JPH0374658A - Gear shifter for automatic transmission - Google Patents

Abstract

PURPOSE:To simplify structure and to facilitate control by providing three sets of single pinion type planetary gear mechanisms and the low number of engaging means. CONSTITUTION:A ring gear 1R of a first planetary gear mechanism and a carrier 2C of a second planetary gear mechanism are formed integrally with each other through an engaging means or individually or a carrier 1C of the first planetary gear mechanism and a ring gear 3R of a third planetary gear mechanism are formed integrally with each other through an engaging means or individually, a sun gear 1S of the first planetary gear mechanism and the carrier 3R of the third planetary gear mechanism are formed integrally with each other through an engaging means or individually, and a sun gear 2S of a second planetary gear mechanism and a sun gear 3S of the third planetary gear mechanism are formed integrally with each other or individually to form an input element, an output element, or a stationary element in each of above cases. An independent element, e.g. a ring gear 2R of the secondary planetary gear mechanism, forms an input element, an output element, or a stationary element.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application This invention relates to a gear transmission used in an automatic transmission for a vehicle, and in particular to a gear train consisting of three sets of single pinion type 11-regular II [mechanism as main body]. ft4 threatening teeth, I
This relates to an I transmission.

As is well known in the art, a planetary gear mechanism has three elements: a sun gear, a ring gear, and a carrier that holds a pinion gear that meshes with these elements.One of these elements is used as an input element, and one of the other elements is output. ! ! East and further speed up the input rotation by fixing other remaining elements,
Alternatively, it is possible to perform forward rotation deceleration or reverse deceleration and output. Therefore, conventionally, a plurality of planetary gear mechanisms are generally combined to form a gear transmission for an automatic transmission. In that case, how to combine the planetary gears** and the gear ratio of the planetary gear mechanism (the ratio of the number of teeth between the sun gear and the ring gear)
ring, and even a single-binion type Yuri! III1m
The gear ratios that can be obtained vary depending on whether an L structure or a double pinion type free tooth skewer mechanism is used, but not all combinations are practical, and it is difficult to install them on a vehicle or manufacture them. Gear trains that can be put to practical use are limited by various conditions such as performance, speed change characteristics, and required power performance. In other words, gear trains can be configured in a huge number of ways depending on the combination of planetary gear mechanisms and how to set gear ratios, so they meet the various conditions required for automatic transmissions for vehicles. Creating one involves great difficulties.

Conventionally, a large number of gear transmissions 111t devised against this background have been proposed, among which three sets of lI star teeth I
@ placement using the Im structure is, for example, published in JP-A-60-8825.
Publication No. 2, Publication No. 51-48062, Publication No. 54-132
It is described in the 058M publication.

Invention will solve the problem! ! The gear transmission VT position described in the above-mentioned Japanese Patent Application Publication No. 60-88252 has three sets of single pinion type planetary teeth 1! It is constructed so that five forward gears and one rear gear for 1 m can be set by combining mechanisms. However, in this gear shifting system, in order to prevent a significant drop in the vehicle's driving force before and after shifting, the gear ratio of each planetary tooth II mechanism is set so that the gear ratio of each gear is close to a geometric series. , it is necessary to set the gear ratio of any of the 11 radial teeth 1IIRII4 to an extremely large value, which results in the inconvenience that the outer diameter of the i-star gear mechanism increases, and conversely, the outer diameter of each planetary gear mechanism increases. If the gear ratio is set to such an extent that the outer diameter dimension does not particularly increase, there is a problem in that the gear ratio of each gear stage does not have a relationship close to that of a geometric series, resulting in a disadvantage that the power performance of the vehicle deteriorates.

Also, Il[
The 1III transmission is configured by combining two sets of single pinion type planetary gear mechanisms and one set of double pinion type planetary gear mechanisms so as to be able to set five forward speeds and two reverse speeds. However, with this gear shift @ position, #1M! When changing gears between first and second speeds and between second and third speeds, a total of four engaging means, two clutch means and two brake means, are engaged. It is necessary to change the engagement and release states, which causes problems such as worsening shift shock or requiring complicated shift control.

Furthermore, the gear transmission described in the above-mentioned Japanese Patent Application Laid-Open No. 54-132058 has a Rapini 1 O type planetary gear mechanism and a single pinion all planetary gear m structure, or two sets of single pinion type. Layer W tooth 11 mechanism and a set of double pinion type parts! In combination with a gear mechanism, it is configured to be able to set five forward speeds and one reverse speed. However, in this gear transmission, a large load torque is applied to each sun gear with a free play of 1111111 m in the first and second forward speeds and in the reverse gear, which is disadvantageous in terms of strength and durability. Circulation occurs, which is disadvantageous in terms of strength and durability, as well as deterioration in power transmission efficiency. Furthermore, if three brake means are required and the number is reduced to two to simplify the configuration, the load torque of a given clutch means will increase and its durability will decrease, or the clutch means There were problems such as the need to increase the torque transmission capacity of the engine and the need for a double-binion type planetary gear mechanism.

The present invention was made against the background of the above-mentioned circumstances, and provides a gear transmission device which is capable of simplifying the configuration by reducing the number of retaining means required for shifting, and at the same time making control easier. The purpose is to provide

Means for Solving Problems In order to achieve the above object, the present invention provides three sets of single pinion planetary gears each having a sun gear, a ring gear, and a carrier holding a pinion gear that meshes with the sun gear and the ring gear. The ring gear of the first planetary gear mechanism and the carrier of the first planetary gear mechanism are constantly connected or selectively connected via an engagement means, and the first play! ! Gear mechanism carrier and third
．． [The ring gear of the star gear mechanism is always connected or selectively connected via an engagement means, and the sun gear of the first planetary gear mechanism and the carrier of the third planetary tooth 1siii structure are always connected or connected with a retaining means. The sun gear of the second planetary gear mechanism and the sun gear of the third planetary gear mechanism are connected at all times or selectively through an engagement means. It is.

Operation In the device of the present invention, the ring gear of the first planetary gear mechanism and the carrier of the 21st planetary gear mechanism are integrated with each other or separately, and the carrier of the first planetary gear mechanism and the ring gear of the third planetary gear mechanism are integrated with each other or separately, and the sun gear of the first planetary gear mechanism and the carrier of the third planetary gear mechanism are integrated with each other or separately, and the sun gear of the second planetary tooth arrangement and the third planet The sun gears of the gear mechanism are integrally or individually used as input elements, output elements, or fixed elements, respectively, and independent elements such as the ring gear of the second play mechanism are also used as input elements, output elements, or fixed elements. It is considered a fixed element. As a result, 1 each! The star gear mechanisms work together or individually to increase/decelerate the rotation of the input shaft, and transmit the rotation of the input shaft to the output shaft either unchanged or reversed.

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

FIG. 1 is a schematic diagram showing the principle of an embodiment of the present invention, and the gear transmission shown here has first to third I
ll Gear mechanism 1, 2.3 is single binion type *Ua*
Each of the main parts 71 in each of these play structures 1.about.2.3 is connected in the following manner. That is, each planetary gear mechanism 1.2.3 is a sun gear 1S.

2, S, 3S, ring gears 1R, 2R, 3R arranged concentrically with sun gears 18, 28.33, these sun gears 1s, 23.38, and ring gears IR, 2R.
, a carrier IC that holds a pinion gear that meshes with 3R.
, 2C, and 3C as main elements. When the ring gear 1R of the first planetary gear mechanism 1 and the carrier 2Cε of the second planetary gear mechanism 2 are connected to rotate together, the carrier 1C of the first planetary gear mechanism 1
And 311th village I! The ring gears 3R of the first planetary gear mechanism 3 are connected to rotate together, and the sun gear 1S of the first planetary gear mechanism 1 and the carrier 3Cε of the third planetary gear mechanism 3 are connected to rotate together. There is. On the other hand, the sun gear 2S of the second planetary gear mechanism 2 and the sun gear 33 of the third planetary gear mechanism 3. ! 4 is provided in the fourth clutch means between : so that these sun gears 2s and 3s are selectively connected to each other. Further, 2 is disposed in the second clutch means between the sun gear 2S of the second planetary gear mechanism 2 and the carrier 3C of the first idler gear mechanism 3, and the second clutch means 2 is connected to the second planetary gear mechanism. 2 sun gear 2S and carrier 3C of the third cruising gear mechanism 3
Selectively, 1! It is designed to be tied.

Note that the connection structure for the above-mentioned elements may be a connection structure used in general automatic transmissions, such as a hollow shaft, a solid ring, or an appropriate connecting drum.

The input shaft 4 is connected to an engine (not shown) via a power transmission means (not shown) such as a torque converter or a fluid coupling. In between, there is a first
A clutch means 1 is provided, and a third clutch means 3 is provided between the input shaft 4 and the sun gear 2S of the second M gear mechanism 2 to selectively connect the two.

1, K2, K3,
The key point of K4 is to selectively connect and release the above-mentioned members, and the K4 is engaged and released by a mechanism conventionally used in the automatic transmission 311I, such as a hydraulic servo mechanism. A wet type multi-disc clutch, a one-way clutch, or a configuration in which these wet-type multi-disc clutches and a one-way clutch are arranged in series or in parallel can be adopted as necessary. In addition, in practical use, since there are restrictions on the arrangement of each component, it is not possible to interpose an appropriate intermediate member such as a connecting drum as a connecting member for each clutch means Kl, 2, 3, and 4. Of course.

The first also connected to each other]! A first braking means B1 that selectively prevents the rotation of the sun gear 1S of the toothed lN mechanism 1 and the carrier 3C of the 3111th gear 11@3 is connected to the carrier 3C and the transformer main shaft 1 case (under JX, simply called the case). 6). Also the 31st
! A second brake means B2 for selectively blocking the rotation of the sun gear 3S of the star ms mechanism 3 is provided between the sun gear 3S and the case 6. These braking means Bl
, 82 can be a wet multi-disc brake, a band brake, or a one-way clutch driven by a hydraulic servo mechanism, which is conventionally used in general automatic transmission, or a combination of these. In addition, in practical use, each point lA to be fixed by these brake means B1 and B2 and these brake means 81 and B2 is
Of course, an appropriate connecting member may be interposed between the sleeves or between the case 6 and the case 6.

The output shaft 5 that transmits rotation to the propeller shaft and the counter gear (not shown) is connected to the carrier 1C of the first planetary gear mechanism 1 and the ring gear 3R of the 331i star tooth skewer mechanism 3, which are connected to each other. has been done.

The gear transmission configured as described above is capable of shifting between 5 front gears and 1 rear gear, or 7 forward gears and 1 reverse gear, and each of these gears is controlled by each clutch means K described above.
l, ni2, ni3, ni4 and brake means 81.
This is accomplished by engaging 82 as shown in Table 1. Table W41 also shows the gear ratio of each gear stage and its specific chain, and the specific chain is the gear ratio ρ1.3 of each planetary gear 11111.2°3. ρ2. ρ3, ρ1
= 0.398, ρ2 = 0.456, ρ3 =
This is the value when it is set to 0.365. Further, in Table 1, a 0 mark indicates an engaged state, and an x mark indicates a released state.

Hereinafter, the case where the transmission is set to 5 forward gears and 31!1 rear gear will be explained first, and then two gears that can be added to these gears will be explained.

(First forward speed) The first clutch means 1 and the fourth clutch means 4 and the first brake means B1 are engaged.

That is, when the ring gear 2R of the Wj2 planetary gear mechanism 112 is connected to the input shaft 4, the sun gear 2S of the 2111th gear 11@2 and the sun gear 3S of the third planetary gear mechanism 3 are connected to the fourth clutch means by 4, and the sun gear 1S of the first planetary gear mechanism 1 and the third sun gear 1S connected thereto.
1. Fix the carrier 3C of the tooth IIl structure 3. Therefore, in the second planetary gear mechanism 2, the ring gear 2R is connected to the input shaft 4.
By rotating with the carrier 2C, the carrier 2C rotates in the forward direction (rotation in four directions on the input shaft 4, the same applies hereinafter), and the sun gear 2C rotates in the same direction.
S rotates in the opposite direction (rotates in the opposite direction to input shaft 4. The same applies below)
do. As a result, in the first planetary gear mechanism 1, the ring gear 1R is connected to the carrier 2C of the second planetary gear a mechanism 2,
Also, because the sun gear 1S is fixed, the carrier 1C rotates forward at a lower speed than the ring gear 1R, and in the third planetary gear mechanism 3, the sun gear 3S rotates in the 2.1st! I
Since it is connected to the speed gear 2S of the II wheel mechanism 2 and the carrier 3C is fixed, its ring gear 3R
rotates forward. In the end, the carrier 1 of the first planetary gear mechanism 1
The output shaft 5 connected to the ring gear 3R of the carrier 1C and the third freewheel gear mechanism 3 is decelerated relative to the input shaft 4 and rotates in the forward direction together with the carrier 1C and the ring gear 3R. It becomes a large first gear. As shown in Table 1, the gear ratio is expressed as (1+ρ1)+ρ2 (1+ρ3+ρlρ3)/ρ3, and its specific value is 3.285. In this case, no power circulation occurs.

(Second forward speed) The first and second clutch means 1, 2 and the first brake means B1ε are engaged. That is, in the state of the first forward speed, clutch 2 is engaged in the second clutch instead of clutch 4 in the fourth clutch. In this case, the sun gear 2S of the second planetary tooth I mechanism 2 is connected to the sun gear 1S of the first idler V south skewer mechanism 1 and the 312nd ring gear 1N by the second clutch means 2.
However, since the sun gear 1S of the first idling gear mechanism 1 and the carrier 3C of the 311th gear mechanism 3 are fixed by the first brake means B1, the second 2 acts as a brake on the clutch means, and the 7 sun gear 2S of the second planetary gear mechanism 2 is fixed. Therefore, in the first Ifl gear mechanism 2, the ring gear 2R is connected to the input shaft 4 with the sun gear 2S fixed.
Therefore, the carrier 2C is decelerated relative to the input shaft 4 and rotates in the forward direction, which is transmitted to the ring gear 1R of the first planetary gear mechanism 1, and in the first planetary gear mechanism 1, the sun gear 1S is fixed. Since the ring gear 1R rotates slowly in the forward direction, the carrier 1C is decelerated relative to the ring gear 1R and rotates in the forward direction. the result,
The output shaft 5 connected to the carrier 1C of the first planetary gear mechanism 1 is decelerated relative to the input shaft 4 and rotates in the forward direction.
become faster. In this case, since the sun gear 3S of the third planetary gear mechanism 3 is not connected to the sun gear 2S of the second planetary gear mechanism 2 and the case 6, the third planetary gear mechanism 3 does not particularly perform an acceleration/deceleration operation. Therefore, as shown in Table 1, the gear ratio in this case is expressed as (1+ρ<(1+ρ2>), and its specific value is 2.035. In this case as well, no power circulation occurs.

(Third Forward Speed) The first clutch means 1, the third clutch means 3, and the first brake means 81 are engaged. That is, in the state of the second speed, clutch 2 is engaged in the second clutch, and clutch 3 is engaged in the third clutch. Therefore the 11th! The sun gear 1S of the star gear mechanism 1, the carrier 3C of the third planet 1!1111@3, and the sun gear 2S of the second planet l1Il wheel mechanism 2 are in a disconnected state, and similarly the sun gear of the second planetary gear mechanism 2 2S and 3rd m21 tooth 1! The sun gear 3S of the mechanism 3 becomes disconnected. In the second planetary gear mechanism 2, the ring gear 2R and the sun gear 2S rotate together with the input shaft 4, so that the whole unit rotates forward at the same speed as the input shaft 4, and accordingly, the first planetary gear The ring gear IR of the first planetary cart mechanism 1 connected to the carrier 2C of the mechanism 2 rotates forward at the same speed as the input shaft 4. In the 1'M star gear mechanism 1, as in the above case, the sun gear 1
Since S is fixed, when the ring gear IR rotates in the forward direction at the same speed as the input shaft 4, the carrier 1C is decelerated with respect to the input shaft 4 and rotates in the forward direction. It should be noted that the third planetary gear mechanism 3 does not particularly perform an increasing or decelerating operation because its sun gear 3S is not connected to the case 6 and the sun gear 2S of the second II star tooth 1s mechanism 2. Therefore, in this case, it's actually the first game! 1llll
Only the ell mechanism 1 performs a deceleration effect, decelerating the rotation of the input shaft 4 and transmitting it to the output shaft 5.

As shown in Table 1, the gear ratio is expressed as (1+ρ1), and its specific value is 1.398. Also, no power circulation occurs.

(Forward 4th ya> 1, K2, K for the first to fourth clutch means
3. engages at least any three of 4;
And the brake means B1 and B2 are released.

That is, for example, in the third speed state, the first brake means B1
Instead, 2 is engaged with the second clutch means, or 4 is engaged with the fourth clutch means.

In this case, at least three clutch means are engaged, such as engaging the first to thirteenth clutch means 1 to 3, or engaging tAl and the third and fourth clutch means Kl, 3 to 4, etc. When engaged, the entire gear train rotates together with the input shaft 4, and no acceleration/deceleration action occurs, so the gear ratio becomes 1''.For example, the first to third clutch means Kl, By engaging 2 and 3, the driving force from the input shaft 4 can be transmitted to the output shaft 5 without generating power@ring.

(Fifth forward speed) The second and third clutch means 2, 3, and the second brake means B2 are engaged. That is, in the above-mentioned fourth speed state, the first to third clutch hands 8KI~ are engaged at 3, and from that state, the second brake means B2 is engaged in contrast to the first clutch means 1. Therefore, game 3! In gear 11113, sun gear 3S
Since the carrier 3C rotates together with the input shaft 4 in a fixed state, the ring gear 3R is accelerated with respect to the input shaft 4 and rotates in the forward direction. In this case, the 211th! In gear *m structure 2, ring gear 2R is not connected to input shaft 4?
Also, the first game 11!1iIt is on the carrier 2C.
Since the ring gear 1R of Is structure 1 is connected, the first
The planetary gear mechanism 1 and the second planetary gear mechanism 2 do not particularly perform an increasing/decreasing operation. As a result, the rotation of the input shaft 4 is actually increased in speed only by the 3111th gear mechanism 3 and transmitted to the output wheel 5, and the gear ratio is 1/1 as shown in Table 1. It is expressed as (1+ρ3), and its concrete value is 0.733. Also in this case, no power circulation occurs.

(Backwards) Engage the third and fourth clutch means by 3°K4 and the first brake means 81. That is, the sun gear 3S of the third idler gear mechanism 3 and the sun gear 2S of the star tooth skewer mechanism 2 are connected to the input shaft 4, and the carrier 3C of the third planetary gear mechanism 3 and the first planet 111111 structure 1 are connected to the input shaft 4. Fix the sun gear 1S.

In this case, since the carrier 2C of the 231st digital gear mechanism 2 is not connected to the input shaft 4,
As in the case of speed, the second idler gear mechanism 2 and the first planetary gear mechanism 1 are not particularly involved in the speed increase/deceleration action. At the third free tooth $11113, the sun gear 3S rotates together with the input shaft 4 with the carrier 3C fixed, so the ring gear 3R rotates in the opposite direction at a lower speed than the input shaft 4. That is, in this case, the rotation of the input shaft 4 is substantially decelerated and reversed only by the third planetary gear mechanism 3 and transmitted to the output shaft 5, resulting in the reverse gear. The gear ratio in this case is expressed as -1/ρa as shown in Table 1, and its specific value is -2,740. Note that, in this case as well, no circulation of power occurs.

As is clear from the above description of the 11th to 5th gears and the reverse gears, the 11th to 5th gears and the reverse gears have been described above. I
In the gear transmission shown in the figure, when setting 5 forward gears and 1 reverse gear, the gear ratio in the # advanced gear can be in a relationship close to a geometric series, so there is a significant drop in driving force before and after shifting. (The power performance of the vehicle can be made good, and the gear ratio of each lI gear mechanism 1.2゜3 is 0.3
Because you can make a suitable pot of about 6 to 0.46,
Three sets of single pinion type parts without introducing a larger diameter idling gear mechanism! Since the fil1 mechanism can be configured as the main component, the gear transmission 11F can be made compact.

Also, as mentioned in the explanation of each 1119, when shifting to another adjacent gear, one of the engagement means is released,
In addition, since it is only necessary to engage the other engagement means, that is, the shift in the forward gear can be performed by switching between the two engagement means, and therefore the control for shifting is easy.
It is possible to do something that is advantageous for improving gear shift shock when opening. Furthermore, since there is no power circulation, the transmission efficiency of driving force is good, and the relative rotation speed of the pinion gear to the carrier is low, the load torque of each gear and each engagement means is small, and the rotation speed of each gear is low. As a result, a highly durable and compact gear transmission can be achieved. Also, the gear ratio in the overdrive stage is 0.7.
By setting the gear ratio to about 33, it is possible to improve power performance, fuel efficiency, and quietness during high-speed driving, and by setting the gear ratio in reverse gear to about -2,740, sufficient driving force can be ensured. be able to. Since the input shaft 4 and the output shaft 5 can be arranged on the same axis, it is possible to provide a gear transmission suitable for FRl (front engine rear wheel drive vehicle).

In addition, in the configuration shown in FIG. 1, two more gears can be set in addition to the gears mentioned above, and the gear ratios of the two gears are between the second and third gears. and the value between 31st and 4th gear, which is shown in the lower row of Table 1 as 2.519 (2,5th) and 3.5th gear (3rd).
, 5th).

(2nd and 5th forward speed) This gear is a gear that corresponds to the aforementioned 2nd and 3rd forward speed, and the first and fourth clutches are connected to the first clutch means.
4 and the second brake means B2 are engaged with the clutch means. Therefore, the sun gear 3S of the third free tooth *a structure 3
is fixed by the second brake means 82 and the sun gear 2S of the second planetary gear mechanism 2 is fixed by the second brake means B2 via the fourth clutch means 4, and the ring ear of the second planetary gear mechanism 2 is fixed by the second brake means B2. 2R rotates together with the input shaft 4.

Therefore, in the 211111111 mechanism 2, the carrier 2C
rotates forward at a lower speed than the input shaft 4. On the other hand, the first game II! In Il1 mechanism 1, the ring gear 1R is the second play! ! Together with the carrier 2C of the gear mechanism 2, it rotates forward at a lower speed than the input shaft 4, and the carrier 1C is integrally connected to the ring gear 3R of the third idler gear mechanism 3 and the output shaft 5,
And the sun gear 1S is the carrier 3 of the third free tooth I1 mechanism 3.
C, and also because the sun gear 3S of the first planetary gear mechanism 3 is fixed, the first planetary gear mechanism 1
The sun gear 1S rotates forward at a lower speed than the ring gear 1R, and the carrier 1C rotates at a lower speed than the ring gear Hlj sun gear 1S.
Rotates forward at an intermediate speed. Horizontal third planetary gear - mechanism 3
In this case, the ring gear 3R rotates in the forward direction at a lower speed than the input shaft 4, and the carrier 3C rotates in the forward direction at an even lower speed than the input shaft 4. After all, in this case, the first to third games! ! 111111 structure 1
, 2 and 3 work together to perform a deceleration effect, thereby decelerating the rotation of the input shaft 4 and transmitting it to the output shaft 5. As shown in Table 1, the ratio of the gear ratio is expressed as (1+ρ1)(1+ρ3+ρlρG)/(1+ρ3), and its specific value is 1.611.

<i-road 3.5th speed) This gear position corresponds to the aforementioned third forward speed and fourth forward speed, and the first and third clutch means K
3 and the second brake means B2 are engaged. That is, the ring gear 2R and sun gear 2S of the second planetary gear mechanism 2 are connected to the input shaft 4, and the sun gear 3S of the third planetary gear mechanism 3 is fixed. Therefore, since the two elements of the second idler gear mechanism 2 rotate together with the input shaft 4, the whole unit rotates forward at the same speed as the input shaft 4, and accordingly, the ring gear 1R of the first planetary gear mechanism 1 rotates forward at the same speed as the input shaft 4. Also, the first planetary gear mechanism 1 and the third! second star tooth r! The connection and fixed state of each element of the i-mechanism 3 is the same as in the case of the 2.5 forward speed described above, and therefore the first planetary gear III mechanism 1 and the third planetary gear mechanism 3
Each element rotates slightly faster than in the case of the above-mentioned forward 2.5 speed. In other words, this forward speed 3.531i rotates slightly faster than in the case of the above-mentioned forward 2.5 speed. This is a state in which the 2nd, 1!11111 mechanism 2 is in an integrally rotating state with no action, and therefore its gear ratio is (1+ρ3 +ρ1 ρ3)/(1+ρ3) as shown in Table 1.
It is expressed as , and its concrete capacity is 1.106.

By the way, in the embodiment shown in FIG. 1, each planetary gear mechanism 1.
2.3 are arranged in order from the input shaft 4Il, but these arrangements may be arbitrarily changed as long as the connection state of each element is maintained as described above. The second example! It is shown in FIG.

That is, in the example shown in FIG. 2, the second idler gear mechanism 2 is arranged on the input shaft 4 side, followed by the first planetary gear mechanism 1 and the third planetary gear mechanism! 1113 are arranged in sequence, and the first and third clutch means Kl.

3 to the input shaft 4 side from the second planetary tooth 1ill structure 2, and 2 to the other clutch means, 2 to 4, and the brake means 81.
．． 82 is placed on the opposite side of the input shaft 4 across the gear train.

Further, in the example shown in FIG. 3, from the input shaft 4 side, the second planetary gear machine @2, the first M tooth 1! Mechanism 1, No. 312 gear 1 machine 11
3, and the second and fourth clutch means 2, 4, and brake means Bl, B2 are arranged in the order of the first planetary gear mechanism 1 and the 312nd planetary gear mechanism 3, respectively.
It is placed between.

Further, in the example shown in FIG. 4, from the input shaft 4 side, the second planetary gear mechanism 2, the third planetary gear mechanism 3, the first planetary gear mechanism v4
1, and the fourth clutch means 4 and the brake means [31, 32 are arranged between the second planetary gear mechanism 2 and the third planetary gear mechanism 3, and the second clutch means 2 and 2 are arranged in the order of 3rd planetary rain wheel mechanism 3 and 11th! This is arranged between the i-wheel gear mechanism 1 and the gear mechanism 1.

Even if the gear transmission device has the configuration shown in FIGS. 2, 3, and 14, the +RU shown in FIG.
ii transmission, with 5 forward speeds and 1 reverse speed, or 7 forward speeds with the addition of 2.5 forward speeds and 3.5th speeds.
It is possible to set one reverse gear.

Gear transmission with the configuration shown in Figures 1 to 4 above
At IF, in the second forward speed, the first brake means B1
By engaging 2 with the second clutch means, the sun gear 2S of the 2nd M star gear mechanism 2 is fixed.
A load will be applied to the second clutch means 2, but in order to eliminate the load 2 on the second clutch means, it is necessary to You can add . An example is shown in FIG. In the example shown here, a third brake means B3 is additionally installed between the sun gear 2S of the 21st star gear mechanism 2 and the case 6 in the configuration shown in FIG. 1 described above. The working clothes are shown in Table 2. In the following embodiments as well, it is possible to set a gear stage of 5 to 7 forward gears and 1 reverse gear, and in the working clothes listed in Table 2 and thereafter, the forward gears are 2.5 to 7 forward gears. speed (2,
5th) and forward 3.5th gear (3,5th) are shown as additional gears based on the case where 5 forward gears and 1 reverse gear are set. If the configuration is such that one reverse speed is set, the 2.5th forward speed corresponds to the 3rd forward speed, and the 3.5th forward speed corresponds to the 5th forward speed Ii. Furthermore, as is known from Table 2, in the @ position shown in FIG. 5, the second clutch is 2 to the means B and the third brake means B
By engaging or disengaging 3, it is possible to perform a gear change without using 2 for the second clutch means.

(This page, blank spaces below) In the gear transmission with the configuration shown in FIGS. 1 to 5 described above, although the sun gear 2S of the second free tooth III mechanism 2 is connected to the input shaft 4 in the reverse gear, First, in practical terms, only the third planetary gear mechanism 3 performs the deceleration action,
Therefore, in this invention, in the reverse gear, the third play 1f! The sun gear 3S of the single wheel mechanism 3 may be configured to be directly connected to the input shaft 4.

An example of this is shown in FIG. 6. In the example shown here, in the configuration shown in FIG. It is constructed by interposing.

The operating gear of the gear transmission shown in Fig. 6 is as shown in Table 3.
It is possible to set 11 gears, and there is also a second play in reverse gear! ! l! ! Since the rotational speed of the sun gear 2S and the relative rotational speed of the pinion gear with respect to the carrier 2C in the III structure 2 can be reduced, this is advantageous in terms of durability.

(This page, blank spaces below) Table (・1): Engage 1 and at least two others, or engage at least two of 2 and 3, 4, and 5. All you have to do is match it.

($2): Engage at least 5, or 5
Instead of 2. 3 may be engaged with 5, 1 may be engaged with 5, 2 may be engaged with 2, or 3 and 4 may be engaged.

By the way, although the above-mentioned gear transmission uses three sets of planetary gear mechanisms, not all of the planetary gear mechanisms are always involved in torque transmission, and some planetary gear mechanisms simply idle at a predetermined gear stage. It may exist. That is, in each of the configurations shown in FIGS. 1 to 6, the first and third clutch means 1, 3, and the first
When the brake means B1 is engaged to set the third forward speed, the entire second MM gear mechanism 2 rotates as a unit as described above, whereas in the third MM gear vaII43, the carrier 3C is fixed. In this state, the ring gear 3R rotates in the forward direction at a lower speed than the input shaft 4, so the sun gear 3S rotates in the reverse direction. Therefore, the relative rotational speed of the sun gear 2S of the second planetary gear mechanism 2 and the sun gear 3S of the third M-gear mechanism 3, which may be rotated 11 times by the fourth clutch means 4, increases.

As a result, when a multi-disc clutch is used as the fourth clutch means, the relative rotation between the clutch disk and the clutch plate increases, so-called drag loss increases, and at the same time, it becomes disadvantageous in terms of durability. If a one-way clutch is used, the relative rotational speed between the inner race and the seventh outer race will increase in the 311st clutch, which is disadvantageous in terms of durability. Therefore, if 6 is additionally installed in the 6th clutch means as shown in FIGS. 7 to 9, for example, in the third forward speed, the 3I2 Satonan II
The carrier 3C of the n structure 3 and the sun gear 1S of the first planetary gear mechanism 1 are disconnected, and the third M star tooth 1!11411
The sun gear 3S of No. 3 is used as the third and fourth clutch means.
．． The sun gear 2s of the third planetary gear mechanism 3 and the second planetary gear mechanism 2 is connected to the input shaft 4 via the input shaft 4.
3s can be rotated at the same speed. At the same time, the pinion gear carrier 3C in the third planetary gear mechanism 3
The relative rotation speed can be reduced.

That is, in the example shown in FIG. 7, of the configuration shown in FIG. This is an additional installation. The working clothes are shown in Table 4.

(This page, below margin) No. 4 table It's ours. The working clothes are shown in Table 5.

5. Also, the example shown in FIG. 8, out of the configuration shown in FIG. In the example shown in FIG. 9 in which the fourth brake means B4 is additionally installed, the sun gear 2 of the second idler Nm wheel mechanism 2 of the configuration shown in FIG.
Sε case 61! : A third brake means 83 is interposed between the sun gear 2S and the rotation of the sun gear 2S. The working clothes are shown in Table 6.

No. Sorrow An example is shown below.

In other words, in the example shown in FIG. 10, the configuration shown in FIG.
5 is additionally installed in the clutch means to create a third idler tooth van structure 3.
The sun gear 3S is directly connected to the input shaft 4. The working clothes are shown in Table 7.

(This page, hereafter in the margin) (Umbrella 1): Any two or more of these three may be engaged.

Furthermore, in the present invention, the example shown in Table 7 and FIG. Additional installation or 9th! A fourth brake means 84 is additionally installed in the configuration shown in FIG.
The sun gear 2S of li*II@2 and the carrier 3C of the third M star gear mechanism 3 are selectively fixed. The working clothes are shown in Table 8.

(This page, margin below) 8EIX is 0 good.

The gear transmission having the configuration shown in FIG. 11 described above can have other configurations by changing the arrangement of its constituent elements, an example of which is shown in FIG. 12. That is, in the example shown in FIG. 12, the @211N gear mechanism 2, the third planetary gear* mechanism 3, and the first planetary gear mechanism 1 are arranged in this order from the input shaft 4 side, and accordingly, the sixth clutch means is 1 disposed on the outer peripheral side of the planetary gear mechanism 1, and at least the second and fourth clutch means are provided with 2°K4 and a second brake hand PiB2.
lI1 mechanism 2 and 3rd game! ! This configuration is arranged between the gear mechanism 3 and the gear mechanism 3. With this configuration, the restriction on the outer diameter of the clutch means is greatly reduced. Of course, the working clothes are no different from those shown in Table 8 above.

Further, another clutch means (temporarily referred to as a ninth clutch means ε) K9 can be additionally provided to the II gear transmission shown in FIG. An example of this is shown in FIG.
9 is interposed between the ring gear 1R of the idling gear mechanism 1 and a ninth clutch means for selectively connecting the two. Table 9 shows the operating gear for the gear shifting arrangement shown in FIG. 13.

9. Since 1 is always engaged with the front contact means, this first
1 may be omitted from the clutch means and the ring gear 2R of the second planetary gear mechanism 2 may be always connected to the input shaft 4.

In the example shown in FIG. 14, a fourth brake means B4 is added 8W1 to II4 shown in FIG. 10 to selectively fix the carrier 3C of the third M* mechanism 3. The working clothes are shown in Table 10.

(This page, below margin) is possible.

As is known from this Table 9, the third brake means B3
The fourth brake means B4 can be omitted depending on how the other clutch means and brake means are engaged and released, or the first brake means can be additionally installed. The 11th work clothes
Shown in the table.

No. 1 table It is possible to determine

The example shown in FIG. 15 has the structure shown in FIG. ! 7 (-) to the seventh clutch means that selectively connects the ring gear 3R of the 1111 mechanism 3 and the output shaft 5 or the carrier 1C of the first planetary gear mechanism 1: engages any two or more of these three. Just let it happen.

The example shown in FIG. 16 has the configuration shown in FIG. 1
8 is additionally installed in the eighth clutch means that selectively connects the carrier 3C of the vehicle mechanism 3. The working clothes are shown in Table 12.

(This page, hereafter in the margin) Table 2 (-2): Any two or more of these three may be engaged.

Here, the combination of engagement and disengagement of each clutch means and brake means for setting each gear stage is referred to as the 17th combination.
They are summarized in the figure. In FIG. 17, the 0 mark indicates engagement, the blank space indicates release, and the * mark indicates engagement.

Furthermore, FIG. 17 was created as an operating garment for the gear transmission having the configuration shown in FIGS. 11 and 12 described above.

As can be seen from FIG. 17, the first brake means B
The first and third brake means 83 and the fourth brake means B4 can be released at any gear stage depending on the combination of engagement and release of the other clutch means and brake means. Any one or two of the means 81, 33, 34 can be omitted. Further, 6 can be always engaged in the sixth clutch means depending on the engagement/release method of other clutch means or brake means. Therefore, 6 can be omitted in the sixth clutch means and the 112th star gear mechanism 1 It is also possible to employ an @kai in which the sun gear 1S and the carrier 3C of the third planetary gear mechanism 3 are always connected. Further, the same applies to the first clutch means 1, and it is also possible to eliminate this and have a configuration in which the ring gear 2R of the second planetary gear mechanism 2 is always connected to the input shaft 4. As described above, various modifications of the present invention can be easily inferred from FIG. 17.

By the way, in each of the embodiments described above, each clutch means has one to
9 and each of the pre-key means B1 to B4 are shown with the symbol of a multi-disc clutch or a multi-disc brake, but in this invention, in order to facilitate control for shifting and to alleviate shift shock, clutch means are used. Alternatively, an engaging means having unidirectional characteristics can be used as the brake means. Here, the engagement means having one-way characteristics includes a well-known one-way clutch equipped with a transfer element such as a sprag, a band brake whose torque capacity differs depending on the direction in which a load is applied, and the like.
By using this type of unidirectional engagement means alone or in combination with a multi-disc clutch or multi-disc brake, the number of engagement means that must be controlled for engagement/m switching during gear shifting can be reduced. It can be reduced, and the engagement and
Shift shock is improved because the release state is automatically switched. In order to produce such an effect, the elements connected to each other by the unidirectional engagement means must rotate at the same rate (including in a stopped state) just before shifting, and rotate relative to each other after shifting; It is necessary that the acting element takes part in the torque transmission before shifting.

In addition, the unidirectional engagement means is interposed between two elements that are directly connected by the unidirectional engagement means.
It may also be between two elements that are connected via another element that rotates the same way before shifting. The position where the unidirectional engagement means is provided is the clutch means (sixth clutch means 6 Or, the case where the eighth clutch means is provided with 8) is different from the case where the clutch means is not provided, and also for each shift pattern, including so-called jump shifting other than shifting to adjacent gears. They are different, and the positions where the unidirectional engagement means are provided for each will be exemplarily shown below.

First, as shown in FIGS. 1 to 6 and FIG. 15, the sun gear 1S of the first planetary gear mechanism 1 and the carrier 3C of the third planetary gear mechanism 3 are always connected, and a clutch is connected between them. The case where no means are provided is shown below.

1st speed and 2nd I! Regarding the speed change between the two, a one-way engagement means such as a one-way clutch may be interposed between the sun gear 2S of the second planetary tooth T11m12 and the sun gear 3S of the third planetary gear mechanism 3. Regarding the shift between 1st speed and 2.5th speed, the 3'f1 ring gear nII! Between carrier 3C of 43 and case 6 or 112th village 1! i
A unidirectional engagement means may be provided between at least one of the sun gear 1S of the vehicle mechanism 1 and the case 6. 1st
For shifting between speed and 3's, a unidirectional engagement means may be provided between the sun gear 2S of the 2nd M star gear mechanism 2 and the sun gear 3S of the 311th star gear mechanism 4113. good. Regarding the shift between 1st gear and 365th gear, between the sun gear 2S of the second free tooth*m mechanism 2 and the sun gear 3S of the third planetary gear mechanism 3, the carrier 3C of the third planet #ASS mechanism 3 and the case A unidirectional engagement means may be interposed between the sun gear 1S of the first planetary gear mechanism 1 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 1st speed and the 4th speed, the carrier 3C case 6 of the 3M digital gear machine lI43
A unidirectional engagement means may be interposed between at least one of the case 6 and the sun gear 1S of the 111th tooth skewer mechanism 1. Regarding the shift between 1st speed and 5th speed, the sun gear 1S of 21111!1I14f12,! -13 Yusho 61111 Mechanism 3 Sun Gear 3S
between the carrier 3C of the third planetary gear mechanism 3 and the case 6.
between the sun gear 1S of the first idler mechanism 1 and the case 6, and the ring gear 2 of the 211th mile**
A unidirectional engagement means may be interposed at at least one location between R and the input shaft 4. In this case as well, there are shift patterns that require multiple shifts.

Regarding the shift between 2nd speed and 2.5th speed, between the sun gear 2S of the 2nd M planetary gear mechanism 2 and the sun gear 1S of the first planetary gear mechanism 1, or between the sun gear 1S of the 1st planetary gear mechanism 1. A unidirectional engagement means may be interposed between at least one of the case 6 and the case 6. Regarding the shift between the second speed and the third speed, between the sun gear 2S of the second free U-tooth lI mechanism 2 and the sun gear 1S of the first planetary gear mechanism 1, or between the sun gear 2S of the second planetary gear mechanism 2. A unidirectional engagement means may be interposed between at least one of the cases 6ε. Regarding the shift between 2nd speed and 3.5th speed, between the sun gear 2S of the 2nd N planetary gear mechanism 2 and the sun gear 1S of the 1st planetary gear mechanism 1, and between the sun gear 2S of the 2nd planetary gear mechanism 2. A unidirectional engagement means may be interposed between the case 6 and at least one location between the sun gear 1S of the first planetary gear mechanism 1 and the case 6. In this case, there is a shift pattern that requires multiple shifts. Regarding the dark shift between 2nd speed and 4th speed, between the sun gear 2S of the 2nd planetary gear mechanism 2 and the case 6 or the 1st M star 1111i1
A unidirectional engagement means may be interposed between at least one of the sun gear 1S of 11111 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 1S of the first planetary gear mechanism 1 and the case 6, and between the sun gear 1S of the first planetary gear mechanism 1 and the case 6, A unidirectional engagement means may be interposed at at least one location between the ring gear 2R of the free tooth structure 2 and the input shaft 4. In this case as well, there is a shift pattern that requires multiple shifts.

When it comes to shifting between 2.5th and 3rd speeds, it's the 2nd M star! IIIIII! Between the sun gear 2S of I structure 2 and the sun gear 3S of the third planetary tooth skewer III@3, 1212 1!1l
Between the sun gear 2S of fll112 and case 6, the 31st
A unidirectionality securing means may be interposed at at least one location between the sun gear 3S of the No. 11 gear mechanism 3 and the case 6. In this case, there is a shift pattern that requires multiple shifts. Regarding the shift between 2.5th speed and 3.5th speed, between the sun gear 2S of the second planetary gear mechanism 2 and the sun gear 3S of the third planetary tooth q1 mechanism 3 or the second planetary tooth II! A unidirectional engagement means may be interposed in at least one of the sun gear 2S of the II structure 2 and the case 6. Regarding the transmission between the 2.5th gear and the 4th gear, the second idler tooth l [between the sun gear 2S of the mechanism 2 and the case 6ε or between the sun gear 3S of the third planetary gear mechanism 3 and the case 6] A unidirectional engagement means may be interposed between at least one of them. Regarding the shift between the 2.5th speed and the 5th speed, between the sun gear 2S of the second planetary gear mechanism 2 and the sun gear 3s of the third planetary gear mechanism 3, the second planetary gear mechanism 2
between the sun gear 2s and the case 6ε, the second idler gear mechanism 2
A unidirectional engagement means may be interposed at at least one location between the ring gear 2R and the input shaft 4. In this case, there is a shift pattern that requires multiple shifts.

For shifting between 3rd speed and 3.5th speed and between 3rd speed and 4th speed, there is a unidirectional engagement between the sun gear 1S of the first planetary gear mechanism 1 and the case 6. What is necessary is to intervene with a combining means. Regarding the shift between 3rd speed and 531st speed, 2nd! ! Sun gear 2S and second play of Startooth II mechanism 2! ! Carrier 2C or ring gear 2R or first play of gear mechanism 2! Between the ring gear 1R of the 1m wheel mechanism 1,
The input shaft 4 and the carrier 2C or ring gear 2R of the 2121st gear mechanism 2 or the ring gear 1R of the first free tooth *mechanism 1,! :) 15, 111th Ri 111m 11111
f) A unidirectional engagement means may be interposed at at least one location between the case 6 and the case 6. In this case, multiple shifting is also required! ! There is a shift pattern that hits.

During the shift between the 3.5th speed and the 4th speed, a unidirectional engagement means may be interposed between the sun gear 3S of the third planetary south gear mechanism 3 and the case 6. Regarding the dark shift between 3rd, s, 1 and 5th speed, the sun gear 2S of the second idler gear mechanism 2 and the carrier 2C of the second planetary gear mechanism 2 or the ring gear 2R or the first idler gear mechanism 1 ring gear 1R
between the input shaft 4 and the carrier 2C of the second planetary gear mechanism 2.
Alternatively, a unidirectional engagement means may be interposed in at least one of the ring gear 2R and the ring gear 1R of the first idling gear mechanism 1.

Regarding the dark shift between 4th and 5th speeds, the entire gear train rotates as a unit in 4th speed, so each of the three elements of planetary gear II structure 1.2.3. Directional engagement means may be provided. i.e. the second ″f1
For the sun gear 2s of star fa111112, the carrier 2C and ring gear 2R of the second planetary gear * mechanism 2, the sun gear 3S and the ring gear 3 of the third idler mechanism 3
A unidirectional engagement means may be interposed between R, the carrier icJ'j of the first free gear mechanism 1, and the ring gear 1R. Carrier 2C of the second play wmiti Tsukikai 2
In this case, a unidirectional engagement means may be interposed between the ring gear 1R of the first idling gear mechanism 1 and any other element (including the input shaft 4) other than the case 6. Second
Ring gear 2R and 3'111w of planetary gear mechanism 2
[For each sun gear 3S of the llN mechanism 3,
A unidirectional engagement means may be interposed between any other element (including the input shaft 4) ε other than the case 6. Third
Regarding carrier 3C of M Yagashi*a structure 3, the second! i!
! Tooth** structure 2 carrier 2C and ring gear 2R, 3rd play! Sun gear 3S and ring gear 3R of gear mechanism 3
, the carrier and ring gear 1 of the 11i-th ring gear mechanism 1
A unidirectional engagement means may be interposed between R. Regarding the ring gear 3R of the 31st!1 gear mechanism 3, the carrier 1C and the case 6 of the first floating float mechanism 1 are
A unidirectional engagement means may be interposed between the input shaft and any other element (including the input shaft 4) except for the input shaft 4. Regarding the sun gear 1S of the first planetary m skewer mechanism 1, the carrier 2C and the ring gear 2R of the 2111th tooth 11 mechanism 2, the 3111th
Sun gear 3S and ring gear 3R of gear mechanism 3, first
A unidirectional engagement means may be interposed between either the carrier 1C of the free plastic gear mechanism 1 or the ring gear 1R. Regarding the carrier 1C of the first floating float mechanism 1, the third
A unidirectional engagement means may be interposed between the ring gear 3R of the planetary gear mechanism 3 and other elements (including the input shaft 4) other than the case 6. Regarding the ring gear 1R of the first idler gear mechanism 1, the second! A unidirectional engagement means may be interposed between the carrier 2C of the I-shaped gear mechanism 2 and other elements other than the case 6 (including the input shaft 4).

Next, as shown in FIGS. 7 to 13 and 16, a clutch means is provided for selectively connecting the sun gear 1S of the first planetary gear machine 4111 and the carrier 3C of the third planetary gear mechanism 3. Indicates the case where In addition,
In the configuration including such a latch means, the 31st
The carrier 3C of the 21 gear machine 4113 and the sun gear 1S of the first planetary gear mechanism 1 can be selectively connected and uncoupled, and accordingly, the carrier 3C of the third planetary gear mechanism 3 is fixed alone. This is done, and each planet l!
i'f! Sun gear 1S of im structure 1.2.3, 23.38
Since the connection relationship between them can be changed as appropriate, the
Compared to the case where the clutch means is not provided with 6 or the 8th clutch means is not provided with 8, mainly the
between the carrier 3C and the sun gear 1S of the first planetary gear structure 1 and the third planetary gear II! Whether or not a one-way engagement means can be arranged between the carrier 3C of the mechanism 3 and the case 6, and whether or not a one-way engagement means can be interposed between each sun gear 13°23.38. There is a difference in the following points. Therefore, in the following explanation, only the locations that are different from the arrangement positions of the unidirectional engagement means for each shift pattern described above will be explained, and explanations of the same sections will be omitted.

That is, regarding each of the shift between the 1st speed and the 2nd speed and the shift between the 1st speed and the 3rd speed, in addition to the above-mentioned locations, the carrier 3C of the third planetary gear mechanism 3 and the first A unidirectional engagement means may be interposed either between the planetary l1lIK mechanism 1 and the sun gear 1S or between the carrier 3C of the third free tooth iti* mechanism 3 and the case 6. In addition to the above-mentioned locations, between the shift with the fourth gear and the shift between the first and fifth gear,
Planet Tooth II! Carrier 3C of mechanism 3 and first planet 1111
A unidirectional engagement means may be interposed between the sun gear 1S of the mechanism 1 and the sun gear 1S.

The 21st shift between 2nd gear and 2nd gear! Regarding the shift between and fifth speed, a unidirectional engagement means may be interposed between the sun gear 2S of the second planetary gear mechanism 2 and the sun gear 1S of the first idler gear 1@1.

Regarding the shift between the 4th speed and the 2.5th speed, the sun gear 2S of the second planetary gear set 4112 and the 31st gear [
A unidirectionality ensuring means may be interposed between the H.111 mechanism 3 and the sun gear 3S.

Furthermore, regarding the shift between the 4th speed and the 5th speed, in addition to the above-mentioned locations, the 21st helical gear [between the sun gear 2S of the mechanism 2 and the sun gear 1S of the A unidirectional engagement means is interposed between the carrier 3C of the mechanism 3 and the sun gear 1S of the first planetary gear mechanism 1, or between the sun gear 1S of the first planetary gear mechanism 1 and the input shaft 4. Good too.

As mentioned above, the unidirectional engagement means for performing smooth gear shifting can be set at various locations as needed, but it is important to note that the unidirectional engagement means can be set at various locations as necessary, but it is important to note that the unidirectional engagement means can be set at various locations as necessary. When using a unidirectional engagement means for shifting to an adjacent gear, the connection between the sun gear 2S of the 211st gear mechanism 2 and the sun gear 3S of the third planetary gear mechanism 3, and the sun gear 3S of the 21st helical gear mechanism 2 Sun gear 2S and sun gear 1S of the first planetary gear mechanism 1
Between or the second loose tooth l! Either one between the sun gear 2S of the mechanism 2 and the case 6, between the sun gear 1S of the first planetary gear mechanism 1 and the case 6, the second M star tooth! Sun gear 2S and 31st of tI mechanism 2! Between star gear 4m@3 and sun gear 3S or ring gear 2 of 2nd M star gear mechanism 2
A unidirectional engagement means may be provided between R and the input shaft 4. This is the same regardless of whether the sixth clutch means 6 or the third clutch means 8 is provided or not.

The method of using the unidirectional engagement means is as described in the specifications and drawings attached to the patent application No. 176270/1983 or the application number 221670/1983 filed by the present applicant. can be adopted.

For example, as shown in FIG. 18, the first clutch means is
A one-way clutch 10 and a multi-disc clutch 11 capable of transmitting torque in the forward rotation direction from the input shaft 4 to the ring gear 2R of the second free tooth 1tii+w structure 2 are arranged in series, and It is possible to have a configuration in which the multi-disc clutches 12 are arranged in parallel. The first clutch means 1 is engaged when shifting between 4th gear and 5th gear, or between 3rd gear and 4th gear, or while maintaining the 4th gear state. Alternatively, in the case of an upshift, the rotation speed of the ring gear 2R of the second free wheel mechanism 2 is the same as or higher than the rotation speed of the input shaft 4, and in the case of a downshift. The opposite is true, so even if the one-way clutch 10 and the multi-disc clutch 11 in series are engaged, and the other multi-disc clutch 12 in parallel with these remains disengaged, the one-way clutch 10 is During a simple shift between the third and fourth speeds, the held state can be maintained, and during a shift between the fourth and fifth speeds, the gear can be engaged or disengaged to execute each shift. In addition, the 21st
1! Since the ring gear 2R of the P gear mechanism 2 rotates in reverse in reverse gear, a multi-plate clutch 11 is arranged in series with the one-way clutch 10.

Further, the fourth clutch means 4 is shown in FIG. 19(A).

As shown in (8), the third game! Sun gear 3 of gear mechanism 3
One-way clutch 20 that engages when S is about to rotate forward relative to sun gear 2 of second planetary gear mechanism 2
A configuration (first
9(A), or the one-way clutch 20 is obtained by omitting the multi-disc clutch 21 from the configuration shown in FIG. 19(A).
and a multi-disc clutch 22 arranged in parallel (FIG. 19(B)). Here, one-way clutch 2
The reason why the multi-plate clutch 21 is provided in series with 0 is that depending on how the third forward speed is set, the sun gear 3S of the 3rd:11th gear mechanism 3 can be moved to the second idler! This is because the sun gear 2S of the single-wheel mechanism 2 needs to rotate forward at a higher speed, and the reason why the multi-plate clutch 21 is omitted and the structure shown in FIG. Depending on how you set it up, the third
This is because the sun gear 3S of the M-gear mechanism 3 does not rotate at a higher speed than the sun gear 2S of the second planetary gear mechanism 2. And the fourth clutch means 4 is, as mentioned above,
When changing gears between 1st and 2nd forward speed or 4th forward speed
The engaged/disengaged state is switched between speed and fifth speed.

6 in the sixth clutch means, as shown in FIG.
Play It! 1111! It is constructed by arranging in parallel a one-way clutch 30 and a multi-disc clutch 31 that are engaged when the sun gear 1S of the 1111 is about to rotate forward relative to the carrier 3C of the third planetary gear mechanism 3. be able to. 6th
As mentioned above, the clutch means 6 acts together with the first brake means 81 in the first forward speed to prevent reverse rotation of the carrier 3C of the third planetary gear mechanism 3, but when moving from that state to the second speed. Since the carrier 3C rotates forward during a shift, the one-way clutch 30 is automatically disengaged and an upshift can be performed.

As shown in FIG. 21, the first brake means B1 includes a first
Play! A one-way clutch 40 that is engaged when the sun gear 1 of the 1-meter car mechanism 1 is about to rotate in the opposite direction with respect to the case 6, and a multi-disc brake or band brake (hereinafter referred to simply as a brake) arranged in parallel with the one-way clutch 40. ) 41. The 1st to 3rd speeds prevent reverse rotation of the sun gear 1S of the first planetary gear mechanism 1. Also, since the 4th and 5th speeds rotate the sun gear 1S of the first planetary tooth I1 mechanism 1 in the forward direction, the I! can be performed by the one-way clutch 40.

The second brake means B2 includes a third brake means B2, as shown in FIG.
A one-way clutch 50 and a brake 51 that are engaged when the sun gear 3S of the Yuuriminami mechanism 3 is about to reversely rotate with respect to the case 6 are arranged in series, and another brake 52 is arranged in parallel with these. It can be set as llI. That is, as is known from each of the above-mentioned sides, when the third clutch means is released from 3 to set the second forward speed,
If the sun gear 3S of the third planetary tooth rf1 mechanism 3 is prevented from rotating backwards and shifted from this state to the third speed, the sun gear 3S of the third planetary tooth 118m@3 will start to rotate forward, and therefore the one-way clutch Even if the brake 51 in series with the brake 50 is maintained in the engaged state, the sun gear 3
Depending on the direction of the torque applied to S, the one-way clutch 50 can be automatically released to perform an upshift from second to third speed, and conversely, the one-way clutch 50 can be automatically engaged. A downshift from 3rd gear to 2nd gear can be performed.

As shown in FIG. 23, the fourth brake means B4 includes a third
A one-way clutch 60 and a brake 61, which are engaged when the carrier 3C of the M tooth 1 [11@3 is about to rotate in a reverse direction with respect to the case 6, are arranged in parallel. The carrier 3C of the 3'iI zone sub-mechanism 3 moves forward to the first position.
When the carrier 3C is not fixed to the sixth clutch means 6 and the first brake means B1, it is fixed by the fourth brake means B4. Therefore, in the configuration shown in FIG. 23, shifting between the first speed and the second speed can be performed by operating the one-way clutch 60.

In addition, on each side shown in FIGS. 18 to 23 above,
A multi-plate clutch or braking means is provided in parallel with the one-way clutch ε, and this is to apply engine braking. Further, the fourth clutch means 4, the sixth clutch means 6, and the multi-disc clutches or brakes in the first brake means B1 and fourth brake means B4 are also engaged in the reverse gear. A modified example in which improvements are made to the latching means and braking means will be shown below.

In the example shown in FIG. 24, of the configuration shown in FIG. 4 described above, 2 is arranged in the second clutch means in parallel to the one-way clutch 70 and the multi-disc clutch 71 arranged in series, and the combination thereof. I! by 31 with another multi-disc clutch 72! 1! Further, the fourth clutch means 4 was constructed as shown in FIG. 19(B), the first brake means B1 was constructed as shown in FIG. 21, and the second brake means B2 was constructed as a band brake. It is something. Table 13 shows an example of an operation table for the gear transmission having the configuration shown in FIG. In addition, in the operation table below, the 0 mark indicates the engaged state and the × mark indicates the disengaged state, which is the same as the above operation table. In addition, in the operation table below, the ◎ mark indicates the engine Indicates that the brake is engaged during braking.

Furthermore, in the gear column, a, b, c, etc. are displayed to indicate other combinations of engagement and disengagement to set the gear. The combination of engagement and release may be changed in this order, or any combination of engagement and release may be selected.

(This page, hereafter in the margin) Table 13 A third brake means 83 consisting of a rake is provided. An example of the operation table is shown in Table 14.

In the example shown in Table 14 and FIG. 25, the second clutch means 2 of the configuration shown in FIG. The example shown in FIG. 26 of selectively fixing pan doves is the configuration shown in FIG. The fifth brake means B5 are arranged in parallel.

An example of the operation table is shown in Table 15.

Table 15 The embodiments shown in FIGS. 24 to 26 described above are shown in Table 6.
Since the clutch means is not equipped with 6, as described above, the relative rotational speed between the sun gear 3S of the third idler gear mechanism 3 and the sun gear 2S of the second planetary gear mechanism 2, that is, the fourth clutch means 4 is The relative rotation speed between the inner race and the outer race of the one-way clutch 20 increases, which is disadvantageous in terms of durability. In order to eliminate such inconveniences, it is effective to use 6 for the sixth clutch means, but in that case, as explained with reference to FIGS. 18 to 23, the first clutch means 1, 4 in the fourth clutch means, 6 in the sixth clutch means, the first brake means B1 and the fourth brake means 84, and furthermore, if these and the second brake means B2 are configured to include one-way clutches, one-way clutches can be used. It is possible to change gears by applying a clutch, and in particular, when the fourth clutch means is set to 4, and the sixth clutch means is set to either 6 or the fourth brake hand 11B4,
the first brake means 81, or either the first clutch means 1 or the fourth clutch means 4; the sixth clutch means 6 or the fourth brake means 84; 1 brake means B1;
If at least the enclosure with the second brake means B2 is improved to include a one-way clutch as shown in FIGS. This can be achieved by applying a target clutch, thus providing good shift controllability and being advantageous in reducing shift shock.

An example is shown below.

That is, in the example shown in FIG. 27, among the configurations shown in FIG. 12 described above, 4 is used as the fourth clutch means as shown in FIG.
The structure shown in the figure is adopted, and the first brake means B1 is replaced by a second brake means B1.
The configuration is shown in FIG. Its operation table is number 16
As shown in the table, as is clear from this table, in the case of a configuration that sets the basic gears of 5 forward gears and 1 reverse gear,
Shifting of the forward gear can be achieved by manually controlling one locking means.

In the example shown in Table 16 and FIG. 28, of the configuration shown in FIG. 27 above, 6 is a single multi-disc clutch for the sixth clutch means, and the fourth brake means B4 is configured as shown in FIG. 23. This is what I did. The operation table is shown in Table 17.

Table 17 In the configurations shown in FIGS. 27 and 28, in addition to being able to perform gear shifting in m-advanced gears using a one-way clutch, the 31st! Reduce the relative rotational speed of the sun gear 28.33 between the second planetary gear mechanism 2 and the II3 planetary gear mechanism 3 at be able to.

In the example shown in FIG. 29, the fourth clutch means 4 in the configuration shown in FIG. 27 is replaced with the configuration shown in FIG. The configuration has been changed. The operation table is shown in Table 18, and in this @kai also there is only one locking means that is artificially controlled when shifting in the forward gear.

(This page, below margin) Table 18 The means B4 has the configuration shown in FIG. 23.

The working clothes are shown in Table 19.

In the example shown in Table 19, and in FIG. In the configuration shown in FIG. 30, in addition to being able to perform a shift in the forward gear by operating a one-way clutch, the sun gear 2s of the second planetary gear mechanism 2 and the third planetary gear mechanism 3 is activated in the second and third gears. , the relative rotation speed of 3s can be eliminated,
Further, the relative rotational speed of the pinion gear to the carrier 3C in the third Mirisi* mechanism 3 at the second speed and the third speed can be reduced.

In the example shown in FIG. 31, the one-way clutch 40 in the first brake means B1 is disposed on the inner circumferential side of the carrier 3C of the third planetary gear mechanism 3 in the aforementioned FIG. 24, and its inner race is integrated with the case 6. Attach it to the designated fixed part of the
In addition, the outer race is connected to the carrier 3C and the multi-disc brake 41, and the other configurations are the same as the configuration shown in FIG. 24. Therefore, in the example shown in FIG. 31, the arrangement of the components of the gear transmission shown in FIG. 24 is changed, so that its working clothes are the same as those in Table 13 mentioned above.

In the example shown in FIG. 32, the fifth brake means B5 consisting of a one-way clutch 80 and a multi-disc brake 81 arranged in series is connected to the second M zone of II4 shown in FIG.
! Provided between the sun gear 2S of the single-wheel mechanism 2 and the case 6,
In other words, the third brake means B3 is removed from the configuration shown in FIG. 26, and the first brake means B1 is replaced with the first brake means B1. This configuration is similar to the configuration shown in FIG. 31. An example of the working clothing is shown in Table 20.

(This page, the following is a margin) 20. It is composed of a one-way clutch 20ε arranged on the front flange, and these multi-plate clutches 22 and one-way clutch 20 are connected to the sun gear 2S of the second M gear mechanism 2 and the third idler M tooth. The first brake means B1 is arranged in parallel with the sun gear 3S of the II mechanism 3, and the first brake means B1 is connected to the band brake 42 and the one-way clutch 4.
0 and II4, and the second brake means B2 is a band brake, and the second clutch means 2 is a multi-plate clutch, and the other parts are the same as in FIG.

An example of the operation table is shown in Table 21.

(This page, hereafter in the margin) The example shown in FIG. 33 is an example in which the sixth clutch means is provided with 6, and is a modification of the configuration shown in FIG. 28 described above, for example. That is, the 14 clutch means 4 is provided with a multi-disc clutch 22 and its inner circumference 1st table B3, and the one-way clutch 40 constituting the first brake hand &181 is of a small diameter, and the other configuration is the 33rd
This is similar to the 41I precept shown in the figure.

An example of the operation table is shown in Table 22.

(This page, the following is a margin) The example shown in FIG. 3
The example shown in FIG. 5 is a further modification of the configuration shown in FIG.
One-way latch F that engages in the direction of forward rotation with respect to R
and the outer race and the second planetary gear mechanism 2
A multi-disc clutch K is provided between the ring gear 2R and the fourth clutch means 4, and the fourth brake means B4 has the same structure as shown in FIG. The means B1 is constituted by a band brake. An example of the operation table is shown in Table 23.

(This page, hereafter in the margin) The example shown in FIG. 36 is an example in which the configuration shown in FIG. 33 is changed to include the sixth clutch means 6 and the first brake means B1. That is, the sixth clutch means 6 has the structure shown in FIG. 20 described above, and the first brake means B
1 is operated by a band brake 42 and a one-way clutch 40 in parallel with these, and the one-way clutch 40 is arranged on the inner peripheral side, and its outer race is attached to a predetermined fixed part integral with the case 6. There is. An example of the created vJ table is shown in Table 24.

(This page, the following is a margin) 24. It is composed of a one-way clutch 50 and a multi-disc brake 51, and a band brake 53 that is in a row with them, and the first brake means B1 is a band brake. be. The rest of the configuration is the same as the configuration shown in FIG. 36. An example of the operation table is shown in Table 25.

(This page, the following is a margin) In the example shown in FIG. 37, the second braking means B2 of the configuration shown in FIG. Fifth
In place of the brake means B5, a tenth clutch means KIO is provided between the carrier 3C of the third F1 ring gear mechanism 3 and the sun gear 3S to selectively connect the two, and the first brake means B1 is also provided internally. It is composed of a one-way clutch 40 and a band brake 42 provided on the circumferential side.

The rest of the configuration is the same as the configuration shown in FIG. 35. An example of the operation table is shown in Table 26.

(This page, the following is a margin) In the example shown in FIG. 138, the third brake means B3 between the sun gear 2S of the second planetary gear mechanism 2 and the case 6 is In both tables, a one-way clutch as the fourth braking means 84 is provided on the inner circumferential side, and the first braking means B1 is composed only of a band brake, and the other configuration is the same as that shown in FIG. 34. It is. An example of the working clothing is shown in Table 27. In the example shown in FIG. 39, the carrier 3C of the third planetary gear mechanism 3 is fixed by engaging the first brake means B1 while the sixth clutch means 6 is engaged when moving backward. When traveling backward, the load torque applied to the sixth clutch means 6 increases.

Therefore, it is preferable to reduce the size of the sixth clutch means 6, or to reduce the engine output or the input torque to the gear transmission mechanism when traveling in reverse in order to maintain its durability.

(This page, the following is a margin) In the example shown in FIG. 39, in the configuration shown in FIG. Then, the example shown in Table 7, FIG.
A one-way clutch 30 comprising 6 as the sixth clutch means.
It is arranged closer to the outer circumferential side, and the other configurations are the same as that shown in FIG. 36. Therefore, an example of the working clothing is the same as Table 24 of 1IIJ.

The example shown in FIG. 41 is obtained by removing the third brake means B3 from the above-mentioned configuration shown in FIG. It is obtained by deleting all and bII of . The working clothes are shown in Table 28 for reference. In this configuration as well, it is preferable to reduce the size of the sixth clutch means 6 or to reduce the engine output or the input torque to the gear transmission mechanism during reversing in order to maintain its durability.

(This page, hereafter in the margin) 28. It is composed of a front latch 40 and a band brake 42 in a parallel relationship thereto, and the other constructions are the same as the construction shown in FIG. 41. In this configuration as well, it is preferable to reduce the size of the sixth clutch means 6 or to reduce the engine output or the input torque to the gear transmission mechanism during reverse movement in order to maintain its durability. An example of the working clothing is shown in Table 29.

(This page, the following is a margin) The example shown in Figure 1N42 is a one-way clutch 50 that engages the first brake means B1 in one direction of a small diameter and a one-way clutch 50 in series therewith, which engages the first brake means B1 in one direction of the configuration shown in Figure 41 above. It is constituted by a multi-plate brake 51 in a relationship and a band brake 53 in a parallel relationship thereto, and a second
A third brake means B3, which is a band brake that selectively fixes the sun gear 2S of the 12th collection 1ul12, is provided, and the fourth brake means B4 is replaced with a single multi-disc brake, and the other configuration is shown in FIG. It is as impressive as the composition.

An example of the working clothing is shown in Table 30.

, (this page, hereafter blank) The example shown in FIG. 43 is an example in which the second brake means 82 of the configuration shown in FIG. In addition to replacing the third brake means B3 with the 30th front rake, a fifth brake means B5 consisting of a one-way latch 80 and a multi-plate brake 81 which are in series with each other is provided, and the other l! Alternatively, it may be similar to 414 shown in FIG. An example of the actuating plate is shown in Table 31.

(This page, the following is a margin) In the example shown in FIG. 44, the second brake means B2 is a single pan dove in the configuration shown in FIG. Sun gear 2S
and the case 6. Other configurations are 4th
The configuration is similar to that shown in FIG. An example of the operating plate is shown in the third section.
It is shown in Table 2.

(This page, the following is a margin) The example shown in FIG. 45 is the fifth pump 1461!I, which consists of a one-way clutch 80 and a multi-disc brake 81 that are in a series relationship with each other in the above-mentioned II command shown in FIG. 40. In the example shown in FIG. 41, the structure shown in FIG. 41 is changed from 1 to the first clutch means and 4 to the fourth clutch means, and a third brake means B3 is provided. The means 1 includes a multi-plate clutch 91 disposed between the input shaft 4 and the ring gear 2R of the second M star gear mechanism 2.
, another multi-disc clutch 92 and one-way clutch 93 which are parallel to this multi-disc clutch 91 and in series with each other, and the obtained Ii4
The clutch means 4 is composed of a single multi-disc clutch, and the second 'lIi star south car 411! A third brake means 83 is provided which is a band brake that selectively fixes the sun gear 2S of I2. The rest of the configuration is the same as that shown in FIG. 41. An example of the actuating plate is shown in Table 33. In addition, in this configuration as well, the sixth clutch means has six clutches.
In order to downsize the vehicle or maintain its durability, it is preferable to lower the engine output or reduce the input torque of the #B vehicle speed mechanism when traveling in reverse.

In the example shown in FIG. 47, the third brake means 83 is removed from the configuration shown in FIG.
A one-way clutch, which is the fourth brake means B4, is disposed on the inner circumferential side of the sixth clutch means, and the other configuration is the fourth brake means B4.
The configuration is similar to that shown in the figure. In this configuration as well, it is preferable to reduce the size of the sixth clutch means or to maintain its durability by lowering the engine output or reducing the input torque to the gear transmission mechanism during reverse travel. An example of the #IJ table is shown in Table 34.

(This page, hereafter in the margin) Table 34 As means B5, a one-way clutch 80 and a multi-disc brake 81 which are in a series relationship with each other are provided between the case 6,
Other configurations are similar to those shown in FIG. 47. In this configuration as well, it is preferable to reduce the engine output or the input torque to the gear shift position when moving backward, as in the example shown in FIG. 47. An example of the operation table is shown in Table 35.

(This page, blank space below) In the example shown in Fig. F1a, the second brake means B2 of the configuration shown in Fig. 47 is changed to a single band brake, and the sun gear 2S of the second M star gear mechanism 2 is changed. 5th brake that selectively locks Table 35 Above, and in Figures 24 to 48, examples have been shown that are advantageous in improving shift controllability and shift shock by using one-sided clutches, but they have one-way characteristics. As an engagement means, a band brake can be used in addition to a one-sided clutch.

In other words, with a band brake, if the band is tightened when a rotating body such as a drum is rotating from one part of the anchor (the fixed end of the band) to the other end, that is, the direction of rotation of the rotating body is in the so-called energy direction. If so, the rotating body will actively try to wind up the band, so the braking force will increase, and in the opposite direction of deenergization, the rotational force of the rotating body will tighten the band in a direction different from that of the deenergizing direction. Since the opposite is true, the braking force becomes smaller, and as a result, a directional characteristic is generated, which can be effectively applied with a one-way characteristic. Therefore, in this invention, a configuration in which a one-way clutch and a multi-disc brake are arranged in series or parallel on each side, a configuration in which a one-way launch and a band brake are arranged in parallel, or a configuration in which a one-way clutch and a multi-disc brake are arranged in parallel, or a one-way clutch and a multi-disc brake are provided. If they are arranged in series, it is also possible to replace the configuration in which multi-plate brakes are arranged in parallel with a single band or a band brake with a pair of bands wrapped in opposite directions. You can. In addition, the locations where engagement means with unidirectional characteristics are used can be arbitrarily selected as required, and therefore, as shown in FIGS. 24 to 48, unidirectional engagement means are not used at multiple locations. A unidirectional engagement means may be employed at only one location.

A more specific embodiment of the present invention is shown in FIG. 49. The example shown in FIG. 49 embodies the configuration shown in FIG. 31 described above, in which the input shaft 4 is connected to the output shaft (not shown) of a joint member such as a torque converter. , the tip of the input shaft 4 is connected to one clutch drum 100 of the first clutch means. The first clutch means 1 includes a clutch drum 100 and a clutch hub 101 integrated with the ring gear 2R of the second planetary gear machine @2, and a disc and a plate spline-fitted to each other. The hydraulic piston 102 that engages and disengages is disposed inside the clutch drum 100 in the axial direction. It is arranged so that it can move back and forth.

This hydraulic piston 102 is moved backward by a return spring 103. Input shaft 4 and 211th star m1
Similarly to 1, the third clutch means 3, which connects the sun gear 2S of il14t12, has the clutch drum 104 and the clutch hub 105, and the disks and plates spline-fitted to each other are brought into frictional contact with each other. The clutch huff 105 is integrated into the clutch drum 10G of the first clutch means, and the clutch huff 105 is integrated into the first clutch drum 10G. Further, the clutch drum 104 is connected to a cylindrical connecting drum 106 that covers the outer peripheral sides of the first and 211th ring gear mechanism 2 in the wi1 clutch means and has one end connected to the sun gear 2S of the second planetary gear i 4112. It's completely stopped. This third clutch hand I! A hydraulic piston 107 for engaging and disengaging the iK3 is built into the clutch drum 104, and a return spring 108 for moving the hydraulic piston 107 backward is provided.

On the opposite side of the first clutch means 1 with the 2121st gear mechanism 2 in between, a multi-plate clutch 70 constituting a part of the second clutch means 2 is arranged.
is supported by a hollow shaft 11G rotatably disposed on the inner peripheral side of the first center support 109. That is, the first center support 109 is fixed to the inner peripheral surface of the case 6, and the clutch drum 111 of the multi-disc clutch 70 is fitted to the boss portion of the first center support 109 so as to rotate while maintaining a liquid-tight state. On the other hand, the tip end is non-rotatably engaged with the connecting drum 106, and the clutch drum 111 is spline-fitted to a hollow shaft 110 rotatably supported on the inner peripheral side of the first center support 109. connected. A clutch hub 112 connected to the clutch drum 111 by frictional contact between a disk and a plate is connected to a first sun gear shaft 113 rotatably supported on the inner peripheral side of the hollow shaft 110. A hydraulic piston 114 for engaging and disengaging the second clutch means 2 is housed on the inner circumferential side of the clutch drum 111 so as to be movable back and forth, and hydraulic pressure is supplied to and discharged from the first center support. 109 from the outer circumferential side thereof and is formed through an oil passage 115. Furthermore, a return spring 116 is provided on the front side of the hydraulic piston 114.

The input shaft 4 is disposed on the inner peripheral side of the first sun gear shaft 113.
An intermediate shaft 117 is provided on the same axis as the second. ! ! It extends from the 42 side to the rear end on the opposite side of the input shaft 4, and the carrier 2C of the second planetary gear mechanism 2 is attached to the front end.
are connected to each other, and a ring gear 1R of the 11I ring gear mechanism 1 is connected to the rear end.

A multi-disc clutch 71, which constitutes a part of the second clutch means 2, is disposed on the opposite side of the second clutch means 2 with the first center support 109 in between. It is fitted into the boss portion of the 1 center support 109 so as to rotate while maintaining a liquid-tight state, and
It is connected to the hollow shaft 110. Multi-plate clutch 71
Torque is transmitted between the clutch drum 118 and the clutch hub 120 by pressing the disk and plate and bringing them into frictional contact with a hydraulic piston 119 housed inside the clutch drum 118 so as to be able to move back and forth. 2, the clutch hub 120 is connected to the second clutch means by means of a one-way clutch 7 forming part of the second clutch means.
The inner race of the one-way clutch 70 is integrated with the outer race of the first sun gear shaft 113.
is connected to. That is, the multi-disc clutch 71 and the one-way clutch 70 are arranged in series. In addition, tIt
J&! Multi-disc clutch multi-disc clutch return spring 1
This is done by moving the hydraulic piston 119 backward using the arrow 21.

Also, a hydraulic piston 119 that operates the multi-disc clutch 70
The hydraulic pressure is supplied to and discharged from the first center support 109 through another oil 122 formed by penetrating the first center support 109.

Multi-disc clutch 7 forming part of second clutch means 2
4 is arranged on the fourth clutch means so as to face 0. That is, this fourth clutch means 4 is composed of a multi-disc clutch 22 and a one-way clutch 20 which are in a parallel relationship with each other, and the multi-disc clutch 22 also includes a clutch drum 123, a disk, and a plate like the other clutches. The clutch drum 123 is mainly composed of a clutch hub 124, a hydraulic piston 125, and a return spring 126, which are connected to and released from the clutch drum 123 in a torque transmitting manner. Liquid-tight S on the boss part of the 2 center support 127
: The first
It is connected to one end of a second sun gear shaft 128 rotatably disposed around the outer periphery of the sun gear shaft 113 . Further, the clutch hub 124 is integrated with the outer race of the one-way clutch 20, and the inner race of the one-way clutch 20 is spline-fitted to the second sun gear shaft 128. The hydraulic pressure that operates the hydraulic piston 125 is the second hydraulic pressure.
It is configured to be supplied and discharged through an oil passage 129 formed by penetrating the center support 127. In addition, the second
The other end of the sun gear shaft 128 is connected to the sun gear 3S of the third planetary gear machine 113.

Further, the clutch drum 123 of the multi-disc clutch 22, which constitutes a part of the fourth clutch means 4, also serves as a brake drum, and a second brake means B2 consisting of a band brake is provided on the outer circumferential side of this clutch drum 123. ing.

A multi-disc brake 41 and a one-way clutch 40, which constitute the first brake means B1, are arranged on the opposite side of the fourth clutch means 4 with the second center support 127 in between. The disc of the multi-disc brake 41 is spline-fitted to the tip of the second center support 127, the plate is spline-fitted to the outer peripheral surface of the outer race of the one-way clutch 40, and the inner race of the one-way clutch 40 is spline-fitted. is spline-fitted to a sleeve 130 integrated with the second center support 127. A carrier 3C of the third planetary tooth IIw structure 3 is connected to the outer race of the one-way clutch 40. Therefore, the multi-disc brake 41 and the one-way clutch 40 are in a parallel relationship with each other, and each selectively blocks the rotation of the carrier 30 of the third M ring gear lNN3. In addition, the hydraulic piston 13 that engages and releases the first brake means B1
1 is built in the second center support 127 and supplies and discharges hydraulic pressure to and from the hydraulic piston 131 via another oil passage (not shown) formed by penetrating the second center support 127 from the outer circumferential side thereof. It looks like this. The backward movement of the hydraulic piston 131 is performed by a return spring 132.

The third planetary gear mechanism 3 and the first planetary gear mechanism 1 are arranged in sequence following the first brake means 81, and the carrier 3C of the third planetary gear mechanism 3 is connected to the first sun gear shaft 11.
The ring gear 3R is connected to the carrier 1C of the 11i star gear **i, and these ring gear 3R and carrier 1C are connected to the output shaft 117 arranged on an extension of the intermediate shaft 117. It is connected to the shaft 5.

Therefore, even in the configuration shown in FIG. 49, the previous l! It is possible to set 5 gears and 1 reverse gear, or 7 forward gears and 1 reverse gear by adding the aforementioned 2.5 forward gears and 3.5 forward gears.

It should be noted that this invention is of course not limited to the above-mentioned embodiments, and the present invention essentially only needs to have the configuration described in the section of "Means for Solving the Problems" above. The connection form between the elements in each 11-wheel gear mechanism may be constant connection or selective connection via engagement means such as a clutch, and the input shaft and output shaft may be connected together. The elements to be fixed and the elements to be fixed may be determined as appropriate.

DETAILED DESCRIPTION OF THE INVENTION According to the present invention, as described in detail, there is provided a gear transmission fil using three sets of single-binion type M-gear mechanisms, and which uses a small number of engagement means to shift from five to seven forward speeds. It is possible to change gears, and when five forward gears are set, the gear ratio of each gear has a relationship close to a geometric series.
The gear ratio of each planetary gear mechanism is appropriate and the outer diameter of the device is small.
Therefore, according to the present invention, a compact l! lII speed change ti:IIW can be obtained.

[Brief explanation of drawings]

1 to 16 are skeleton diagrams showing embodiments of the present invention, and FIG. 17 is an operation table showing possible engagement/release combinations of each engagement means for setting each gear stage, Fig. 18 is a schematic diagram showing a specific example of the first clutch means, Figs. 19 (A) and (B) are schematic diagrams showing a specific example of the fourth clutch means, and Fig. 20! ! ! 21 is a schematic diagram showing a specific example of the first brake means, FIG. 22 is a schematic diagram showing a specific example of the second brake means, and FIG. 23 is a schematic diagram showing a specific example of the second brake means. 4 schematic diagrams showing specific examples of the brake means, FIGS. 24 to 48 are skeleton diagrams showing still other embodiments of the present invention, and FIG.
FIG. 2 is a sectional view showing an embodiment of the gear shift position shown in the skeleton in FIG. 1; 1.2.3--Planetary gear mechanism, IS, 2S, 3S
-...Sun gear, 1C, 2C, 3C...Carrier,
IR, 2R, 3R--Ring gear. Figure 12 Figure 13 Figure 17 @ 26 Figure 29 Figure 30 Figure 28 ff1 irh31 Figure 33r! ! J Figure 34 Figure 38 Figure 35 Hammer diagram

Claims (1)

[Scope of Claims] Three sets of single pinion type planetary gear mechanisms each having a sun gear, a ring gear, and a carrier holding a pinion gear that meshes with the sun gear and the ring gear, the ring gear of the first planetary gear mechanism and the second planetary gear mechanism. The carrier of the gear mechanism is always connected or selectively connected via the engagement means, and the carrier of the first planetary gear mechanism and the ring gear of the third planetary gear mechanism are always connected or connected via the engagement means. The sun gear of the first planetary gear mechanism and the carrier of the third planetary gear mechanism are constantly connected or selectively connected via an engagement means, and the sun gear of the second planetary gear mechanism A gear transmission for an automatic transmission, characterized in that a sun gear of a third planetary gear mechanism is constantly connected or selectively connected via an engagement means.