sun gear 1S of first planetary gear mechanism 1 and third planetary gear mechanism 3
Means for selectively connecting the carrier 3C of the
The case in which the clutch means K6 or the eighth clutch means K8) is provided is different from the case in which the clutch means is not provided. The position is different from that of the first embodiment.

First, as shown in FIGS. 1 to 6 and 15, the sun gear 1S of the first planetary gear mechanism 1 and the carrier 3C of the third planetary gear mechanism 3 are always connected, and a clutch means is provided between them. The case where it is not provided is shown.

Regarding the shift between the first speed and the second speed, the sun gear 2S of the second planetary gear mechanism 2 and the sun gear 2 of the third planetary gear mechanism 3
One-way engagement means such as a one-way clutch may be interposed between the 3S and the 3S. Regarding the shift between the first speed and the second speed, between the carrier 3C of the third planetary gear mechanism 3 and the case 6 or the sun gear 1S of the first planetary gear mechanism 1 and the case 6
The one-way engagement means may be provided in at least one of them. Regarding the shift between the first speed and the third speed, a one-way engagement means may be provided between the sun gear 2S of the second planetary gear mechanism 2 and the sun gear 3S of the third planetary gear mechanism 3. Regarding the shift between the first gear and the third gear, the second gear
Between the sun gear 2S of the planetary gear mechanism 2 and the sun gear 3S of the third planetary gear mechanism 3, between the carrier 3C of the third planetary gear mechanism 3 and the case 6, and between the sun gear 1S and the case 6 of the first planetary gear mechanism 1; The one-way engagement means may be interposed at least at any one of the positions. In this case, there is a shift pattern that requires a so-called multiple shift in which three or more engaging means are simultaneously switched to perform a shift. Regarding the shift between the first speed and the fourth speed, the shift between the carrier 3C of the third planetary gear mechanism 3 and the case 6 or the first planetary gear mechanism 1
One-way engaging means may be interposed in at least one of the sun gear 1S and the case 6. Regarding the shift between the first speed and the fifth speed, between the sun gear 2S of the second planetary gear mechanism 2 and the sun gear 3S of the third planetary gear mechanism 3, the carrier 3C of the third planetary gear mechanism 3 and the case 6 Between the first
One-way engagement means may be interposed at least at one location between the sun gear 1S of the planetary gear mechanism 1 and the case 6 and between the ring gear 2R of the second planetary gear mechanism 2 and the input shaft 4. In this case, there are also shift patterns that require multiple shifts.

Regarding the shift between the second speed and the second speed, the sun gear 2S of the second planetary gear mechanism 2 and the sun gear 1S of the first planetary gear mechanism 1 or the sun gear 1S of the first planetary gear mechanism 1 and the case 6 The one-way engagement means may be interposed in at least one of the two. Regarding the shift between the second speed and the third speed, the sun gear 2S of the second planetary gear mechanism 2 and the first
One-way engagement means may be interposed between at least one of the sun gear 1S of the planetary gear mechanism 1 or at least one of the sun gear 2S of the second planetary gear mechanism 2 and the case 6. Regarding the shift between the second speed and the third speed, the sun gear 2S of the second planetary gear mechanism 2 and the sun gear 1S of the first planetary gear mechanism 1
, The sun gear 2S of the second planetary gear mechanism 2 and the case 6, and the one-way engagement means interposed at least at one place between the sun gear 1S of the first planetary gear mechanism 1 and the case 6. It should be done. In this case, there is a shift pattern that requires multiple shifts. Regarding the shift between the second speed and the fourth speed,
At least one one-way engagement means may be interposed between the sun gear 2S of the second planetary gear mechanism 2 and the case 6 or between the sun gear 1S of the first planetary gear mechanism 1 and the case 6. Regarding the shift between the second speed and the fifth speed, the shift between the sun gear 2S of the second planetary gear mechanism 2 and the case 6, the shift between the sun gear 1S of the first planetary gear mechanism 1 and the case 6, the second planetary gear One-way engaging means may be interposed at least at any one position between the ring gear 2R of the gear mechanism 2 and the input shaft 4. Also in this case, there is a shift pattern that requires multiple shifts.

Regarding the shift between the 2.5th speed and the 3rd speed, the sun gear 2S of the second planetary gear mechanism 2 and the sun gear 3S of the third planetary gear mechanism 3 and the sun gear 2S of the second planetary gear mechanism 2 and the case 6 , The sun gear 3S of the third planetary gear mechanism 3 and the case 6
The one-way engagement means may be interposed at least at any one position between the two. In this case, there is a shift pattern that requires multiple shifts. Regarding the shift between the 2.5th speed and the 3.5th speed, the sun gear 2S of the second planetary gear mechanism 2 and the sun gear 3S of the third planetary gear mechanism 3 or the sun gear 2S of the second planetary gear mechanism 2 and the case 6 The one-way engagement means may be interposed in at least one of the two. 2.5th
Regarding the shift between the fourth speed and the fourth speed, at least one of between the sun gear 2S of the second planetary gear mechanism 2 and the case 6 or between the sun gear 3S of the third planetary gear mechanism 3 and the case 6 What is necessary is just to interpose a one-way engagement means. No. 2.
As for the shift between the fifth speed and the fifth speed, the sun gear 2S of the second planetary gear mechanism 2 and the sun gear 3S of the third planetary gear mechanism 3 and the sun gear 2S of the second planetary gear mechanism 2 and the case 6 During this time, a one-way engaging means may be interposed at least at any one position between the ring gear 2R of the second planetary gear mechanism 2 and the input shaft 4. In this case, there is a shift pattern that requires multiple shifts.

Regarding the speed change between the third speed and the 3.5th speed and the speed change between the third speed and the fourth speed, respectively, a one-way engagement means is provided between the sun gear 1S of the first planetary gear mechanism 1 and the case 6. May be interposed. As for the shift between the third speed and the fifth speed, the sun gear 2S of the second planetary gear mechanism 2 and the carrier 2C or the ring gear 2R of the second planetary gear mechanism 2 or the ring gear 2R or the first planetary gear mechanism 1 and the ring gear 1R At least one of between the input shaft 4 and the carrier 2C or the ring gear 2R of the second planetary gear mechanism 2 or the ring gear 1R of the first planetary gear mechanism 1, or between the sun gear 1S of the first planetary gear mechanism 1 and the case 6. What is necessary is just to interpose the one-way engagement means in one place. Also in this case, there is a shift pattern that requires multiple shifts.

Regarding the shift between the 3.5th speed and the 4th speed, a one-way engagement means may be interposed between the sun gear 3S of the third planetary gear mechanism 3 and the case 6. Regarding the shift between the 3.5th speed and the 5th speed, between the sun gear 2S of the second planetary gear mechanism 2 and the carrier 2C or the ring gear 2R of the second planetary gear mechanism 2 or the ring gear 1R of the first planetary gear mechanism 1 , Input shaft 4 and carrier 2C or ring gear of second planetary gear mechanism 2
One-way engagement means may be interposed in at least one of the 2R and the ring gear 1R of the first planetary gear mechanism 1.

As for the shift between the fourth speed and the fifth speed, the fourth speed
Since the entire gear train rotates integrally at high speed, one-way engagement means can be provided for each of the three elements of each of the planetary gear mechanisms 1, 2, and 3. That is, the sun gear 2S of the second planetary gear mechanism 2 includes the carrier 2C and the ring gear 2R of the second planetary gear mechanism 2, the sun gear 3S and the ring gear 3R of the third planetary gear mechanism 3, the carrier 1C and the ring gear of the first planetary gear mechanism 1. One-way engagement means may be interposed between any one of the 1Rs. Regarding the carrier 2C of the second planetary gear mechanism 2, one-way engagement between the ring gear 1R of the first planetary gear mechanism 1 and any other element (including the input shaft 4) except the case 6 is provided. Means may be interposed. Each of the ring gear 2R of the second planetary gear mechanism 2 and the sun gear 3S of the third planetary gear mechanism 3 has a unidirectional relationship with any other element (including the input shaft 4) except for the case 6. What is necessary is just to interpose a combining means. Regarding the carrier 3C of the third planetary gear mechanism 3, the second planetary gear mechanism 2
Carrier 2C and ring gear 2R, third planetary gear mechanism 3
Sun gear 3S and ring gear 3R, first planetary gear mechanism 1
The one-way engagement means may be interposed between the carrier and any one of the ring gear 1R. Third planetary gear mechanism 3
As for the ring gear 3R, the one-way engaging means may be interposed between the carrier 1C of the first planetary gear mechanism 1 and any other element (including the input shaft 4) except for the case 6. . Regarding the sun gear 1S of the first planetary gear mechanism 1,
A carrier 2C and a ring gear 2R of the second planetary gear mechanism 2;
A sun gear 3S and a ring gear 3R of the third planetary gear mechanism 3,
A one-way engaging means may be interposed between the carrier 1C and the ring gear 1R of the first planetary gear mechanism 1. Regarding the carrier 1C of the first planetary gear mechanism 1,
A one-way engagement means may be interposed between the ring gear 3R of the planetary gear mechanism 3 and other elements (including the input shaft 4) except for the case 6. For the ring gear 1R of the first planetary gear mechanism 1, the carrier 2C of the second planetary gear mechanism 2 is used.
One-way engagement means may be interposed between the housing and other elements (including the input shaft 4) except for the case 6.

Next, as shown in FIGS. 7 to 13 and 16 described above, there is provided a clutch means for selectively connecting the sun gear 1S of the first planetary gear mechanism 1 and the carrier 3C of the third planetary gear mechanism 3. Is shown. In the configuration having such clutch means, the third planetary gear mechanism 3
Carrier 3C and the sun gear 1S of the first planetary gear mechanism 1 can be selectively connected and the connection can be released, so that the carrier 3C of the third planetary gear mechanism 3 can be fixed independently. In addition, sun gears 1S, 2 of each planetary gear mechanism 1, 2, 3
Since the connection relationship between S and 3S can be changed as appropriate, compared to the case where the sixth clutch means K6 or K8 clutch means K8 is not provided, the carrier 3C of the third planetary gear mechanism 3 and the first Whether or not one-way engagement means can be arranged between the sun gear 1S of the planetary gear mechanism 1 and between the carrier 3C of the third planetary gear mechanism 3 and the case 6;
There is a difference in whether a one-way engagement means can be interposed between S, 2S, and 3S. Therefore, in the following description, portions different from the arrangement positions of the one-way engagement means for each shift pattern described above will be described, and description of the same portions will be omitted.

That is, regarding the shift between the first speed and the second speed and the shift between the first speed and the third speed, the carrier 3C of the third planetary gear mechanism 3 and the first planetary gear One-way engagement means may be interposed between the sun gear 1S of the mechanism 1 or between the carrier 3C of the third planetary gear mechanism 3 and the case 6. Regarding the shift between the first speed and the fourth speed and the shift between the first speed and the fifth speed, the carrier 3C of the third planetary gear mechanism 3 and the first planetary gear One-way engagement means may be interposed between the mechanism 1 and the sun gear 1S.

Regarding the shift between the second speed and the fifth speed among the shifts between the second speed, the sun gear 2S of the second planetary gear mechanism 2 is unidirectionally engaged with the sun gear 1S of the first planetary gear mechanism 1. Means may be interposed.

Regarding the shift to the fourth speed among the shifts to the 2.5th speed, one-way engaging means is interposed between the sun gear 2S of the second planetary gear mechanism 2 and the sun gear 3S of the third planetary gear mechanism 3. You may.

Further, regarding the shift between the fourth speed and the fifth speed, the sun gear 2S of the second planetary gear mechanism 2 and the first
Between the sun gear 1S of the planetary gear mechanism 1, between the carrier 3C of the third planetary gear mechanism 3 and the sun gear 1S of the first planetary gear mechanism 1, and between the sun gear 1S of the first planetary gear mechanism 1 and the input shaft 4. May be provided with a one-way engaging means.

As described above, the one-way engagement means for executing a smooth shift can be set at various places as necessary.
When the one-way engaging means is used for shifting from the first forward speed to the fifth forward speed to each of the adjacent forward speeds, the sun gear 2S of the second planetary gear mechanism 2 and the third planetary gear are used. Either between the sun gear 3S of the gear mechanism 3, between the sun gear 2S of the second planetary gear mechanism 2 and the sun gear 1S of the first planetary gear mechanism 1, or between the sun gear 2S of the second planetary gear mechanism 2 and the case 6. On the other hand, between the sun gear 1S of the first planetary gear mechanism 1 and the case 6, between the sun gear 2S of the second planetary gear mechanism 2 and the sun gear 3S of the third planetary gear mechanism 3, or the ring gear of the second planetary gear mechanism 2 One-way engagement means may be set in any one of the 2R and the input shaft 4. This is the same regardless of whether the sixth clutch K6 or the sixth clutch K8 is provided or not.

The method of using the one-way engaging means is described in Japanese Patent Application No. 63-176270 and Japanese Patent Application No.
The description and drawings attached to the application No. 1670 may be adopted.

For example, as shown in FIG. 18, the first clutch means K1 includes a one-way clutch 10 and a multi-plate clutch 11 capable of transmitting torque in the forward rotation direction from the input shaft 4 to the ring gear 2R of the second planetary gear mechanism 2. May be arranged in series, and another multi-plate clutch 12 may be arranged in parallel with these. The first clutch means K1 is engaged or disengaged at the time of shifting between the forward fourth speed and the fifth speed, or at the time of shifting between the third speed and the fourth speed, or while maintaining the fourth speed state. However, in the case of an upshift, the second
Since the rotation speed of the ring gear 2R of the planetary gear mechanism 2 is equal to or higher than the rotation speed of the input shaft 4 and is opposite in the case of a downshift, the multi-plate clutch 11 in series with the one-way clutch 10 And the one-way clutch 10 maintains the engaged state, for example, when shifting between the third speed and the fourth speed, even if the other multiple disc clutches 12 in parallel are left disengaged. In the shift between the fourth speed and the fifth speed, each shift can be executed by engaging or disengaging. Since the ring gear 2R of the second planetary gear mechanism 2 rotates reversely in the reverse gear, a multi-plate clutch 11 is arranged in series with the one-way clutch 10.

Further, the fourth clutch means K4 is arranged such that the sun gear 3S of the third planetary gear mechanism 3 rotates forward with respect to the sun gear 2S of the second planetary gear mechanism 2, as shown in FIGS. One way clutch 20 and multiple disc clutch to engage when trying
21 are arranged in series and another multi-disc clutch 22 is arranged in parallel with them (FIG. 19 (A)). Alternatively, the multi-disc clutch shown in FIG. twenty one
And the one-way clutch 20 and the multi-plate clutch 22 can be arranged in parallel (FIG. 19 (B)). The reason why the multi-plate clutch 21 is provided in series with the one-way clutch 20 is that the sun gear 3S of the third planetary gear mechanism 3 is separated from the sun gear 2S of the second planetary gear mechanism 2 depending on how to set the third forward speed. This is because it is necessary to make a forward rotation at a high speed, and the multi-plate clutch 21 is omitted and the structure is configured as shown in FIG. 19 (B). This is because the sun gear 3S of the mechanism 3 does not rotate forward at a higher speed than the sun gear 2S of the second planetary gear mechanism 2. Then, as described above, the engagement / disengagement state of the fourth clutch means K4 is switched at the time of shifting between the first forward speed and the second speed or at the fourth forward speed and the fifth forward speed.

As shown in FIG. 20, the sixth clutch means K6 is engaged when the sun gear 1S of the first planetary gear mechanism 1 attempts to make a forward rotation relative to the carrier 3C of the third planetary gear mechanism 3. The one-way clutch 30 and the multi-plate clutch 31 can be arranged in parallel. As described above, the sixth clutch means K6 acts together with the first brake means B1 in the first forward speed to prevent reverse rotation of the carrier 3C of the third planetary gear mechanism 3, but from that state to the second speed. Since the carrier 3C rotates forward during the upshift, the one-way clutch 30 is automatically disengaged, and the upshift can be performed.

As shown in FIG. 21, the first brake means B1 is arranged in parallel with a one-way clutch 40 which is engaged when the sun gear 1S of the first planetary gear mechanism 1 tries to rotate in the reverse direction with respect to the case 6. And a multi-disc brake or a band brake (hereinafter, these are simply referred to as brakes) 41. The first to third forward speeds are achieved by preventing reverse rotation of the sun gear 1S of the first planetary gear mechanism 1, and
The first and fifth speeds cause the sun gear 1S of the first planetary gear mechanism 1 to rotate forward, so that the one-way clutch 40 can shift between the third and fourth speeds.

As shown in FIG. 22, the second brake means B2 includes a one-way clutch 50 and a brake 51 which are engaged when the sun gear 3S of the third planetary gear mechanism 3 tries to rotate in the reverse direction with respect to the case 6.
Are arranged in series, and another brake 52 is arranged in parallel with them. That is, as is known from the above-described respective examples, when the third clutch means K3 is released to set the forward second speed, the reverse rotation of the sun gear 3S of the third planetary gear mechanism 3 is prevented, and from this state, the third When the gear is up-shifted, the sun gear 3S of the third planetary gear mechanism 3 starts to rotate forward, so that the one-way clutch 50
The one-way clutch 50 is automatically disengaged according to the direction of the torque applied to the sun gear 3S even if the in-line brake 51 is maintained in the engaged state, and the second speed is increased to the third speed. A shift can be performed, and conversely, the one-way clutch 50 can be automatically engaged to perform a downshift from the third speed to the second speed.

As shown in FIG. 23, the fourth brake means B4 includes a one-way clutch 60 and a brake 61 which are engaged when the carrier 3C of the third planetary gear mechanism 3 tries to rotate reversely with respect to the case 6.
And can be arranged in parallel. The carrier 3C of the third planetary gear mechanism 3 is prevented from rotating in the reverse direction at the first forward speed and is fixed, and rotates forward at the other forward speeds. 23, it is fixed by the fourth brake means B4. Therefore, in the configuration shown in FIG. 23, the shift between the first speed and the second speed is performed by applying the one-way clutch 60. Can be.

In each of the examples shown in FIGS. 18 to 23, a multi-plate clutch or a brake means is provided in parallel with the one-way clutch, in order to make the engine brake effective. A fourth clutch means K4, a sixth clutch means;
K6, the multiple disc clutch or the brake in the first brake means B1 and the fourth brake means B4 are also engaged in the reverse gear. Modifications in which such clutch means and brake means are improved will be described below.

In the example shown in FIG. 24, in the configuration shown in FIG. 4 described above, the second clutch means K2 is arranged in parallel with the one-way clutch 70 and the multi-plate clutch 71 arranged in series with the one-way clutch 70. Another multi-plate clutch 72 is used, the fourth clutch means K4 is configured as shown in FIG. 19 (B), and the first brake means B1 is configured as shown in FIG. The two-brake means B2 is constituted by a band brake. An example of an operation table of the gear transmission having the structure shown in FIG. 24 is shown in Table 13.
In addition, in the following operation table, a circle indicates an engaged state,
In addition, the fact that the crosses indicate the released state is the same as in the above-mentioned operation table, and in addition, in the following operation tables, the mark ◎ indicates that the engine is in the engaged state at the time of engine braking. Further, the indications of a, b, c... In the column of the gear position indicate other combinations of the engagement and disengagement for setting the gear position. The combination of engagement and release may be changed, or any combination of engagement and release may be selected.

In the example shown in FIG. 25, of the configuration shown in FIG. 24, the second clutch means K2 is constituted by a single multi-plate clutch, and the sun gear 2S of the second planetary gear mechanism 2 is selectively fixed. Third brake means B3 consisting of a band brake
Is provided. An example of the operation table is shown in Table 14.

The example shown in FIG. 26 is different from the above-described configuration shown in FIG. 25 in that a multi-disc brake 81 and a one-way clutch 80 are arranged in series with a third brake means B3 composed of a band brake. The five brake means B5 are arranged in parallel. An example of the operation table is shown in Table 15.

Since the embodiment shown in FIGS. 24 to 26 described above does not include the sixth clutch means K6, as described above,
The sun gear 3S of the third planetary gear mechanism 3 and the second planetary gear mechanism 2
Relative to the sun gear 2S, that is, the relative rotational speed between the inner race and the outer race of the one-way clutch 20 in the fourth clutch means K4, is disadvantageous in terms of durability and the like. It is effective to use the sixth clutch means K6 in order to solve such inconvenience. In this case, as described with reference to FIGS. 18 to 23, the first clutch means K1 and the fourth clutch means K6 are used. If the clutch means K4, the sixth clutch means K6, the first brake means B1 and the fourth brake means B4, and these and the second brake means B2 are configured to include a one-way clutch, the one-way clutch is actuated. In particular, the fourth clutch means K4
And at least three of the sixth clutch means K6 or the fourth brake means B4 and the first brake means B1, or one of the first clutch means K1 or the fourth clutch means K4 and the sixth Clutch means K6 or 4th
One of the brake means B4 and the first brake means B1
And at least four of the second brake means B2 are improved to include a one-way clutch as shown in FIGS. 18 to 23, so that a shift between adjacent shift speeds in the forward speed can be achieved. This can be achieved by operating a one-way clutch, so that the shift controllability is good and the shift shock can be advantageously reduced. An example is shown below.

That is, in the example shown in FIG. 27, the fourth clutch means K4 of the above-described structure shown in FIG. 12 has the structure shown in FIG. 19 (A), and the sixth clutch means K6 has the structure shown in FIG. Further, the first brake means B1 has a configuration shown in FIG. The operation table is as shown in Table 16,
As is clear from this table, the basic 5 steps forward and 1 reverse
In the case of a configuration in which the shift speed of the second gear is set, the shift of the forward gear can be achieved by artificially controlling one engagement means.

The example shown in FIG. 28 is different from the above-mentioned structure shown in FIG. 27 in that the sixth clutch means K6 is a single multi-plate clutch and the fourth brake means B4 is the structure shown in FIG. The operation table is shown in Table 17.

In the configurations shown in FIGS. 27 and 28, the shift in the forward gear can be performed by using a one-way clutch, and the second planetary gear mechanism 2 and the third planetary gear mechanism 3 in the third speed can be connected. The relative rotation speed of the sun gears 2S and 3S can be reduced, and at the same time, the rotation speed of the pinion gear of the third planetary gear mechanism 3 relative to the carrier 3C can be reduced.

In the example shown in FIG. 29, the fourth clutch means K4 of the above-described structure shown in FIG. 27 is replaced with the structure shown in FIG. 19 (B), and the second brake means B2 is replaced with the structure shown in FIG. It has been changed to. The operation table is as shown in Table 18, and also in this configuration, there is one engaging means for artificially controlling the speed change in the forward gear.

Further, in the example shown in FIG. 30, the sixth clutch means K6 of the structure shown in FIG. 29 is constituted by a single multi-plate clutch, and the fourth brake means B4 is constituted by the structure shown in FIG. It was done. Table 19 shows the operation table.

In the configurations shown in FIGS. 29 and 30, the one-way clutch is actuated to perform the shift in the forward gear, and the second planetary gear mechanism 2 and the third gear in the second and third speeds are used.
The relative rotation speed of the sun gears 2S and 3S with the planetary gear mechanism 3 can be eliminated, and the relative rotation speed of the pinion gear in the third planetary gear mechanism 3 at the second speed and the third speed with respect to the carrier 3C can be reduced. it can.

In the example shown in FIG. 31, the one-way clutch 40 of the first brake means B1 in FIG. 24, and the outer race is connected to the carrier 3C and the multiple disc brake 41, and the other configuration is the same as the configuration shown in FIG. Therefore, in the example shown in FIG. 31, the arrangement of the components of the gear transmission shown in FIG. 24 is changed, and the operation table is the same as that in Table 13 described above.

The example shown in FIG. 32 is a fifth brake means B5 comprising a one-way clutch 80 and a multi-plate brake 81 arranged in series with each other.
Is provided between the sun gear 2S of the second planetary gear mechanism 2 having the configuration shown in FIG. 31 and the case 6, and the second clutch means K2 is constituted by a multi-plate clutch. The third brake means B3 is removed from the structure shown in FIG. 26, and the first brake means B1 is the same as the structure shown in FIG. An example of the operation table is shown in Table 20.

The example shown in FIG. 33 is an example in which the sixth clutch means K6 is provided, and for example, the configuration shown in FIG. 28 described above is modified. That is, the fourth clutch means K4 is composed of the multi-plate clutch 22 and the one-way clutch 20 arranged on the inner peripheral side thereof, and these multi-plate clutch 22 and the one-way clutch 20 are connected to the sun gear 2S of the second planetary gear mechanism 2. And the sun gear 3S of the third planetary gear mechanism 3 are arranged in parallel.
Brake means B1 is replaced with band brake 42 and one-way clutch 40
And the second brake means B2 is a band brake, and the second clutch means K2 is a multi-plate clutch.
Other configurations are the same as those in FIG. An example of the operation table is as shown in Table 21.

In the example shown in FIG. 34, the third brake means B3 comprising a band brake for fixing the sun gear 2S of the second planetary gear mechanism 2 in the configuration shown in FIG. 33 is provided, and the first brake means B1 is formed. The one-way clutch 40 has a small diameter, and the other configuration is the same as the configuration shown in FIG. An example of the operation table is shown in Table 22.

The example shown in FIG. 35 is obtained by further modifying the configuration shown in FIG. 33 described above. Between the sun gear 2S and the ring gear 2R of the second planetary gear mechanism 2, the sun gear 2S is A one-way clutch F that engages in the forward rotation direction is provided, and a multi-plate clutch K is provided between the outer race and the ring gear 2R of the second planetary gear mechanism 2,
The fourth clutch means K4 is constituted by a multi-plate clutch, and the fourth brake means B4 is the same as that shown in FIG.
Further, the first brake means B1 is constituted by a band brake. An example of the operation table is shown in Table 23.

In the example shown in FIG. 36, the configuration of the sixth clutch means K6 and the first brake means B1 in the configuration shown in FIG. 33 is changed. That is, the sixth clutch means K6 has the structure shown in FIG. 20, and the first brake means B1 comprises a band brake 42 and these one-way clutches 40 in parallel, and the one-way clutch 40 The outer race is mounted on a predetermined fixed portion integral with the case 6. An example of the operation table is shown in Table 24.

The example shown in FIG. 37 is one of the configurations shown in FIG.
The second brake means B2 is connected to the one-way clutch 50
And a multi-disc clutch 51 and a band brake 53 in parallel with these, and the first brake means B1
Is a band brake. Other configurations are
The configuration is the same as that shown in FIG. An example of the operation table is as shown in Table 25.

In the example shown in FIG. 38, the third brake means B3 between the sun gear 2S of the second planetary gear mechanism 2 and the case 6 in the configuration shown in FIG. And a tenth clutch means K10 for selectively connecting the carrier 3C and the sun gear 3S of the third planetary gear mechanism 3 to each other,
Further, the first brake means B1 is constituted by a one-way clutch 40 and a band brake 42 provided on the inner peripheral side.
Other configurations are the same as those shown in FIG. An example of the operation table is shown in Table 26.

In the example shown in FIG. 39, the sixth clutch means K6 is arranged between the second planetary gear mechanism 2 and the third planetary gear mechanism 3 in the configuration shown in FIG. 4th
A one-way clutch as a brake means B4 is provided, and the first brake means B1 is constituted only by a band brake, and the other constitution is the same as that shown in FIG. An example of the operation table is shown in Table 27. This 39th
In the example shown in the figure, the carrier 3C of the third planetary gear mechanism 3 is fixed by engaging the first brake means B1 in the state in which the sixth clutch means K6 is engaged during reverse movement. The load torque applied to K6 increases. Therefore, it is preferable to reduce the size of the sixth clutch means K6 or to reduce the engine output or the input torque to the gear transmission mechanism when the vehicle is moving backward in order to maintain its durability.

In the example shown in FIG. 40, the one-way clutch 40 constituting the first brake means B1 of the configuration shown in FIG.
The clutch means K6 is arranged on the outer peripheral side of the one-way clutch 30, and other components are the same as those shown in FIG. Therefore, an example of the operation table is the same as Table 24 described above.

The example shown in FIG. 41 is obtained by removing the third brake means B3 from the structure shown in FIG. 39 described above.
Column and column b are deleted. The operation table is shown in Table 28 for reference. In addition, also in this configuration, in order to reduce the size of the sixth clutch means K6 or maintain its durability,
It is preferable to reduce the engine output or the input torque to the gear transmission mechanism during reverse travel.

The example shown in FIG. 42 is different from the structure shown in FIG. 41 in that the first brake means B1 is constituted by a small-diameter one-way clutch 40 and a band brake 42 in a parallel relationship to the one-way clutch 40. Is similar to the configuration shown in FIG. Also in this configuration, in order to reduce the size of the sixth clutch means K6 or to maintain its durability, it is preferable that the engine output be reduced or the input torque to the gear transmission mechanism be reduced during reverse travel. An example of the operation table is shown in Table 29.

In the example shown in FIG. 43, in the configuration shown in FIG. 42, the second brake means B2 is connected to the sun gear 3S of the third planetary gear mechanism 3.
A one-way clutch 50, a multi-plate brake 51 in series with the one-way clutch 50, and a band brake 53 in parallel with these, and a second planetary gear mechanism. Third brake means B3 which is a band brake for selectively fixing the second sun gear 2S.
And the fourth brake means B4 is replaced with a single multi-plate brake, and the other configuration is the same as the configuration shown in FIG. Table 30 shows an example of the operation table.

In the example shown in FIG. 44, in the configuration shown in FIG. 43, the second brake means B2 is replaced with a single band brake, and the third brake means B3 is replaced with one direction in series with each other. A fifth brake means B5 comprising a clutch 80 and a multi-plate brake 81 is provided, and the other configuration is the same as the configuration shown in FIG. An example of the operation table is shown in Table 31.
It is shown in the table.

In the example shown in FIG. 45, in the configuration shown in FIG. It is provided between 2S and case 6. The other configuration is the same as the configuration shown in FIG. An example of the operation table is shown in Table 32.

In the example shown in FIG. 46, the configuration of the first clutch means K1 and the fourth clutch means K4 in the configuration shown in FIG. 41 is changed, and the third brake means B3 is provided. That is, the first clutch means K1 is a multi-plate clutch 91 disposed between the input shaft 4 and the ring gear 2R of the second planetary gear mechanism 2.
And another multi-plate clutch 92 and a one-way clutch in parallel with each other and in series with each other.
The fourth clutch means K4 is formed of a single multi-plate clutch, and is a band brake for selectively fixing the sun gear 2S of the second planetary gear mechanism 2. Brake means B3 is provided. The other configuration is the same as the configuration shown in FIG. Table 33 shows an example of the operation table. Also in this configuration, it is preferable to reduce the engine output or reduce the input torque to the gear transmission mechanism when the vehicle reverses in order to reduce the size of the sixth clutch means K6 or to maintain its durability.

In the example shown in FIG. 47, the third brake means B3 is removed from the structure shown in FIG.
K6 is arranged adjacent to the third planetary gear mechanism 3, and a one-way clutch which is fourth braking means B4 is arranged on the inner peripheral side of the sixth clutch means K6. It is the same as. Also in this configuration, in order to reduce the size of the sixth clutch means K6 or to maintain its durability,
It is preferable that the engine output be reduced or the input torque to the gear transmission mechanism be reduced during reverse travel. Table 34 shows an example of the operation table.

In the example shown in FIG. 48, the second brake means B2 of the configuration shown in FIG. 47 is changed to a single band brake, and the sun gear 2S of the second planetary gear mechanism 2 is selectively fixed. As a five-brake means B5, a one-way clutch 80 and a multi-disc brake 81 which are in series with each other are provided between the case 6, and the other structure is the same as the structure shown in FIG. Also in this configuration, it is preferable that the engine output or the input torque to the gear transmission be reduced during reverse travel, as in the example shown in FIG. 47. An example of the operation table is shown in Table 35.

As described above, FIGS. 24 to 48 show examples in which a one-way clutch is used to improve the shift controllability and the shift shock. However, as an engagement means having one-way characteristics, a band brake other than the one-way clutch is used. Can be used. That is, the band brake is tightened when the rotating body such as a drum is rotating from the anchor portion which is the fixed end of the band toward the other end, that is, the rotating direction of the rotating body is in a so-called energy direction. If there is, the rotating body will actively try to wind the band, so the braking force will be large, and the rotating force of the rotating body will be opposite to the band tightening direction for the opposite deenergization direction Therefore, the braking force is reduced, and as a result, directivity is generated, which can be effectively applied as a one-way characteristic. Therefore, in the present invention, a configuration in which the one-way clutch and the multiple disc brake in each of the above-described examples are arranged in series or in parallel, a configuration in which the one-way clutch and the band brake are arranged in parallel, or a one-way clutch and the multiple disc brake May be replaced by a band brake provided with a single band or a pair of bands having opposite winding directions. Further, the location where the engagement means having the one-way characteristic is used may be arbitrarily selected as necessary, and therefore, as shown in FIG. 24 to FIG. 48, the unidirectional engagement means is not used at a plurality of locations. The one-way engaging means may be employed only at one location.

FIG. 49 shows a more specific embodiment of the present invention. The example shown in FIG. 49 embodies the configuration shown in FIG. 31 described above, and the input shaft 4 is connected to an output shaft (each not shown) of a joint member such as a torque converter. The tip of the input shaft 4 is a first clutch means.
It is connected to the clutch drum 100 of K1. The first clutch means K1 brings the clutch drum 101 and the clutch hub 101 integrated with the ring gear 2R of the second planetary gear mechanism 2 into frictional contact with a disk and a plate, which are spline-fitted to each other, to reduce torque. The hydraulic piston 102 for transmitting, that is, engaging and releasing the frictional contact so as not to transmit the torque, moves back and forth in the axial direction inside the clutch drum 100 to perform the engagement and release. It is arranged as follows. The hydraulic piston 102 is moved backward by a return spring 103. Input shaft 4 and sun gear 2S of second planetary gear mechanism 2
And the third clutch means K3 for connecting the first clutch means
Similarly to K1, the clutch drum 104 and the clutch hub 105 are connected so as to be able to transmit a torque by bringing a disk and a plate, each of which is spline-fitted, into frictional contact with each other, that is, engage and release the frictional contact. The clutch hub 105 is integrated with the clutch drum 100 of the first clutch means K1, and the clutch drum 104 covers the outer peripheral sides of the first clutch means K1 and the second planetary gear mechanism 2. And one end is second
The planetary gear mechanism 2 is integrally connected to a cylindrical connecting drum 106 connected to a sun gear 2S. Hydraulic piston 107 for engaging and disengaging this third clutch means K3
Is provided in the clutch drum 104, and a return spring 108 for retreating the hydraulic piston 107 is provided.

A multi-plate clutch 70 that constitutes a part of the second clutch means K2 is disposed on the opposite side of the first clutch means K1 with the second planetary gear mechanism 2 interposed therebetween.
It is supported by a hollow shaft 110 rotatably arranged on the inner peripheral side of the center support 109. That is, the first center support 1
09 is fixed to the inner peripheral surface of case 6 and the multi-plate clutch 70
The clutch drum 111 is fitted to the boss portion of the first center support 109 so as to rotate while maintaining a liquid-tight state, while the leading end portion is non-rotatably engaged with the connecting drum 106. The drum 111 is spline-fitted and connected to a hollow shaft 110 rotatably supported on the inner peripheral side of the first center support 109. Clutch drum 11
The clutch hub 112 connected to the disk 1 by frictional contact between the disk and the plate is connected to a first sun gear shaft 113 rotatably supported on the inner peripheral side of the hollow shaft 110. A hydraulic piston 114 for engaging and disengaging the second clutch means K2 is accommodated in the inner peripheral side of the clutch drum 111 so as to be movable back and forth. Through an oil passage 115 penetrating from the outer peripheral side thereof. Further, a return spring 116 is provided on the front side of the hydraulic piston 114.

On the inner peripheral side of the first sun gear shaft 113, the input shaft 4
An intermediate shaft 117 is provided on the same axis as the intermediate shaft 117. The intermediate shaft 117 extends from the second planetary gear mechanism 2 side to the rear end opposite to the input shaft 4, and is provided at While the carrier 2C of the second planetary gear mechanism 2 is connected,
The ring gear 1R of the first planetary gear mechanism 1 is connected to the rear end.

On the opposite side of the first center support 109 from the second clutch means K2, a multi-plate clutch 71 constituting a part of the second clutch means K2 is arranged.
118 is fitted to the boss portion of the first center support 109 so as to rotate while maintaining a liquid-tight state, and the hollow shaft 110
It is connected to. The multi-plate clutch 71 transmits a torque between the clutch drum 118 and the clutch hub 120 by pressing the disk and the plate by the hydraulic piston 119 housed in the clutch drum 118 so as to be able to move back and forth and bringing them into frictional contact. The clutch hub 120 is integrated with the outer race of the one-way clutch 70 forming a part of the second clutch means K2, and the inner race of the one-way clutch 70 is
It is connected to the sun gear shaft 113. That is, the multi-plate clutch 71 and the one-way clutch 70 are arranged in series. The release of the multi-plate clutch 71 is also performed by the return spring 12.
This is performed by moving the hydraulic piston 119 backward by 1. Hydraulic piston to operate multi-plate clutch 70
The supply and discharge of the hydraulic pressure to and from the 119 are performed via another oil passage 122 formed through the first center support 109.

Multi-plate clutch 70 forming a part of the second clutch means K2
The fourth clutch means K4 is disposed so as to be opposed to.
That is, the fourth clutch means K4 is composed of a multi-plate clutch 22 and a one-way clutch 20 which are in a parallel relationship with each other. A clutch hub 124, a hydraulic piston 125, and a return spring 126 which are connected to and released from the clutch drum 123 so as to be capable of transmitting torque. The clutch drum 123 is fixed to the inner peripheral surface of The boss portion of the center support 127 is fitted so as to rotate while maintaining a liquid-tight state, and is connected to one end of a second sun gear shaft 128 rotatably disposed on the outer periphery of the first sun gear shaft 113. . The clutch hub 124 is integrated with the outer race of the one-way clutch 20, and the one-way clutch 20
Is spline-fitted to the second sun gear shaft 128. The hydraulic pressure for operating the hydraulic piston 125 is applied to an oil passage 129 formed through the second center support 127.
It is configured to supply / discharge via The other end of the second sun gear shaft 128 is connected to the sun gear 3S of the third planetary gear mechanism 3.

Further, the clutch drum 123 of the multi-plate clutch 22, which constitutes a part of the fourth clutch means K4, also serves as a brake drum. I have.

Fourth clutch means K4 sandwiching the second center support 127
On the opposite side, a multiple disc brake 41 and a one-way clutch 40 constituting the first brake means B1 are arranged. The disc of the multi-plate brake 41 is spline-fitted to the tip of the second center support 127, and the plate is spline-fitted to the outer peripheral surface of the outer race of the one-way clutch 40. Are spline-fitted to the sleeve 130 integrated with the second center support 127. The carrier 3C of the third planetary gear mechanism 3 is connected to the outer race of the one-way clutch 40. Therefore, the multi-plate brake 41 and the one-way clutch 40 are in a parallel relationship with each other, and each of them selectively blocks the rotation of the carrier 3C of the third planetary gear mechanism 3. The hydraulic piston 131 for engaging and disengaging the first brake means B1 is built in the second center support 127,
The hydraulic pressure is supplied / discharged to / from the hydraulic piston 131 through another oil passage (not shown) formed through the center support 127 from the outer peripheral side thereof. The backward movement of the hydraulic piston 131 is performed by a return spring 132.

Then, the third planetary gear mechanism 3 and the first planetary gear mechanism 1
Are arranged in sequence following the first brake means B1, and the carrier 3C of the third planetary gear mechanism 3 is spline-fitted to the first sun gear shaft 113 and its ring gear 3R
Are connected to the carrier 1C of the first planetary gear mechanism 1, and the ring gear 3R and the carrier 1C are connected to the output shaft 5 disposed on the extension of the intermediate shaft 117.

Therefore, even with the structure shown in FIG.
Step or forward 2.5th and 3.5 forward as described above
The speed can be set to seven forward speeds and one reverse speed by adding speed.

It is needless to say that the present invention is not limited to each of the above-described embodiments, and that the present invention has only to have the configuration described in the section of “Means for Solving the Problems”. The mode of connection between the elements in each planetary gear mechanism may be a constant connection or a selective connection via engagement means such as a clutch, and further connects the input shaft and the output shaft. The elements and the elements to be fixed may be determined as needed.

Effect of the Invention As described above, according to the present invention, there is provided a gear transmission using three sets of single pinion type planetary gear mechanisms. In addition to the above, the gear ratio of each gear in the case of setting five forward gears has a relationship close to a geometric series, and the gear ratio of each planetary gear mechanism is appropriate and the outer diameter of the device is small. According to the present invention, it is possible to obtain a compact gear transmission for an automatic transmission having good power performance, shift shock or shift control system.

[Brief description of the drawings]

1 to 16 are skeleton diagrams each showing an embodiment of the present invention, and FIG. 17 is an operation table showing a possible combination of engagement and release of each engagement means for setting each gear position. FIG. 8 is a schematic diagram showing a specific example of the first clutch means,
FIGS. 19 (A) and (B) are schematic views showing a specific example of the fourth clutch means, FIG. 20 is a schematic view showing a specific example of the sixth clutch means, and FIG. 21 is a schematic view showing a specific example of the first brake means. Schematic diagram,
FIG. 22 is a schematic diagram showing a specific example of the second brake means, and FIG.
The drawings are schematic views showing a specific example of the fourth brake means, FIGS. 24 to 48 are skeleton diagrams showing still another embodiment of the present invention, and FIG. 49 is a gear transmission shown in FIG. 31 as a skeleton. It is sectional drawing which shows the example which actualized. 1,2,3… Planetary gear mechanism, 1S, 2S, 3S… Sun gear, 1C, 2C, 3C
… Carrier, 1R, 2R, 3R… Ring gear.

Claims (1)

(57) [Claims] 1. A three-pinion type planetary gear mechanism having a sun gear, a ring gear, and a carrier holding a pinion gear meshing with the sun gear and the ring gear. The carrier of the mechanism is always connected or selectively connected via an engaging means, and the carrier of the first planetary gear mechanism and the ring gear of the third planetary gear mechanism are always connected or via the engaging means. The sun gear of the first planetary gear mechanism and the carrier of the third planetary gear mechanism are always connected or selectively connected via engaging means, and further connected to the sun gear of the second planetary gear mechanism. An automatic transmission, wherein the sun gear of the three planetary gear mechanism is always connected or selectively connected via engagement means. Gear transmission.