JP2890501B2 - 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 particularly to two sets of single pinion type planetary gear mechanisms and one set of double pinion type planetary gear mechanisms. And a gear transmission configured by combining the above.

2. Description of the Related Art As is well known, a planetary gear mechanism has three elements, a sun gear, a ring gear, and a carrier that holds a pinion gear that meshes with the sun gear, a ring gear, and a carrier that holds a pinion gear. By fixing the remaining elements as elements, the input rotation can be increased, or reduced in forward rotation or reduced in reverse, and output.Therefore, conventionally, generally, a plurality of planetary gear mechanisms are combined. To form 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.

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 that can be downsized and that can easily perform shift control.

Means for Solving the Problems In order to achieve the above object, the present invention provides a first sun gear, a first ring gear, a first sun gear, and a first carrier holding a pinion gear meshing with the first ring gear. (1) a planetary gear mechanism, a second sun gear, and a second
A second carrier having a ring gear, a pinion gear meshing with the second sun gear, and a second carrier holding another pinion gear meshing with the pinion gear and the second ring gear;
A planetary gear mechanism, a third sun gear, a third ring gear,
A third planetary gear mechanism having a third carrier that holds a pinion gear meshing with the third sun gear and the third ring gear, wherein the three members of the first ring gear, the second ring gear, and the third ring gear are always connected or engaged. The first carrier and the third carrier are selectively connected via a joining means.
The sun gear is always connected or selectively connected via engagement means, the first sun gear and the second sun gear are always connected or selectively connected via engagement means, and the second sun gear is further connected. The second carrier is selectively connected to the input shaft, or is always connected to the input shaft.

In the apparatus according to the present invention, the first to third ring gears are integrated with each other or individually, the first carrier and the third sun gear are integrated with each other or individually, and the first sun gear and the second sun gear are further integrated. May be integrated or separate from each other as input or output elements or fixed elements, respectively, and independent elements such as the second carrier 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, a first planetary gear mechanism 1 and a third planetary gear mechanism 3 are composed of a single pinion type planetary gear. Mechanism, and the second
The planetary gear mechanism 2 is constituted by a double pinion type planetary gear mechanism, and the respective elements of the respective planetary gear mechanisms 1, 2, 3 are connected as follows. That is, the first planetary gear mechanism 1 includes a sun gear 1S, a ring gear 1R concentrically arranged with the sun gear 1S, and these gears 1S and 1R.
And a carrier 1C that holds a pinion gear that meshes with the carrier 1C. On the other hand, the second planetary gear mechanism 2 includes, as main elements, a sun gear 2S, a ring gear 2R, and a carrier 2C disposed between these gears 2S and 2R and holding at least one pair of pinion gears meshing with each other. It is configured. Also, the third planetary gear mechanism 3
Like the first planetary gear mechanism 1, the sun gear 3S, a ring gear 3R concentrically arranged with respect to the sun gear 3S, and a carrier 3C holding a pinion gear meshing with the gears 3S, 3R are configured as main elements. Have been. The ring gear 1R of the first planetary gear mechanism 1 and the second planetary gear mechanism 2
The ring gear 2R of the third planetary gear mechanism 3 and the ring gear 3R of the third planetary gear mechanism 3 are connected so as to rotate together, and the carrier 1C of the first planetary gear mechanism 1 and the sun gear 3S of the third planetary gear mechanism 3 are connected to each other. Are connected so as to rotate together. On the other hand, a fourth clutch means K4 is provided between the sun gear 1S of the first planetary gear mechanism 1 and the sun gear 2S of the second planetary gear mechanism 2 so that these sun gears 1S, 2S are selectively connected to each other. Has become. Further, a second clutch means K2 is arranged between the carrier 1C of the first planetary gear mechanism 1 and the sun gear 2S of the second planetary gear mechanism 2, and the second clutch means K2 and the carrier 1C of the first planetary gear mechanism 1 The sun gear 2S of the second planetary gear mechanism 2 is selectively connected.

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) through a power transmission means (not shown) such as a torque converter and a fluid coupling, and the input shaft 4 and the carrier 2C of the second planetary gear mechanism 2 are connected to each other. Between the input shaft 4 and the sun gear 2S of the second planetary gear mechanism 1, there is provided a first clutch means K1 for selectively connecting the two. A clutch means K3 is provided.

The above-described clutch means K1, K2, K3, K4 selectively connect the above-described members and release the connection.For example, a conventional automatic transmission such as a hydraulic servo mechanism is generally used. 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 adopted 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 carrier of the first planetary gear mechanism 1 connected to each other;
First brake means B1 for selectively preventing rotation of 1C and the sun gear 3S of the third planetary gear mechanism 3 is provided between the carrier 1C and the sun gear 3S and a transmission case (hereinafter simply referred to as a case) 6. Have been. Also the second
Second brake means B2 for selectively preventing rotation of the sun gear 2S of the planetary gear mechanism 2 is provided between the sun gear 2S and the case 6. Further, third brake means B3 for selectively preventing rotation of the sun gear 1S of the first planetary gear mechanism 1 is disposed between the sun gear 1S and the case 6. These brake means B1, B2, B3 are composed of wet multi-plate brakes and hand brakes driven by a hydraulic servo mechanism or the like employed in conventional general automatic transmissions, or one-way clutches, or a combination of these. In practical use, these brake means B1, B
Needless to say, an appropriate connecting member can be interposed between the case 2 and the components to be fixed by the brake means B1, B2, and B3 and the case 6, respectively.

An output shaft 5 for transmitting rotation to a propeller shaft and a counter gear (not shown) is connected to the carrier 3C of the third planetary gear mechanism 3.

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.
This is achieved by engaging 1, K2, K3, K4 and the brake means B1, B2, B3 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 ρ of the planetary gear mechanisms 1, 2, and 3.
1, ρ2, ρ3 are calculated by ρ1 = 0.510, ρ2 = 0.313, ρ3 = 0.39
This is the value when 8 is set. 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 carrier 2C of the second planetary gear mechanism 2 is connected to the input shaft 4, the sun gear 1S of the first planetary gear mechanism 1 and the sun gear 2S of the second planetary gear mechanism 2 are connected by the fourth clutch means K4, and The carrier 1C of the first planetary gear mechanism 1 and the sun gear 3S of the third planetary gear mechanism 3 connected thereto are fixed. Accordingly, in the second planetary gear mechanism 2, when the carrier 2C rotates with the input shaft 4, the ring gear 2R rotates forward (rotation in the same direction as the input shaft 4; the same applies hereinafter), and the sun gear 2S rotates reversely (input shaft 4). (The rotation is in the opposite direction to that of 4. The same applies hereinafter.) As a result, in the first planetary gear mechanism 1, since the ring gear 1R is connected to the ring gear 2R of the second planetary gear mechanism 2 and the carrier 1C is fixed, the sun gear 1S rotates in the reverse direction, and the third planetary gear In the mechanism 3, the ring gear 3R is connected to the ring gear 2R of the second planetary gear mechanism 2 and rotates forward, and the carrier 3C rotates forward because the sun gear 3S is fixed. As a result, the output shaft 5 connected to the carrier 3C of the third planetary gear mechanism 3 is decelerated with respect to the input shaft 4 together with the carrier 3C and rotates forward.
The first speed has the largest gear ratio in the forward gear. And, as shown in Table 1, the gear ratio is And its specific value is 3.284. in this case,
No power circulation occurs.

<< Second Forward Speed >> While the first clutch means K1 is engaged, at least any two of the second clutch means K2, the first brake means B1, and the second brake means B2 (for example, the first and second The brake means B1, B2) is engaged. That is, the first clutch means K1 and the first and second brake means
When engaging B1 and B2, the second brake means B2 is engaged instead of the fourth clutch means K4 in the first forward speed state. Therefore, in the second planetary gear mechanism 2, the carrier 2C rotates together with the input shaft 4 while the sun gear 2S is fixed, so that the ring gear 2R is reduced in speed with respect to the input shaft 4 and rotates forward. Ring gear 1R
And transmitted to the ring gear 3R of the third planetary gear mechanism 3,
In the third planetary gear mechanism 3, the ring gear 3R slowly rotates forward with the sun gear 3S fixed, so that the carrier 3C is reduced in speed with respect to the ring gear 3R and rotates forward. As a result, the carrier 3C of the third planetary gear mechanism 3
The output shaft 5 connected to the input shaft 4 is decelerated with respect to the input shaft 4 and rotates forward to become the second forward speed. In this case, in the first planetary gear mechanism 1, the sun gear 1S is not connected to the sun gear 2S of the second planetary gear mechanism 2 and the case 6,
In particular, no acceleration / deceleration action is performed. Therefore, the gear ratio in this case is represented by (1 + ρ ₃ ) / (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, the first clutch means K1, the first brake means B1, and the second brake means B2 are engaged to set the second speed, and the third clutch means K3 is used instead of the second brake means B2 in that state.
Is engaged. Therefore, both the carrier 2C and the sun gear 2S of the second planetary gear mechanism 2 are connected to the input shaft 4, and the carrier 1C of the first planetary gear mechanism 1 and the sun gear 3S of the third planetary gear mechanism 3 are fixed. . As a result, in the second planetary gear mechanism 2, the two elements, the carrier 2C and the sun gear 2S, rotate together with the input shaft 4, so that the whole of the second planetary gear mechanism 2 rotates at the same speed as the input shaft 4, and its ring gear
The rotation of 2R is transmitted to the ring gears 1R and 3R of the first planetary gear mechanism 1 and the third planetary gear mechanism 3. In the third planetary gear mechanism 3, since the sun gear 3S is fixed, the ring gear
By rotating the 3R at the same speed as the input shaft 4, the carrier
3C is decelerated with respect to the ring gear 3R and rotates forward. On the other hand, in the first planetary gear mechanism 1, the sun gear 1S is not connected to the sun gear 2S of the second planetary gear mechanism 2 and the case 6, and therefore does not particularly participate in the acceleration / deceleration action.
That is, in this case, substantially, only the third planetary gear mechanism 3 performs a deceleration operation to transmit the rotation of the input shaft 4 to the output shaft 5, and the speed ratio thereof is (1 + ρ _{3) 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 brake means is provided.
Release B1, B2, B3. That is, for example, the first and third clutch means K1 and K3 and the first brake means B1 are engaged in the third speed state, and the second clutch means K2 is replaced by the first brake means B1 in that state. Or the fourth clutch means K4 is engaged. In this manner, the first to third clutch means K1 to K3 are engaged, or the first and third and fourth clutch means K1, K3,
If at least three clutch means are engaged, such as by engaging K4, the entire gear train rotates together with the input shaft 4 and no speed-up / down action occurs, so that the gear ratio is "1".
Becomes Then, for example, the first to third clutch means K
By engaging 1, K2, K3, the driving force from the input shaft 4 can be transmitted to the means shaft 5 without causing power circulation.

<< Fifth forward speed >> The second and third clutch means K2 and K3 are engaged with the third brake output B3. That is, the first to third clutch means K1 to K3 are engaged in the fourth speed state, and the third brake means B3 is engaged instead of the first clutch means K1 in that state. Therefore, in the first planetary gear mechanism 1, the second clutch means K2 is connected to the sun gear 2S of the second planetary gear mechanism 2 connected to the input shaft 4.
The carrier 1C is connected to the input shaft 4 and the sun gear 1S is fixed, so that the ring gear 1R is rotated forward with an increased speed with respect to the input shaft 4, and this is the second planetary gear mechanism 2 and the third planetary gear. The power is transmitted to the ring gears 2R and 3R of the mechanism 3. In the third planetary gear mechanism 3, the sun gear 3S rotates forward with the carrier 1C of the first planetary gear mechanism 1 at the same speed as the input shaft 4, and the ring gear 3R rotates at a higher speed than the input shaft 4; 3C is sun gear 3S and ring gear 3R
It rotates forward at an intermediate speed. Note that the second planetary gear mechanism 2 is not particularly involved in the acceleration / deceleration action since the carrier 2C is not connected to the input shaft 4, but the sun gear 2S
Is the carrier 1C of the first planetary gear mechanism 1 as described above.
Act as a transmission member for connecting the input shaft 4 to the input shaft 4. That is, in this case, the carrier 1C of the first planetary gear mechanism 1 and the third
The sun gear 3S of the planetary gear mechanism 3 is indirectly connected to the input shaft 4, and these planetary gear mechanisms 1 and 3 increase / decrease the speed of the input shaft 4 to increase the speed of the output shaft 5. The transmission proceeds to the fifth forward speed, which is the overdrive stage. The carrier 1C of the first planetary gear mechanism 1 and the sun gear 3S of the third planetary gear mechanism 3 are not directly connected to the input shaft 4, but are connected to the input shaft 4 via the sun gear 2S of the second planetary gear mechanism 2. Accordingly, in the second planetary gear mechanism 2, the sun gear 2S
And the relative rotation speed of the pinion gear with respect to the carrier 2C is reduced, which is advantageous in terms of durability. As shown in Table 1, the gear ratio in this case is expressed by (1 + ρ ₁ + ρ ₃ ) / (1 + ρ ₃ ), 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 1S of the first planetary gear mechanism 1 and the carrier 2C of the second planetary gear mechanism 2 are connected to the input shaft 4, and the carrier 1C of the first planetary gear mechanism 1 and the sun gear 3S of the third planetary gear mechanism 3 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 does not particularly participate in the acceleration / deceleration action. In the first planetary gear mechanism 1, the sun gear 1S rotates together with the input shaft 4 with the carrier 1C fixed, so that the ring gear 1R is reduced in speed with respect to the input shaft 4 and rotates in the reverse direction. Is transmitted to the ring gear 3R. Therefore, in the third planetary gear mechanism 3, the ring gear 3R rotates in the reverse direction while the sun gear 3S is fixed, so that the carrier 3C rotates in the reverse direction at a lower speed. As a result, the rotation of the input shaft 4 is controlled by the first planetary gear mechanism 1 and the third
The rotation is reduced and inverted by the planetary gear mechanism 3 and transmitted to the output shaft 5, and the reverse gear is set. As shown in Table ₁ , the speed ratio is represented by (1 + ρ ₃ ) / ρ ₁ , and the speed ratio is -2.741. Also in this case, no power circulation occurs.

As is clear from the above description of the first to fifth forward speeds and the fifth speed, 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 relation close to the equivalent class or the like, the driving force does not significantly decrease before and after the gear shift, and the power performance of the vehicle can be improved. Since the gear ratio of the gear mechanisms 1, 2, and 3 can be set to an appropriate value of about 0.31 to 0.51, it is possible to provide a compact gear transmission without increasing the diameter of the planetary gear mechanism. 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 is low, the load torque of each gear and each engagement means is small, and the rotation speed of each gear is low. A compact and highly durable gear transmission can be provided. In addition, the gear ratio in the overdrive stage is set to about 0.733 to improve power performance, fuel efficiency and quietness during high-speed driving, and the gear ratio in the reverse stage is -2.741.
It is possible to secure a sufficient driving force by setting the degree to about.
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. That is, the carrier 2C of the second planetary gear mechanism 2 is connected to the input shaft 4 and the sun gear of the first planetary gear mechanism 1 is connected.
1S and the sun gear 2S of the second planetary gear mechanism 2 are fixed. Therefore, in the second planetary gear mechanism 2, the carrier 2C rotates forward with the input shaft 4 while the sun gear 2S is fixed.
The ring gear 2R is decelerated with respect to the input shaft 4 and rotates forward,
This is transmitted to the ring gears 1R, 3R of the first planetary gear mechanism 1 and the third planetary gear mechanism 3. In the first planetary gear mechanism 1, since the sun gear 1S is fixed, the ring gear
When 1R rotates forward at a lower speed than input shaft 4, carrier 1C rotates forward at a lower speed, and this is transmitted to sun gear 3S of third planetary gear mechanism 3. As a result, in the third planetary gear mechanism 3, since the ring gear 3R rotates forward at a lower speed than the input shaft 4, and the sun gear 3S rotates forward at a lower speed, the carrier 3C and the output connected thereto are rotated. The shaft 5 is greatly decelerated with respect to the input shaft 4 and rotates forward.
That is, each of the planetary gear mechanisms 1, 2 and 3 performs a deceleration operation, and reduces the rotation of the input shaft 4 and transmits the rotation to the output shaft 5. And the value of the gear ratio is as shown in Table 1, And its specific value is 1.610. In this case also, no power circulation occurs.

<< 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 third brake means B3. That is, the carrier 2C and the sun gear 2S of the second planetary gear mechanism 2 are connected to the input shaft 4, and the sun gear 1S of the first planetary gear mechanism 1 is fixed. Therefore, since the two elements of the second planetary gear mechanism 2 rotate together with the input shaft 4, the whole of the second planetary gear mechanism 2 integrally rotates forward at the same speed as the input shaft 4, and accordingly, the first planetary gear mechanism 1 and the third planetary gear mechanism Ring gear 1R, 3R of gear mechanism 3
Rotates forward at the same speed as the input shaft 4. In the first planetary gear mechanism 1, the ring gear 1R rotates forward at the same speed as the input shaft 4 with the sun gear 1S fixed, so that the carrier 1C is
It rotates forward at a lower speed and is transmitted to the sun gear 3S of the third planetary gear mechanism 3. As a result, in the third planetary gear mechanism 3, the sun gear 3S is input while the ring gear 3R rotates forward at the same speed as the input shaft 4. Since the carrier 3C rotates forward at a lower speed than the shaft 4, the carrier 3C and the output shaft 5 connected to the carrier 3C
The first planetary gear mechanism 1 and the third planetary gear mechanism 3
The motor rotates forward at the reduced speed. Therefore, as shown in Table 1, the gear ratio is expressed by (1 + ρ ₁ ) (1 + ρ ₃ ) / (1 + ρ ₁ + ρ ₃ ), and its specific value is 1.106. In this case also, no power circulation occurs.

By the way, in the embodiment shown in FIG. 1, the carrier 1C of the first planetary gear mechanism 1 and the sun gear 3S of the third planetary gear mechanism 3 are always connected, but in the present invention, these are selectively connected. It may be configured. An example thereof is shown in FIG. 2. In the gear transmission shown here, in the configuration shown in FIG. 1, the first brake means B1 is connected to the sun gear 3S of the third planetary gear mechanism 3 and the case 6. While placing in between,
A fifth clutch means K5 is arranged between the sun gear 3S and the carrier 1C of the first planetary gear mechanism 1 to selectively connect the carrier 1C of the first planetary gear mechanism 1 and the sun gear 3S of the third planetary gear mechanism 3. It is configured to be connected to. Even with the configuration shown in FIG. 2, each gear can be set without causing power circulation, and the operation table is as shown in Table 2. In the following embodiments, it is also possible to set the shift speed of five to seven forward speeds and one reverse speed. In the operation tables listed in Table 2 and the subsequent figures, the forward 2.5th speed (2.5 th) or 3.5th forward speed (3.5t
h) is displayed as a shift speed to be added to the case where the setting is based on the case where 5 forward speeds and 1 reverse speed 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.

Further, with the additional installation of the fifth clutch means K5, it is possible to provide further brake means, an example of which is shown in FIG. The configuration shown here is the same as the configuration shown in FIG. 2 except that a fourth brake means B4 is additionally installed between the carrier 1C of the first planetary gear mechanism 1 and the case 6, and the operation table is shown in FIG. The results are shown in Table 3. As is apparent from Table 3, even with the configuration shown in FIG.
It is possible to set a shift speed of one speed / reverse. Further, as shown in Table 3, the fourth brake means B4 can be engaged with the first brake means B1, so in this case, the fifth clutch means K5 is released and this clutch means K5 is released.
Can be reduced to zero, and as a result, the fifth clutch means K5 can be small and small in capacity.

In the configuration shown in FIGS. 1 to 3 described above, as is clear from the respective operation tables, although the second brake means B2 can be engaged at the second forward speed, the second clutch means is replaced with the second clutch. The second forward speed can also be set by engaging the means K2, so that the second forward speed can be set even if the second brake means B2 is abolished. The example shown in FIG. 4 is configured such that the second brake means B2 in the configuration of FIG. 3 is eliminated based on such a concept. The operation table is as shown in Table 4.

In the present invention, the carrier 1C of the first planetary gear mechanism 1 is also provided.
The carrier 1C to indirectly connect the
Instead of providing the second clutch means K12 between the first planetary gear mechanism 2 and the sun gear 2S of the second planetary gear mechanism 2, a clutch means may be provided between the carrier 1C and the carrier 2C of the second planetary gear mechanism 2. An example is shown below.

The configuration shown in FIG. 5 is different from the configuration shown in FIG. 3 in that the second clutch means K2 is eliminated, and instead, the carrier 1C of the first planetary gear mechanism 1 and the carrier of the second planetary gear mechanism 2 are replaced.
6C and the other ring gear 1R with the ring gear 2R of the second planetary gear mechanism 2.
A seventh clutch means K7 for selectively connecting R and 3R is provided,
Further, the third brake means B3 is eliminated. With such a configuration, five forward speeds and one reverse speed, or six forward speeds obtained by adding the 2.5th forward speed to this speed,
The first reverse speed can be set, and the operation table is shown in Table 5.

The example shown in FIG. 6 is obtained by adding the above-described fourth brake means B4 to the configuration shown in FIG.
The operation table is shown in Table 6.

In the configurations shown in FIGS. 5 and 6, respectively,
As can be seen from the respective operation tables, the first clutch means K1
Can be engaged in all the speeds, and therefore, even if the first clutch means K1 is abolished from the configuration shown in FIGS. 5 and 6, five forward speeds and one reverse speed, or 6 forward gears with 2.5 forward gears added
It is possible to set the first reverse speed. That is, the example shown in FIG. 7 is different from the configuration shown in FIG.
Are abolished, and the operation table is as shown in Table 7.

In the example shown in FIG. 8, the first clutch means K1 is eliminated from the configuration shown in FIG.
The operation table is as shown in Table 8.

In each embodiment described above, each of the planetary gear mechanisms 1, 2, 3
Are arranged in the order of their numbers from the input shaft 4 side, but their arrangement can be changed as appropriate, and an example is shown in FIG. In the example shown here, each of the planetary gear mechanisms 1, 2, and 3 of the configuration shown in FIG. 3 is connected to the second planetary gear mechanism 2, the first planetary gear mechanism 1, and the third planetary gear mechanism from the input shaft 4 side. 3, the arrangement of the clutch means K1 to K5 and the arrangement of the brake means B1 to B4 are changed, and the connection relation of the elements is the same as that shown in FIG. With such a configuration, the second clutch means K2 can be arranged outside the connecting member such as the connecting drum without the number of shafts passing through the central portion being three or more, and restrictions on the outer diameter can be eliminated. Further, even with the configuration shown in FIG. 9, it is possible to set the shift speed of five forward steps and one reverse step or seven forward steps and one reverse step. There are many patterns of combinations of engagement / disengagement of the respective engagement means for setting these shift speeds, which are summarized in FIG. In FIG. 10, a circle indicates engagement, a blank indicates release, and an asterisk indicates that the engagement may be performed.

As is known from FIG. 10, the first brake means B1
And second brake means B2 and fourth brake means B4
Can be released at any speed depending on the combination of engagement and release of the other clutch means and brake means, and therefore any one of these brake means B1, B2, B4 or The two can be abolished. From FIG. 10, various modifications of the present invention can be easily inferred.

By the way, in each embodiment described above, each of the clutch means K1 to
Although K7 and each of the brake means B1 to B4 are indicated by a symbol of a multi-plate clutch or a multi-plate brake, according to the present invention, in order to facilitate control for shifting and to reduce shift shock, the clutch means and the brake means are used. 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
Carrier 1C of first planetary gear mechanism 1 and third planetary gear mechanism 3
Clutch means for selectively connecting the sun gear 3S (No. 5)
The case where the clutch means K5) is provided is different from the case where the clutch means is not provided, and is different for each shift pattern including a so-called jump shift other than the shift to the adjacent shift speed. As shown in FIGS. 2 to 9, the position where the one-way engaging means is provided is shown as an example when the fifth clutch means K5 is provided.

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 2S of the first planetary gear mechanism 1
1S, between the carrier 1C of the first planetary gear mechanism 1 and the sun gear 3S of the third planetary gear mechanism 3, or at least one location between the carrier 1C of the first planetary gear mechanism 1 and the case 6. And a one-way clutch such as a one-way clutch may be interposed. Regarding the shift between the first speed and the 2.5th speed, at least one of between the carrier 1C of the first planetary gear mechanism 1 and the case 6 or between the sun gear 3S of the third planetary gear mechanism 3 and the case 6 One side may be provided with one-way engagement means. Regarding the shift between the first speed and the third speed, the shift between the sun gear 2S of the second planetary gear mechanism 2 and the sun gear 1S of the first planetary gear mechanism 1, the carrier 1C of the first planetary gear mechanism 1 and the third One-way engagement means may be provided at at least one location between the sun gear 3S of the planetary gear mechanism 3 and the carrier 1C of the first planetary gear mechanism 1 and the case 6.
Regarding the shift between the first speed and the 3.5th speed, the sun gear 2S of the second planetary gear mechanism 2 and the sun gear 2S of the first planetary gear mechanism 1
1S, the carrier 1C of the first planetary gear mechanism 1 and the case 6
, A one-way engaging means may be interposed at least at any one position between the sun gear 3S of the third planetary gear mechanism 3 and the case 6. 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 carrier of the first planetary gear mechanism 1
One-way engagement means may be interposed between at least one of the space between 1C and the case 6 or between the sun gear 3S of the third planetary gear mechanism 3 and the case 6. Regarding the shift between the first speed and the fifth speed, the sun gear of the second planetary gear mechanism 2
2S and the sun gear 1S of the first planetary gear mechanism 1, between the carrier 1C of the first planetary gear mechanism 1 and the case 6, between the sun gear 3S of the third planetary gear mechanism 3 and the case 6, the second planet One-way engagement means may be interposed at least at any one position between the carrier 2C of the 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 2.5th 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 3S of the third planetary gear mechanism 3 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 third gear
One-way engagement means may be interposed between at least one of the sun gear 3S of the planetary gear mechanism 3 and 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 3S of the third planetary gear mechanism 3
, One-way engagement means is interposed at least at one place between the sun gear 2S of the second planetary gear mechanism 2 and the case 6 and between the sun gear 3S of the third planetary gear mechanism 3 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,
One-way engaging means may be interposed between at least one of the sun gear 2S of the second planetary gear mechanism 2 and the case 6 or at least one of the sun gear 3S of the third planetary gear mechanism 3 and the case 6. Regarding the shift between the second speed and the fifth speed,
Between the sun gear 2S of the second planetary gear mechanism 2 and the case 6; between the sun gear 3S of the third planetary gear mechanism 3 and the case 6;
One-way engagement means may be interposed at least at any one position between the carrier 2C of the planetary 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 1S of the first planetary gear mechanism 1 and the sun gear 2S of the second planetary gear mechanism 2 and the case 6 , The sun gear 1S of the first planetary gear mechanism 1 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 speed change 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 1S of the first planetary gear mechanism 1 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 1S of the first planetary gear mechanism 1 and the case 6 What is necessary is just to interpose a one-way engagement means. No. 2.
Regarding 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 1S of the first planetary gear mechanism 1 and the sun gear 2S of the second planetary gear mechanism 2 and the case 6 During this period, a one-way engaging means may be interposed at least at any one position between the carrier 2C 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 3S of the third planetary gear mechanism 3 and the case 6. May be interposed. Regarding the shift between the third speed and the fifth speed, between the sun gear 3S of the third planetary gear mechanism 3 and the case 6, the sun gear 2S and the ring gear 2R of the second planetary gear mechanism 2, or the carrier 2C or the third planetary gear A one-way engagement is provided between the input shaft 4 and the ring gear 3R of the second planetary gear mechanism 2 or at least one of the carrier 2C and the ring gear 3R of the third planetary gear mechanism 3 between the ring gear 3R of the gear mechanism 3 and the input shaft 4. What is necessary is just to interpose a combining means. 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 1S of the first planetary gear mechanism 1 and the case 6. Regarding the shift between the 3.5th speed and the 5th speed, the sun gear 2S and the ring gear 2R of the second planetary gear mechanism 2 or the carrier 2C or the ring gear 1R of the first planetary gear mechanism 1 or the ring gear 3R of the third planetary gear mechanism 3 Between the input shaft 4 and the ring gear 2R or the carrier 2C of the second planetary gear mechanism 2 or the ring gear 1R of the first planetary gear mechanism 1 or the ring gear of the third planetary gear mechanism 3.
The one-way engagement means may be interposed in at least one of the 3Rs.

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 ring gear 2R and the carrier 2C of the second planetary gear mechanism 2, the sun gear 1S and the ring gear 1R of the first planetary gear mechanism 1, the carrier 3C and the ring gear of the third planetary gear mechanism 3. One-way engagement means may be interposed between any of the 3Rs. Regarding the ring gear 2R of the second planetary gear mechanism 2, any other element (including the input shaft 4) except the ring gear 1R of the first planetary gear mechanism 1, the ring gear 3R of the third planetary gear mechanism 3, and the case 6 is included. And a one-way engaging means may be interposed between them. Each of the carrier 2C of the second planetary gear mechanism 2 and the sun gear 1S of the first planetary gear mechanism 1 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. First planetary gear mechanism 1
Of the carrier 1C between the ring gear 2R and the carrier 2C of the second planetary gear mechanism 2, the sun gear 1S and the ring gear 1R of the first planetary gear mechanism 1, and the carrier 3C and the ring gear 3R of the third planetary gear mechanism 3. What is necessary is just to interpose a one-way engagement means. Regarding the ring gear 1R of the first planetary gear mechanism 1, the ring gear of the second planetary gear mechanism 2
2R and the ring gear 3R of the third planetary gear mechanism 3 and any other element except the case 6 (including the input shaft 4)
And a one-way engaging means may be interposed between them. The sun gear 3S of the third planetary gear mechanism 3 includes a ring gear 2R and a carrier 2C of the second planetary gear mechanism 2, a sun gear 1S and a ring gear 1R of the first planetary gear mechanism 1, and a carrier 3C and a ring gear 3R of the third planetary gear mechanism 3. The one-way engagement means may be interposed between any one of them. Regarding the carrier 3C of the third planetary gear mechanism 3, a one-way engagement means may be interposed between the carrier 3C and the other components (including the input shaft 4) except for the case 6. The ring gear 3R of the third planetary gear mechanism 3 is the same as the ring gear 2R of the second planetary gear mechanism 2, the ring gear 1R of the first planetary gear mechanism 1, and other elements (including the input shaft 4) except for the case 6. What is necessary is just to interpose a one-way engagement means between them.

As shown in FIG. 1, in a configuration in which the carrier 1C of the first planetary gear mechanism 1 and the sun gear 3S of the third planetary gear mechanism 3 are always connected without providing the fifth clutch means K5, For example, the location where the one-way engaging means can be installed is more restricted than in the case described above, for example, the one-way engaging means cannot be provided, and the location where the one-way engaging means can be installed may be appropriately selected.

The method of using the one-way engagement means is described in Japanese Patent Application No. 63-176270 or Japanese Patent Application No.
The description given in the specification and the drawings attached to the application No. 1670 can be adopted, and an example in which such an improvement is added to the engagement means is shown below.

In the example shown in FIG. 11, in the configuration shown in FIG. 4 described above, the fourth clutch means K4 is constituted by the multi-plate clutch 10 and the one-way clutch 11 which are in a parallel relationship with each other, and the first brake means B1 Is constituted by a multi-disc brake 20 and a one-way clutch 21 arranged in parallel with each other, and a third brake means B3 is arranged in parallel with a multi-disc brake 30 and a one-way clutch 31 arranged in series with each other. The fourth brake means B4 is constituted by a multi-disc brake 40 and a one-way clutch 41 which are in parallel with each other. An example of an operation table of the gear transmission having the configuration shown in FIG. 11 is as shown in Table 9. It should be noted that in the following operation table, a circle indicates an engaged state, and a cross indicates a released state, which is the same as the above-mentioned operation table. Indicates the engaged state during 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. 12, one of the multiple disc brakes 32 in the third brake means B3 in the configuration shown in FIG. 11 is replaced with a band brake 33. The operation table is the same as that in Table 9 except that reference numeral 32 in column B3 is replaced with reference numeral 33.

In the example shown in FIG. 13, the third brake means B3 is constituted only by the band brake 33 in the configuration shown in FIG. If you show an example of the operation table, the tenth
It is as shown in the table.

The example shown in FIG. 14 is an example in which the one-way engaging means is employed as the engaging means in the configuration shown in FIG. That is, the fourth of the first to fifth clutch means K1 to K5
The clutch means K4 includes a multi-plate clutch 10 and a one-way clutch 11 which are in a parallel relationship with each other. The first brake means B1 of the brake means is constituted by a one-way clutch 21 and a bant brake 22 which are in a parallel relationship with each other, and the second brake means B2 and the third brake means B3 are each provided with a single band brake. And the fourth brake means B4 is constituted by a single multi-disc brake. Other configurations are the same as those shown in FIG. An example of an operation table of the gear transmission having the configuration shown in FIG. 14 is shown in Table 11.

The configuration shown in FIG. 15 is different from the configuration shown in FIG. 14 in that the third brake means B3 is connected in parallel with the multi-disc brake 30 and the one-way clutch 31 which are in series with each other. And the other configuration is the same as the configuration shown in FIG. An example of the operation table is shown in Table 12.

The example shown in FIG. 16 eliminates the second brake means B2 in the configuration shown in FIG.
Is constituted by a multi-plate clutch 51 and a one-way clutch 52 which are in a parallel relationship with each other, and the other configuration is the same as the configuration shown in FIG. An example of the operation table is shown in Table 13.

In the example shown in FIG. 17, the second brake means B2 in the configuration shown in FIG. 14 is omitted, and the fourth brake means B4 is connected to the multi-disc brake 40 and the one-way clutch 41 The one-way clutch 41 is disposed on the inner peripheral side of the multi-disc brake 40, and the other configuration is the same as the configuration shown in FIG. In other words, the configuration shown in FIG. 17 is different from the configuration shown in FIG. 13 in that the arrangement of the one-way clutch 41 forming the fourth brake means B4 is changed and the multiple discs forming the first brake means B1 are changed. The brake 20 is replaced with a band brake 22. Therefore, an example of the operation table is the same as Table 10 described above.

The example shown in FIG. 18 is the same as the structure shown in FIG. 17 except that the fourth brake means B4 of the structure shown in FIG. 17 is constituted by a single one-way clutch. is there. An example of the operation table is shown in Table 14. In the structure shown in FIG. 18, the carrier 1C of the first planetary gear mechanism 1 is fixed by engaging the band brake 22 of the first brake means B1 and the multi-plate clutch which is the fifth clutch means K5 during reverse travel. Therefore, a large load torque is applied to the fifth clutch means K5, and therefore the fifth clutch means
In order to reduce the capacity of K5 and maintain its durability, it is preferable to reduce the engine output or the input torque to the gear transmission during reverse travel.

In the example shown in FIG. 19, the second brake means B2 of the above-described configuration shown in FIG. 14 is replaced with a configuration comprising a multi-plate brake 61 and a one-way clutch 62 which are in a serial relationship with each other. This is similar to the configuration shown in FIG. An example of the operation table is shown in Table 15.

As described above, the present invention has been described with reference to the first to eighteenth embodiments. However, it is needless to say that the present invention is not limited to each of the above-described embodiments. Means for Solving the Problem "is sufficient as long as it has the configuration described in the section, and the connection form of the elements in each planetary gear mechanism is always connected through engagement means such as a clutch. The connection may be selectively connected, and the elements for connecting the input shaft and the output shaft and the elements to be fixed may be determined as needed. Further, in the present invention, the one-way engaging means such as the one-way clutch may be employed in any one of the clutch means or the brake means, or may be employed in a plurality of clutch means or the brake means.

Effect of the Invention As described above, according to the present invention, a gear transmission using two sets of single pinion type planetary gear mechanisms and one set of double pinion type planetary gear mechanisms, using a small number of engagement means 5 to 7 forward speeds can be performed, and when set to 5 forward speeds, the gear ratio of each speed stage is close to a geometric series, and the gear ratio of each planetary gear mechanism is Therefore, according to the present invention, it is possible to obtain a compact gear transmission for an automatic transmission with good power performance, shift shock or shift control system.

[Brief description of the drawings]

FIGS. 1 to 9 are skeleton diagrams each showing an embodiment of the present invention, and FIG. 10 summarizes combinations of engagement and disengagement that can be set for setting each shift speed in the configuration shown in FIG. FIG. 11 to FIG. 19 are skeleton diagrams showing another embodiment of the present invention. 1,2,3… Planetary gear mechanism, 1S, 2S, 3S… Sun gear, 1C, 2C, 3C
... Carrier, 1R, 2R, 3R ... Ring gear, 4 ... Input shaft.

Claims (1)

(57) [Claims] A first sun gear, a first ring gear, and a first sun gear;
A first planetary gear mechanism having a first carrier holding a pinion gear meshing with the sun gear and the first ring gear; a second sun gear; a second ring gear; a pinion gear meshing with the second sun gear; and the pinion gear and the second ring gear. A second planetary gear mechanism having a second carrier holding another pinion gear meshing with the third carrier, a third sun gear, a third ring gear, and a third carrier holding a pinion gear meshing with the third sun gear and the third ring gear; And a third planetary gear mechanism having a first ring gear, a second ring gear, and a third ring gear. The first ring gear, the second ring gear, and the third ring gear are always connected or selectively connected via engagement means. And the first sun gear and the second sun gear are always connected or selectively connected via engagement means. And the second sun gear is selectively connected to the input shaft, and the second carrier is selectively connected to the input shaft or is always connected. A gear transmission for an automatic transmission, comprising: