JPH0396744A - Mechanical reduction gear for automatic transmission - Google Patents

Abstract

PURPOSE:To reduce the number of engaging means to be controlled at the time of gear change by combining a ravigneaux type epicyclic gear mechanism and a single pinion type epicyclic gear mechanism through a plurality of one- way clutches. CONSTITUTION:A ravigneaux type epicyclic gear mechanism 1 and a single pinion type epicyclic gear mechanism 3 are disposed concentrically with an input shaft 4 and an output shaft 5 through a plurality of one-way clutches 12, 31, 42, 63. Clutches K1-K4, brakes B1-B3, band brakes 41, 61, multiple disc brakes 10, 11, 30, and the one-way clutches 12, 31, 42, 63 are selectively engaged (marked by O, marked by at the time of engine brake), whereby forward 5 steps, reverse, and 2.5-speed are obtained. Thus, the number of engaging means to be controlled at the time of gear change can be reduced, and gear change shock can be reduced.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application This invention relates to a gear transmission that constitutes a gear train in an automatic transmission, and in particular two sets of single pinion type planetary gear mechanisms and one set of double pinion type planetary gear mechanisms. Alternatively, the present invention relates to a gear transmission mainly consisting of a set of Ravigneau type planetary gear mechanism and a set of single pinion type planetary gear mechanism.

Prior art An example of a gear transmission of this type that can set five forward gears and a reverse gear is disclosed in Japanese Patent Laid-Open No. 54-1.
No. 32058, and a brief explanation of this is as follows.

That is, in FIG. 9, the Ravigneau type planetary gear mechanism 1 includes a ring gear R, a carrier C holding a pinion gear IP that meshes with the ring gear R, a sun gear 1S that meshes with the pinion gear IP, and another pinion gear that meshes with the pinion gear ↓P. This Ravigneaux-type planetary gear mechanism 1 is constructed mainly of a second sun gear 2S that meshes with the IP.
The single pinion type planetary gear mechanism 3 arranged on the same axis as the ring gear 3R, the sun gear 3S arranged concentrically with the ring gear 3R, and the carrier 3C holding the pinion gear 3P that meshes with these gears 3R and 3S. It is configured. The ring gears R and 3R of these planetary gear mechanisms 1.3 are connected to each other, and the carrier C of the Ravigneau type planetary gear mechanism 1 and the sun gear 3S of the single-binion type planetary gear mechanism 3 are in a parallel relationship with each other. Certain one-way clutch F and multi-plate clutch C4
They are connected via a clutch means (temporarily referred to as a fourth clutch means) K4 consisting of. Further, the output shaft 5 is connected to the carrier 3C of the single pinion type planetary gear mechanism 3, while the human power shaft 4 is connected to the other sun gear 2S of the Ravigneau type planetary gear mechanism and the carrier C on the Ravigneau type planetary gear mechanism. , and the sun gear IS of the Ravigneaux-type planetary gear mechanism ↓, clutch means (temporarily, the first clutch means K1, the second clutch means K2, and the third clutch means K3)
). Further, as a brake means, a first brake means B is a multi-plate brake or a band brake that selectively fixes the sun gear 3S of the single pinion type planetary gear mechanism 3.
l is provided, and a first brake means B2 for selectively fixing the carrier C of the Ravigneau planetary gear mechanism 1 is provided between the carrier C and the transmission case (hereinafter simply referred to as the case) 6, and further A third brake means B3 is provided for selectively fixing one sun gear 1S of the Ravigneau planetary gear mechanism 1.

Problems to be Solved by the Invention In the above-mentioned gear transmission, gear shifting is performed in five forward gears and an upper reverse gear by appropriately setting the engagement and release states of each clutch means and brake means. 4
The speed is set by engaging each of the above-mentioned second and fourth clutch means Kl, K2, K4, and the adjacent fifth forward speed is set by engaging the second and fourth clutch means K2.
, K4 and the third brake means B3 are engaged and set, so when shifting between these gears, the first clutch means K1 and the third brake means B3 are engaged and released. need to be changed in parallel. Also the second
When changing gears between the third gear and the third gear, it is necessary to switch between the engaged and disengaged states of the third clutch means K3 and the third brake means B3, and also between the third gear and the fourth gear. In the shift between the two, it is necessary to switch between the engaged and released states of the third and fourth clutch means K3 and K4 and the first brake means Bl. As described above, in the above-mentioned conventional gear transmission, there are problems in that there are many retaining means that must be switched to perform a shifting operation, which may worsen shift shock or make shift control difficult. In addition, in the conventional gear transmission described above, the one-way clutch F is provided between the carrier C of the Ravigneau type planetary gear mechanism 1 and the sun gear 3S of the single pinion type planetary gear mechanism 3, which rotate together. When carrying out this process, there was a risk that the rotational inertia of the engine itself could have a negative effect on the speed change characteristics or the dynamic balance. The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a gear transmission device for an automatic transmission with good shifting characteristics.

Means for Solving the Problems In order to achieve the above object, the present invention improves the above-mentioned gear transmission to make it more practical. A single pinion type first planetary gear mechanism and a double pinion type second planetary gear mechanism connected and integrated, or a Ravigneaux type planetary gear substantially equivalent to these first planetary gear mechanism and second planetary gear mechanism. mechanism, and a single-binion type third planetary gear mechanism, the connected and integrated ring gear or the ring gear of the Ravigneau type planetary gear mechanism and the ring gear of the third planetary gear mechanism are capable of transmitting power, and the connected The integrated carrier or the carrier of the Ravigneau type planetary gear mechanism and the sun gear of the third planetary gear mechanism are connected via a clutch means, and the brake means for selectively fixing the sun gear of the third planetary gear mechanism and said connection. A braking means for selectively fixing an integrated carrier or a carrier of the Ravigneau planetary gear mechanism, and a sun gear of the first engineering planetary gear mechanism or a corresponding one of the sun gears of the Ravigneau planetary gear mechanism. Braking means are provided to
Furthermore, the sun gears of the first planetary gear mechanism and the second planetary gear mechanism or the two sun gears of the Ravigneau type planetary gear mechanism and the carrier integrated with the carrier or the carrier of the Ravigneau type planetary gear mechanism are connected to the input shaft by a clutch means. In a gear transmission for an automatic transmission in which the carrier of the third planetary gear mechanism and the output shaft are selectively coupled and capable of transmitting power, one of the sun gear of the upper planetary gear mechanism or the Ravigneau type planetary gear mechanism. a clutch means for selectively coupling the sun gear of the second planetary gear mechanism or the other sun gear of the Ravigneau planetary gear mechanism with the input shaft; ↓ A brake means for selectively fixing the sun gear of the planetary gear mechanism or one sun gear of the Ravignault-type planetary gear mechanism, and a brake means for selectively fixing the connected and integrated carrier or the carrier of the Ravigneau-type planetary gear mechanism. , the brake means for selectively fixing the sun gear of the third planetary gear mechanism includes a unidirectional engagement means whose torque transmission capacity differs depending on the direction of torque action. .

Operation Therefore, in the gear transmission of the present invention, when performing a gear shift, the unidirectional engagement means included in the retaining means such as the clutch means and the brake means involved in the gear shift acts to change the engaged state or The release state changes automatically according to the direction of torque action, and as a result, the number of engagement means to be controlled for gear shifting is reduced, making control easier and at the same time providing better gear shifting shock.

Example Next, embodiments of the invention will be described with reference to the drawings.

The gear transmission of the present invention differs from the conventional gear transmission described above in the structure and arrangement of engagement devices such as clutch means, but has the same basic structure of the gear train or the conventional device as described above.
First, the basic structure of the gear train targeted by this invention will be briefly explained.

The gear train shown in FIG. 2 is mainly composed of one set of Ravigneau type planetary gear mechanism and one set of single pinion type planetary gear mechanism, and this is the fourth gear train in the gear train shown in FIG. Clutch K4 is shown with the symbol of one multi-disc clutch, and the other engagement means and connection relationships of the elements are the same as those shown in FIG.

The gear train shown in FIG. 3 is obtained by replacing the Ravigneau type planetary gear mechanism described above with an equivalent single pinion type planetary gear mechanism and a double pinion type planetary gear mechanism. In other words, the first gear mechanism is a single pinion type planetary gear mechanism.
A planetary gear mechanism 101, a second planetary gear mechanism 102 which is a double pinion type planetary gear mechanism, and a third planetary gear mechanism 3 which is a single pinion type planetary gear mechanism are arranged on the same axis, and the respective ring gears IOIR and IO2R are arranged on the same axis.
, '3R are connected to each other, and the carrier IOIc of the first planetary gear mechanism 101 and the second planetary gear mechanism 102
．． I02C are connected to each other, and the first planetary gear mechanism 101 and the second planetary gear mechanism 1 are connected to each other.
The sun gear 3S of the third planetary gear mechanism 3 is connected to the carriers INc and I02C of 02 via the fourth clutch means K4. Also, a first clutch means K is provided between the input shaft 4 and the sun gear 1G2s of the second planetary gear mechanism 102.
1 is provided, and a second clutch means K is provided between the input shaft 4 and the carrier 102C of the second planetary gear mechanism 1G2.
2 is provided, and further includes an input shaft 4 and a first planetary gear mechanism 10.
A third clutch means K3 is provided between the first sun gear 101S and the second sun gear 101S. The arrangement of the brake means is almost the same as that shown in FIG. Means B2 is the first
The third brake means B3 is provided to selectively fix the carriers IOIC and 102C of the planetary gear mechanism 101 and the second planetary gear mechanism 102, and the third brake means B3 is provided to selectively fix the sun gear LDIS of the first planetary gear mechanism 101. It is being

In the configuration shown in FIGS. 2 and 3 above, it is basically possible to set five forward gears and a reverse gear, and the 2.5 gears between the second forward gear and the third forward gear are basically possible. By adding speed, it is possible to set six forward speeds and one reverse speed. There are many combinations of engagement and disengagement of each engagement means for setting these gear stages, and Table 1 summarizes these combinations. In addition, in Table 1, the ○ mark indicates a congruent state,
A blank column indicates a released state, and an asterisk (*) indicates that it may be engaged.

Table 1 FIG. 1 is a diagram showing an embodiment of the present invention constructed using an engagement means having a one-way characteristic among the basic configurations shown in FIG. 2 described above, in which the first clutch The means Kl includes a multi-disc clutch 10 and another multi-disc clutch arranged in parallel relation to the multi-disc clutch 10, and a Ravigneau type arrangement arranged in series relation to the other multi-disc clutch 11. It is composed of a one-way clutch 12 capable of transmitting torque to the second sun gear 2S of the planetary gear mechanism 1. Further, the fourth clutch means K4 is disposed in a parallel relationship with the multi-disc clutch 30 and is mounted on a carrier C of the Ravigneau type planetary gear mechanism.
and a one-way clutch 31 capable of transmitting torque to the sun gear 3S of the third planetary gear mechanism 3. Further, among the brake means, the t-th brake means B1 is connected to a band brake 4l which is in a parallel relationship with each other and a third brake means B1.
The third braking means B3 is composed of a one-way clutch 42 disposed between the sun gear 3S of the planetary gear mechanism 3 and the case 6, and the third braking means B3 is composed of a band brake 6 and a one-way clutch 42 disposed between the sun gear 3S of the planetary gear mechanism 3 and the case 6. It is composed of a multi-disc brake 62 and a one-way clutch 63 in series with the multi-disc brake 62.

Note that the second clutch means K2 and the third clutch stage K3
is constituted by a multi-disc clutch as shown in the symbol, and the second braking means B2 is also constituted by a multi-disc brake as shown in the symbol. With the gear transmission having the structure shown in FIG. 1, it is also possible to set a gear position of 5 or 6 forward gears and t reverse gear, and the operation table thereof is shown in Table 2. Note that in Table 2 and the tables shown below, the ○ mark indicates the engaged state, the blank column indicates the released state, and the ◎ mark indicates the engaged state during engine braking. In addition, the symbols a and b in the gear column indicate other combinations of engagement and release of the engaging means to set the gear, and are engaged in the order of the symbols when shifting gears. The engagement/disengagement state may be changed, and any combination may be selected to set the gear position.

Table 2 Here, each gear stage of the gear transmission shown in FIG. 1 will be briefly explained with reference to Table 2.

The first forward speed is set by engaging the other multi-disc clutch 11 constituting the first clutch means Kl and the second brake means B2 as controlled objects (column a of Table 2),
Alternatively, it is set by engaging only the first clutch means K1 as the controlled object (column b in Table 2). In any of these cases, the one-way clutch 12 of the first clutch means K1, the one-way clutch 31 of the fourth clutch means K4, and the one-way clutch 42 of the first brake means B1 are engaged depending on the way the torque acts. .

As a result, the second sun gear 2S of the Ravigneau planetary gear mechanism 1 is connected to the input shaft 4 and rotates together with the input shaft 4,
Also, the carrier C and the sun gear 3 of the third planetary gear mechanism 3
Since the sun gear 3S of the third planetary gear mechanism 3 is fixed, the carrier C of the Ravigneau planetary gear mechanism 1 is also fixed. Therefore, in the Ravigneau type planetary gear mechanism 1, the carrier C is fixed and the second
Since the sun gear 2S rotates together with the input shaft 4, the tth sun gear 2S rotates together with the input shaft 4.
The sun gear Is rotates in the opposite direction (rotation in the opposite direction to the input shaft 4; the same applies hereinafter), and the ring gear R rotates forward at a lower speed than the input shaft 4 (rotates in the same direction as the input shaft 4; the same applies hereinafter). The signal is transmitted to the ring gear 3R of the third planetary gear mechanism 3. In addition, in the third planetary gear mechanism 3, since the ring gear 3R rotates forward at a lower speed than the input shaft 4 while the sun gear 3S is fixed, the carrier 3C and the output shaft 5 connected thereto are rotated faster than the ring gear 3R. Rotates forward at low speed. As a result, the rotation of the input shaft 4 is decelerated by each planetary gear mechanism {, 3 and transmitted to the output shaft 5, resulting in the first speed having the largest gear ratio among the forward speeds.

Note that when this first forward speed is set by releasing the second brake means B2 as shown in column b, the sun gear 3S of the third planetary gear mechanism 3 is fixed via the one-way clutch 31 in the fourth clutch means K4. As a result, the one-way clutch 31 has a large torque (1.0 of the input torque).
(approximately 24 times), which is disadvantageous in terms of durability.

On the other hand, in other forward speeds such as the second forward speed, which will be described later, the second brake means B2 is released. Therefore, it is preferable to set the forward speed t by engaging the second brake means B2, and release the second brake means B2 immediately before shifting to another forward gear. The durability of the one-way clutch 31 in the four-clutch means K4 can be improved and its size can be reduced.

In order to apply the engine brake at the forward speed, one of the multi-disc clutches 10 in the first clutch means Kl, the multi-disc clutch 30 in the fourth clutch means K4, and the band brake 4 in the third brake means Bl are required.
1. Note that when the second brake means B2 is engaged, the sun gear 3S of the third planetary gear mechanism 3 engages the multi-disc clutch 30 of the fourth clutch means K4.
Alternatively, the sun gear 3S of the third planetary gear mechanism 3 may be fixed by engaging the band brake 41 of the first brake means B1.

The second forward speed is set by engaging the other multi-disc clutch 1↓ of the first clutch means K1 and the multi-disc brake 62 of the third brake means B3 as controlled objects. In this case, the one-way clutch l2 of the first clutch means Kl, the one-way clutch 42 of the first brake means B1, and the one-way clutch 63 of the third brake means B3 are engaged, but the one-way clutch 3 of the fourth clutch means K4 The mechanism will not engage depending on the way the torque acts. Therefore, in the Ravigneau planetary gear mechanism 1, the second sun gear 2S rotates together with the input shaft 4 while the first sun gear 1S is fixed, so the carrier C rotates forward at a lower speed than the input shaft 4. , and the ring gear R rotates forward at a lower speed than the input shaft 4 and faster than the carrier C, and this is transmitted to the ring gear 3R of the third planetary gear mechanism 3. Further, in the third planetary gear mechanism 3, the one-way clutch 42 of the third e-brake means B1 is engaged and its sun gear 3S is fixed, and the ring gear 3R rotates forward at a lower speed than the input shaft 4, so that the carrier 3
C rotates forward at a lower speed than ring gear 3R. Therefore, in this case as well, each planetary gear mechanism 1.3 performs a deceleration action, and the rotation of the input shaft 4 is decelerated and transmitted to the output shaft 5, and the output shaft 5 rotates slightly faster than in the case of the above-mentioned first working speed. 2nd forward speed. In order to apply the engine brake in this second speed, it is necessary to prevent the action of each of the one-way clutches described above, so the multi-disc clutch 10 in the first clutch means K1, the first brake means Bl, and the third brake means The band brakes 41 and 61 in B3 are respectively engaged.

Therefore, when comparing the case of the above-mentioned first speed and this second speed, the engaging means to be controlled is the third brake means B.
The only difference is the multi-disc brake 62 of the fourth clutch means K4, and the release of the fourth clutch means K4 is automatically performed by the one-way clutch 31, so that the shift shock is improved and control is facilitated.

The third forward speed engages the multi-disc clutch 11 of the first clutch means K1, the second clutch means K2, and the multi-disc brake 62 of the third brake B3 as engaging means to be controlled. Accordingly, the one-way clutch 12 of the first clutch means K1 and the one-way clutch 42 of the first brake means Bl
are engaged according to the direction in which the torque is applied, and the one-way clutches 31.63 of the fourth clutch means K4 and the third brake means Bl are not engaged. Therefore, in the Ravigneau type planetary gear mechanism 1, the carrier C and the second sun gear 2S
and rotates together with the human power shaft 4, the whole rotates as one, and the rotation of the ring gear R is transmitted to the ring gear 3R of the third planetary gear mechanism 3. Since the one-way clutch 42 of the first brake means B1 acts to fix the sun gear 3S, the carrier 3C and the output shaft 5 connected thereto rotate forward at a lower speed than the ring gear 3R, that is, the output shaft 5 is the third
The planetary gear mechanism 3 rotates the input shaft 4 in the forward direction at a reduced rotation speed. In other words, in this case, only the third planetary gear mechanism 3 performs the deceleration action. Therefore, the shift between the second and third speeds can be achieved by controlling only the second clutch means K2, and the shift shock is improved.
It is also easy to control. In addition, when applying the engine brake, the multi-disc clutch ■0 of the first clutch means K1
and the band brake 41 of the first brake means B1 are engaged.

For the fourth forward speed, the engagement means to be controlled are the multi-disc clutch l of the first clutch means K1, the multi-disc clutch 30 of the second clutch means K2, the fourth clutch means K4, and the multi-disc clutch of the third brake means B3. The brake 62 is engaged. That is, in the case of the third speed described above, the multi-disc clutch 30 of the fourth clutch means K4 is newly engaged. Further, as a one-way clutch, only the one-way clutch 12 in the first clutch means K1 is engaged, and the other one-way clutches are not engaged. Therefore, in the Ravignault-type planetary gear mechanism 1, the two elements, the second sun gear 2S and the carrier C, are connected to the input pongee 4, and in the third planetary gear mechanism 3, the ring gear 3R is connected to the ring gear of the Ravigneau-type planetary gear mechanism. R
Since the sun gear 3S is connected to the carrier C, the whole of the Ravigneau planetary gear mechanism 1 and the third planetary gear mechanism 3 rotate together with the input shaft 4.

That is, in this case, the rotation of the input shaft 4 is directly transmitted to the output shaft 5 without any gear change action occurring.

And, as is clear from the above explanation and Table 2, the shift between the fourth speed and the third speed is performed by the fourth clutch means K.
This can be carried out by changing the engagement/release state of the multi-disc clutch 30 of No. 4, and since there is only one object to be controlled, the control is easy and the shift shock is good. In this case, the first
Since only the one-way clutch 2 of the clutch means K1 is acting, it is only necessary to engage the multi-disc clutch 10 of the first clutch means K1 in order to apply engine braking.

The fifth forward speed is controlled by the multi-disc clutch 11 of the first clutch means Kl, the second clutch means K2, the multi-disc clutch 30 of the fourth clutch means K4, and the band brake 6l of the third brake means B3 as the locking means to be controlled. and the multi-disc brake 62 are engaged. In other words, for the case of the fourth speed described above, the band brake 6 of the third brake means B3
1 is newly engaged. In this case, neither one-way clutch is engaged. Therefore, the input shaft 4 is connected only to the carrier C of the Ravignault-type planetary gear mechanism 1, and since the first sun gear IS is fixed in this Ravigneau-type planetary gear mechanism, the ring gear R rotates in the positive direction at a higher speed than the input shaft 4. This is then transmitted to the ring gear 3R of the third planetary gear mechanism 3. Further, in the third planetary gear mechanism 3, the sun gear 3S rotates forward at the same speed as the input shaft 4 connected to the carrier C of the Ravigneau planetary gear mechanism 1, and the ring gear 3R rotates forward at a higher speed than the input shaft 4. From, carrier 3
C and the output shaft 5 connected thereto rotate forward at a higher speed than the input shaft 4. That is, in this case, the rotation of the human power shaft 4, which has been accelerated by the Ravigneau planetary gear mechanism 1, is decelerated by the third planetary gear mechanism 3 and transmitted to the output shaft 5, and as a result, the gear position is changed to the overdrive gear position. It becomes 5th speed. Therefore, the speed change between the fifth speed and the fourth speed can be achieved by changing the engagement/release state of the band brake 61 of the third brake means B3, so control is easy and the speed change shock is can be made good.

In the reverse gear, the third clutch means K3 and the first brake means B
It is set by engaging the band brake 41 of L and the second brake means B2. That is, in the Ravigneau type planetary gear mechanism 1, the first sun gear 1S is connected to the input shaft 4 and the carrier C is fixed, so that the ring gear R
rotates in the opposite direction, and this is the ring gear 3 of the third planetary gear mechanism 3.
transmitted to R. Further, in the third planetary gear mechanism 3, the sun gear 3S is fixed via the fourth clutch means K4, and the ring gear 3R rotates in reverse in this state, so that the carrier 3C and the output shaft 5 connected thereto are connected to the ring gear. Rotates in reverse at a slower speed than 3R.

2.5th gear ratio value is between 2nd speed and 3rd speed
The speed is controlled by the first clutch means Kl as a locking means to be controlled.
The multi-disc clutch 11 and the multi-disc brake 62 of the third brake means B3 are engaged and set. Accordingly, the one-way clutch 12 of the first clutch means K1, the one-way clutch 31 of the fourth clutch means K4, and the one-way clutch 63 of the third brake means B3 are engaged. That is, the input shaft 4 is connected to the second sun gear 2s of the Ravigneau type planetary gear mechanism 1, and in this state, the input shaft 4 is connected to the second sun gear 2s of the Ravigneau type planetary gear mechanism 1.
Since the sun gear IS is fixed, the carrier C rotates forward at a lower speed than the input shaft 4, and this is transmitted to the sun gear 3S of the third planetary gear mechanism 3, and the ring gear R rotates forward at a lower speed than the input shaft 4.
It rotates forward at a lower speed and faster than carrier C, and this is the third
The signal is transmitted to the ring gear 3R of the planetary gear mechanism 3. As a result, in the third planetary gear mechanism 3, both the sun gear 3S and the ring gear 3R rotate in the forward direction, and since the rotation speed of the sun gear 3S is lower than the rotation speed of the ring gear 3R, the carrier 3C and the output shaft 5 connected thereto rotates forward slightly faster than in the case of the second speed described above. This gear has a gear ratio value between the gear ratios of 2nd and 3rd gears, and is a gear that does not need to be set for steady driving, but is a so-called jump gear. This is an effective gear when executing.

In other words, when shifting between 2nd speed and 5th speed, if the intermediate gear is used, the rotation of the first sun gear IS on the Ravigneau planetary gear mechanism will be reverse rotation,
It changes in a complicated manner from stop, forward rotation, and stop, which is disadvantageous in terms of reducing shift shock and maintaining durability. On the other hand, in the 2.5th gear, the first sun gear IS of the Ravigneau planetary gear mechanism l
remains stopped, and when comparing 2.5 speed and 2nd speed, the difference in the locking means to be controlled is the fourth clutch means K4 and the e-brake means B! Furthermore, when comparing 2.5th gear and 5th gear, the only difference in the locking means to be controlled is that the engine brake is set to work in 2.5th gear. Accordingly, the second clutch means K
Only 2 will be available. Therefore, when performing a jump shift from 2nd speed to 5th speed, the fourth clutch means K
It is only necessary to engage the multi-disc clutch 30 of No. 4 to shift to the 2.5th gear, and then engage the second clutch means K2 to shift to the 5th gear. Fluctuations in the rotation of the first sun gear IS of the gear mechanism 1 are suppressed to a minimum, and the number of retaining means that must change the engagement/disengagement state at one time is reduced, so it is possible to easily shift gears without worsening shift shock. It is possible to perform jump shifting.

Next, another embodiment of the invention will be described. FIG. 4 shows an improved structure of the structure shown in FIG. It is constructed by a multi-disc clutch 20 and a one-way clutch 21, and the one-way clutch 42 in the first brake means B1 is further arranged on the outer peripheral side of the fourth clutch means K4. An example of the operation table is shown in Table 3.

(This page, blank space below) Table 3 Although detailed explanations are omitted, even in the structure shown in Fig. 4, by controlling each engagement means as shown in Table 3, it is possible to move backward in 5 or 6 forward gears. It is possible to set one gear. In addition, in the case of shifting from 3rd gear to 5th gear, if the 3rd gear is set by the combination of engagement and release of each engagement means shown in column b of Table 3 immediately after the shift command is issued, Since the number of retaining means to be switched between engagement and disengagement is minimized, smooth gear shifting can be performed. Furthermore, when performing a jump shift between 1st speed and 5th speed, set 1st speed to the engagement/release combination shown in bm in Table 3 immediately before starting the shift, and from this state If the speed is changed once to 2.5 speed and then to 5th speed, or vice versa, the rotation of the first sun gear IS of the Ravigneau planetary gear mechanism 1 will only change from reverse rotation to a stopped state. Therefore, a jump shift can be easily performed without worsening the shift shock. In the configuration shown in FIG. 4, the state of the engine brake at the first forward speed is determined by engaging either the multi-disc clutch 30 in the fourth clutch means K4 or the band brake 41 in the first brake means B1. This can be achieved by

In the example shown in FIG. 5, the fourth clutch means K4 of the configuration shown in FIG. 50 and a one-way clutch 51 disposed between the carrier C and the case 6. An example of the operation table is shown in Table 4.

Table 4 Note that in the configuration shown in FIG. 5, the state of the engine brake in the first speed is determined by the fourth clutch means K4, the band brake 4l of the first brake means B1, and the multi-disc brake 50 of the second brake means B2. This can be achieved by engaging at least two of the following. Also the third
When shifting between 5th and 5th gears, the gear must go through the engagement release state in column b in Table 4 in order to shift smoothly. Instead of the state in column a, it is also possible to temporarily set the third speed to the disengaged state as in column b of the third speed in Table 3 mentioned above. Furthermore, in the configuration shown in FIG. 5, the fourth clutch means K4 can be engaged in the state of the first working speed. It is preferable to go through the 25th forward speed. In other words, the fourth clutch means K4 is engaged in any of the first gear, 2.5th gear, and 5th gear.
By passing through the 2nd and 5th speeds, the number of retaining means that must be controlled to change the engagement and release state during each shift of 1st speed, 2nd speed, 5th speed, and 5th speed is minimized, and at the same time The rotation of the first sun gear 1S of the Ravigneau planetary gear mechanism 1 does not change in a complicated manner, and therefore, smooth gear changes are possible.

In the example shown in FIG. 6, the second brake means B2 of the configuration shown in FIG. 5 described above is replaced with a single one-way clutch. An example of the operation table is shown in Table 5.

(This page, blank space below) Table 5 In the structure shown in FIG. 6, the reverse gear is set by the multi-plate clutch 20 of the third clutch means K3, the fourth clutch means K4, and the band brake 41 of the first brake means B1. In this case, the carrier C of the Ravigneau type planetary gear mechanism is fixed by the band brake 41 via the fourth clutch means K4, so a large torque is applied to the fourth clutch means K4. Therefore, in order to reduce the size and improve the durability of the fourth clutch means K4, it is preferable to suppress the input torque to the gear train as low as possible in the reverse gear. Further, when performing a jump shift between the second speed and the fifth speed, it is preferable to perform the speed change via the 2.5th speed. In other words, the difference in the locking means to be controlled between 2nd speed and 2.5th speed is as follows:
There is only the fourth clutch means K4. Furthermore, since the difference in the engagement means to be controlled between the 2.5th speed and the 5th speed is the first clutch means K1 and the second clutch means K2, by passing through the 2.5th speed, The number of locking means to be controlled in order to execute the speed change is reduced, and at the same time, the rotation of the first sun gear IS of the Lavigny three-year planetary gear mechanism 1 does not change in a complicated manner. Easy and smooth gear shifting is possible.

In the example shown in FIG. 7, the fourth clutch means K4 is replaced with a single multi-disc clutch in the configuration shown in FIG. and a one-way clutch 51. An example of the operation table is shown in Table 6.

Table 6 In the configuration shown in FIG. 7, the state of the engine brake in the first speed is determined by the fourth clutch means K4, the band brake 41 of the first brake means Bl, and the multi-disc brake 50 of the second brake means B2. It can be set by engaging any two of them.

Furthermore, in the configuration shown in FIG. 7, since the first brake means Bl and the second brake means B2 are held in the engaged state in the first speed state, it is necessary to also engage the fourth clutch means K4 in addition to these. In the case of performing a jump shift between the gear and the fifth speed, it is preferable to perform the shift from the state of the first working speed via the second and fifth speed. That is, in the 2.5th speed and the 5th speed, the fourth clutch means K4 is engaged, and the only difference in the engaging means to be controlled between the 1st speed and the 2.5th speed is the third brake means B3. Furthermore, the only difference in the engagement means to be controlled between the 2.5th speed and the 5th speed is the second clutch means K2. If the shift is performed between the 2.5th speed and the 5th speed, the number of locking means to be controlled will be reduced, and the first
Since the rotation change of the sun gear IS is simplified, smooth gear changes are possible.

In the example shown in FIG. 8, the second braking means B2 of the structure shown in FIG. 7 described above is replaced with a single one-way clutch, and the other structure is the same as that in FIG. 7. An example of the operation table is shown in Table 7.

Table 7 In the configuration shown in FIG. 8, the reverse gear is controlled by the third clutch means K3, the fourth clutch means K4, and the third clutch means B1.
In this case, the carrier C on the Ravigneau planetary gear mechanism is fixed by the band brake 41 via the fourth clutch means K4. Therefore, in order to downsize the fourth clutch means K4 and improve its durability, it is preferable to suppress the input torque to the gear train as low as possible in the reverse gear. Further, when performing a jump shift between the first speed and the fifth speed, it is preferable to perform the speed change via the second and fifth speeds. In other words, the difference in the locking means to be controlled between the 1st speed and the 2.5th speed is that the third brake means B
3, the multi-disc brake 62 and the band brake 6, and the difference in the engagement means to be controlled between the 2nd and 5th speeds is the first clutch means K1 and the second clutch means K1.
2, the number of locking means to be controlled to execute the gear change is reduced by going through the 2.5th gear,
At the same time, the first sun gear 1 of the Ravigneau type planetary gear mechanism
The rotation of the gear 3 does not change in a complicated manner, therefore, the speed change control is easy and the speed change can be performed smoothly.

The present invention has been described above with reference to six embodiments, but this invention can have other configurations other than those shown in the above embodiments. Of the configurations shown in the figures, either the first brake means Bl or the third brake means B3, or both, may be configured by a single band brake.

In addition, in this invention, the locations where a one-way locking means such as a one-way clutch or band brake for smooth gear shifting is used are not limited to the locations shown in each of the above-mentioned embodiments. The locations where the securing means with unidirectional characteristics can be installed are collectively illustrated. In the following description, locations where a locking means having unidirectional characteristics can be installed will be shown for an example in which a Ravigneau type planetary gear mechanism and a single pinion type planetary gear mechanism are configured as a gear train shown in FIG. 2.

Regarding the shift between the first speed and the second speed, a unidirectional engagement means is provided between the carrier C and the sun gear 3S of the third planetary gear mechanism 3 or between the carrier C and the case 6. It is sufficient to intervene.

Regarding the shift between the 1st speed and the 2.5th speed, unidirectional engagement is established between at least one of the carrier C case 6 and the sun gear 3S of the third planetary gear mechanism 3 and the case 6. All you need to do is provide a means for combining.

Regarding the shift between the first speed and the third speed and the shift between the first speed and the fourth speed, the carrier C and the third planetary gear mechanism 3
A one-way restraining means may be provided either between the carrier C and the sun gear 3S or between the carrier C and the case 6. Regarding the shift between the first speed and the fifth speed, between the second sun gear 2S and the input shaft 4 of the Ravigneau planetary gear mechanism 1, between the carrier C and the case 6, and between the third planetary gear mechanism 3.
A unidirectional engagement means may be provided between the sun gear 3S and the case 6. In this case, there is a shift pattern that requires a so-called multiple shift in which three or more locking means are simultaneously switched to perform a shift.

Regarding the shift between 2nd speed and 2.5th speed, between the first sun gear IS of the Ravigneau planetary gear mechanism 1 and the sun gear 3S of the third planetary gear mechanism 3, or A unidirectional engagement means may be interposed between at least one of the sun gear 3S and the case 6. Second
Regarding the shift between speed and third speed, the first sun gear IS of the Ravigneau type planetary gear mechanism 1 and the third planetary gear mechanism 3
A unidirectional engagement means may be interposed between the first sun gear IS and the case 6, or between the first sun gear IS of the Ravigneau planetary gear mechanism 1 and the case 6. Regarding the shift between 2nd speed and 4th speed, between the first sun gear iS of the Ravigneau 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. A unidirectional engagement means may be interposed in at least one of them. Regarding the shift between the second speed and the fifth speed, between the second sun gear 2S and the input shaft 4 of the Ravigneau planetary gear mechanism 1, the first sun gear 1S and the third
A unidirectional engagement means may be interposed at at least one location between the sun gear 3s of the planetary gear mechanism 3 and between the sun gear 3S of the third planetary gear mechanism 3 and the case 6. In this case as well, there is a shift pattern that requires multiple shifts.

Regarding the shift between the 2nd and 5th speeds and the 3rd speed, the carrier C of the Ravigneau type planetary gear mechanism 1 and the third planetary gear mechanism 3
A unidirectional engagement means may be interposed between the first sun gear IS of the Ravigneau planetary gear mechanism 1 and the case 6. In this case, there is a shift pattern that requires multiple shifts. For shifting between the second, fifth and fourth speeds, a unidirectional engagement means may be interposed between the first sun gear king S on the Ravigneau planetary gear mechanism and the case 6. Regarding the shift between the 2.5th speed and the 5th speed, a unidirectional engagement means may be interposed between the second sun gear 2S and the case 6 of the Ravigneau planetary gear mechanism 1.

Regarding the shift between the third speed and the fourth speed, a unidirectional 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 3rd speed and 5th speed, between the first sun gear 1S and elements other than the case 6 (including the human power shaft 4), the carrier C and the ring gear R or the second sun gear 2S or the 3 between the carrier 3C or ring gear 3R of the planetary gear mechanism 3; between the ring gear R and the second sun gear 2S or carrier C; between the sun gear 3S or ring gear 3R of the third planetary gear mechanism 3; or between the input shaft 4; Between the sun gear 2S and the carrier C or the ring gear R or each element of the third planetary gear mechanism 3 or the input shaft 4; between the sun gear 3S of the third planetary gear mechanism 3 and its carrier 3C or the ring gear 3R; between the third planetary gear If a unidirectional engagement means is provided at least at one location between the carrier 3C of the mechanism 3 and its ring gear 3R or the input shaft 4, or between the ring gear 3R of the third planetary gear mechanism 3 and the input shaft 4. good. Regarding the shift between the third speed and the fifth speed, there is a shift pattern that requires so-called multiple shifts.

Regarding the shift between 4th and 5th speeds, since the entire gear train rotates as a unit in 4th speed, unidirectional engagement is applied to each of the elements of each planetary gear mechanism 1.3. You can set up the means. That is, for the first sun gear IS of the Ravigneau planetary gear mechanism 1, a unidirectional engagement means may be interposed between it and any of the elements other than the case 6 (including the input shaft 4). Regarding the carrier C, the ring gear R or the second sun gear 2S or the carrier 3C of the third planetary gear mechanism 3 or the ring gear 3
A unidirectional engagement means may be interposed between R and R. As for the ring gear R, a unidirectional engagement means may be interposed between it and the second sun gear 2S or carrier C, the sun gear 3S or carrier 3C of the third planetary gear mechanism 3, or the input shaft 4. Regarding the second sun gear 2S, a unidirectional engagement means may be interposed between the carrier C, the ring gear R, each element of the third planetary gear mechanism 3, or the input shaft 4. Between the sun gear 3S of the third planetary gear mechanism 3 and the carrier 3C or ring gear 3R, and between the carrier 3C and the carrier 3C,
Unidirectional engagement means may be interposed between the ring gear 3R or the input shaft 4, and further between the ring gear 3R and the input shaft 4.

Note that when replacing the Ravigneaux-type planetary gear mechanism with a configuration that combines a single-pinion type planetary gear mechanism and a double-pinion type planetary gear mechanism, the position where the one-way restraining engagement means can be placed will change as the number of components increases. will increase.

In addition, the method of using the unidirectional engagement means is as described in the specifications and drawings attached to the patent application No. 176270/1982 and Japanese Patent Application No. 221670/1983 filed by the present applicant. can be adopted.

Effects of the Invention As explained above, according to the present invention, a Ravigneau-type planetary gear mechanism and a single-binion type planetary gear mechanism are combined, or the Ravigneau-type planetary gear mechanism is combined with a single-binion-type planetary gear mechanism and a double-pinion type planetary gear mechanism. In a gear transmission that replaces a planetary gear mechanism, a locking means with one-way characteristics such as a one-way clutch is interposed at a position where it functions effectively during gear shifting, so the number of locking means to be controlled during gear shifting is reduced. In addition, it is possible to improve the shift characteristics by reducing shift shock. Further, in the gear transmission of the present invention, the second speed and the third speed are set in the forward gear.
It is possible to set a so-called 2.5th speed, which is a speed change ratio between the above speeds, and by passing through this 2.5th speed, a so-called jump shift can be performed smoothly.

[Brief explanation of drawings]

FIG. 1 is a skeleton diagram showing a first embodiment of the present invention;
Fig. 2 is a skeleton diagram of an example of a basic gear train targeted by this invention, Fig. 3 is a skeleton diagram of another basic gear train, and Figs. 4 to 8 are skeleton diagrams showing other embodiments of this invention. , FIG. 9 is a skeleton diagram showing an example of a conventional gear transmission. 1, 3...Planetary gear mechanism, IS, 2S, 3S...
Sun gear, C, 3C...Carrier, R, 3R...
・Ring gear, 4...Input shaft, 5...Output shaft,
1, K2, K3, K4...clutch means, Bl,
B2, B3... Brake means, 12, 21, 31.
42.63...One-way clutch. K

Claims (1)

[Claims] A single pinion type first planetary gear mechanism and a double pinion type second planetary gear mechanism in which ring gears and carriers are connected and integrated, or the first planetary gear mechanism and the second planetary gear. a Ravigneau type planetary gear mechanism substantially equivalent to the mechanism, and a single pinion type third planetary gear mechanism, and the ring gear of the connected and integrated ring gear or the ring gear of the Ravigneau type planetary gear mechanism and the ring gear of the third planetary gear mechanism. are capable of transmitting power, the carrier of the connected and integrated carrier or the carrier of the Ravigneau type planetary gear mechanism and the sun gear of the third planetary gear mechanism are connected via a clutch means, and the sun gear of the third planetary gear mechanism is a brake means for selectively fixing the carrier; a brake means for selectively fixing the carrier of the connected and integrated carrier or the carrier of the Ravigneau type planetary gear mechanism;
A braking means is provided for selectively fixing the sun gear of the planetary gear mechanism or one sun gear of the Lavigneaux-type planetary gear mechanism corresponding thereto, and further includes a brake means for selectively fixing the sun gear of the first planetary gear mechanism and the second planetary gear mechanism or the sun gear of the Ravigneau type planetary gear mechanism corresponding thereto. The two sun gears of the Ravignault-type planetary gear mechanism and the carrier integrated with the carrier or the carrier of the Ravignault-type planetary gear mechanism are selectively connected to the input shaft by a clutch means, and the carrier of the third planetary gear mechanism and the output shaft are selectively connected to the input shaft. and a clutch means for selectively coupling the sun gear of the first planetary gear mechanism or one of the sun gears of the Ravigneau type planetary gear mechanism and the input shaft, and the gear transmission device for an automatic transmission capable of transmitting power; a clutch means for selectively coupling the sun gear of the second planetary gear mechanism or the other sun gear of the Ravigneaux-type planetary gear mechanism with the input shaft, and the sun gear of the first planetary gear mechanism or one sun gear of the Ravigneaux-type planetary gear mechanism a brake means for selectively fixing the carrier, a brake means for selectively fixing the carrier of the connected and integrated carrier or the carrier of the Ravigneau type planetary gear mechanism, and a brake means for selectively fixing the sun gear of the third planetary gear mechanism; A gear transmission for an automatic transmission, characterized in that either one of the gears includes a unidirectional engagement means whose torque transmission capacity differs depending on the direction of torque action.