JPH0374662A - Gear shifter for automatic transmission - Google Patents

Abstract

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

Description

[Detailed Description of the Invention] Industrial Application Field This invention relates to a gear transmission used in an automatic transmission for a vehicle, and in particular, a gear train is mainly composed of three sets of single-binion type i-star gear mechanisms. gear shift till
It is related to.

As is well known in the art, the iI star gear mechanism has three elements: a sun gear, a ring gear, and a carrier that holds a pinion gear that meshes with these elements. By making it the output element and fixing the remaining other elements, the input rotation is increased,
Alternatively, it is possible to output by decelerating the forward rotation or decelerating the reverse rotation. Therefore, conventionally, generally, multiple planetary gears *
The mechanisms are combined to form a gear transmission for automatic transmissions. In that case, the method of combining the planetary gear mechanism, the value of the gear ratio (ratio of the number of teeth between the sun gear and the ring gear) of the planetary gear mechanism, and even the single binion type play! Il! II! The gear ratios that can be obtained vary depending on whether a mechanism or a double pinion type GUM mechanism is used, but not all combinations are practical, and the ease of mounting on a vehicle,
Gear trains that can be put to practical use are limited by various conditions such as manufacturability, 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.
It is very difficult to create an automatic transmission for a vehicle that satisfies the various conditions required.

In the past, many gear changes were devised against this background.
i! A device has been proposed, among which three sets of planetary mu
For example, a device using this structure is disclosed in Japanese Patent Application Laid-Open No. 60-882524.
Publication No. 51-48062, No. 54-13205
It is described in Publication No. 8.

RB to be Solved by the Invention The gear change 31' position described in the above-mentioned Japanese Patent Application Laid-Open No. 6C-88252 is a three-set single-binion type Miri!
1m! It is constructed so that five forward speeds and one reverse speed can be set by combining mechanisms. However, in this gear transmission, if the gear ratio of each planetary gear mechanism is set so that the gear ratio of each gear has a relationship close to a geometric series in order to prevent a significant decrease in the vehicle's driving force before and after shifting, It is necessary to set the gear ratio of the M star gear mechanism to a significantly large value, which results in the inconvenience of increasing the outer diameter of the idling gear mechanism.
If the gear ratio of the i-gear mechanism is set to such an extent that the outer diameter dimension does not particularly increase, the gear ratio of each gear will not have a relationship close to that of a geometric series, resulting in the problem of deterioration of the vehicle's power performance. there were.

Furthermore, the gear transmission described in Japanese Patent Application Laid-Open No. 51-48062 has two sets of single-binion type planetary tooth II mechanisms and one set of double-binion type l! In combination with a star gear mechanism,
It is constructed so that five forward speeds and two reverse speeds can be set. However, in this gear transmission, when shifting between forward first speed and second speed, and between second and third forward speed,
When changing gears between high and low speeds, it is necessary to change the engagement/disengagement state of a total of four engagement means, two clutch means and two brake means, which worsens shift shock.
Or 1! There was a problem that forced complicated gear change control.

Furthermore, the gear change 11'IA arrangement described in the above-mentioned Japanese Patent Application Laid-Open No. 54-132058 is composed of one set of Rapignoux type planetary gear mechanism and one set of single pinion type planetary gear mechanism, or two sets of single pinion type planetary gear mechanism. It is constructed by combining an idler Ill wheel mechanism and a set of double binion type I star gear mechanisms to set five forward speeds and one reverse speed. However, in this gear transmission, a large load torque is applied to the sun gear of each planetary gear mechanism in the first and second forward speeds and the reverse gear, which is disadvantageous in terms of strength and durability. Since power circulation occurs, this is also disadvantageous in terms of strength and durability, and the power transmission efficiency is also deteriorated. Another problem was that it required a double pinion type planetary gear mechanism.

The present invention has been made against the background of the above-mentioned circumstances, and an object of the present invention is to provide a gear transmission device that has a simple configuration and is easy to change speeds 111JIO.

Means for Solving the WR Problem In order to achieve the above object, the present invention provides three sets of single-binion planetary planets 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. A gear mechanism is provided, and the carrier of the first planetary gear mechanism, the ring gear of the second idler gear mechanism, and the ring gear of the 3121st gear mechanism are constantly connected or selectively connected via an engagement means. , the sun gear of the first planetary gear mechanism and the sun gear of the second planetary gear mechanism are always connected or selectively connected via an engagement means, and the carrier of the second planetary gear mechanism and the sun gear of the third planetary gear mechanism are It is characterized in that the sun gear is always connected or selectively connected via a retaining means.

Function: With the device of this invention, the first play! ! Gear mechanism carrier and second play! ! The ring gear of the 1111111 structure and the ring gear of the 31i-th gear mechanism are integrated with each other or separately, the sun gear of the first planetary gear mechanism and the sun gear of the second planetary gear mechanism are integrated with each other or separately, and The carrier of the second planetary gear mechanism and the sun gear of the third planetary gear mechanism, together with each other or separately, are respectively input or output elements or fixed elements, and also independent elements such as the ring gear of the first planetary gear mechanism is an input element, an output element, or a fixed element. As a result, each planetary gear mechanism works together or individually to increase/decelerate the rotation of the input shaft, or change the rotation speed of the input shaft as it is.
Alternatively, it is reversed and transmitted to the output shaft.

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 the first to third planetary gear mechanisms 1.2.3 connected to single-binion type planetary gears. Each of these planetary gear mechanisms 1
, 2.3 are connected as follows. In other words, 1 each! It! The one-wheel mechanism 1, 2.3 is
Sun gear 18°28.38 and its sun gear 18,28
．． Ring gears 1R, 2R, 3R arranged concentrically with 38
The main components are carriers IC, 2C, and 3C that respectively hold pinion gears meshing with sun gears 13, 23, and 33 and ring gears 1R, 2R, and 3R. The carrier IC of the first planetary gear mechanism 1, the ring gear 2R of the second planetary gear mechanism 2, and the third
11! ! The ring gear 3R of the gear mechanism 3 is connected to rotate as one, and the carrier 2C of the second planetary gear mechanism 2 and the sun gear 3S of the third planetary gear mechanism 3 rotate as one. It is connected like this. On the other hand, a fourth clutch means 4 is provided between the sun gear 13 of the first planetary gear mechanism 1 and the sun gear 2S of the second planetary gear mechanism 2, and these sun gears 1S.

2S are selectively connected to each other. Further, a second clutch means 2 is disposed between the sun gear 1S of the first planetary gear mechanism 1 and a carrier 2C of the second planetary gear mechanism 2, and a 1121
The sun gear 1S of the 1111 structure 1 and the carrier 2C of the second planetary gear mechanism 2 are selectively connected.

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

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, and the input shaft 4 and the ring gear 1R of the first planetary gear mechanism 1 are connected to each other. In between, there is a first
1 is provided in the clutch means, and 1! is provided between the input shaft 4 and the sun gear 1S of the first planetary gear mechanism 1, selectively connecting both. 3 is provided in the third clutch means for engaging the clutch.

1, K2, K3,
The key point of K4 is to selectively connect and disconnect each of the above-mentioned members, and is engaged and released by a mechanism conventionally used in automatic transmissions, 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 parallel can be employed as necessary. In practical use, since there are restrictions on the arrangement of each component, it is of course 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. It is.

Also, the carrier 2 of the second planetary gear mechanism 2 connected to each other
C and the 31st! A first brake means B1 for selectively blocking the rotation of the third wheel mechanism 3 with the sun gear 3s is provided between the carrier 2C and the sun gear 3s and the transformer tension case (hereinafter simply referred to as the case) 6. It is being Further, a second brake means 82 for selectively blocking the rotation of the sun gear 1S of the 1121st gear 11111 is provided between the sun gear 1s and the case 6. Furthermore, a third brake means 83 is provided between the sun gear 2S and the case 6 to selectively prevent rotation of the sun gear 2S of the second free tooth *a structure 2. These braking means B
1゜82, B3 may be configured with a wet multi-disc brake, band brake, or one-way clutch driven by a hydraulic servo mechanism conventionally used in general automatic transmissions, or a combination of these. In addition, in practical use, these brake means 81, B2
, B3 and each element to be fixed by these brake means 81, 82, 83 or between the case 6 and the case 6.

The output shaft 5 that transmits rotation to the prover shaft and counter gear (not shown) is connected to the third free tooth 1 [!
It is connected to the carrier 3C of II structure 3.

The gear transmission configured as described above has five forward speeds and
It is possible to change gears to 1 reverse gear or 7 forward gears and 1 reverse gear, and each of these gears has one gear for each of the clutch means described above.
．． 2, 3, 41!5 and brake means 81.
This is accomplished by engaging 82.83 as shown in Table 1. Table 1 also shows the gear ratio of each gear stage and its specific value, and the specific value is the gear ratio ρ1... of each planetary gear mechanism 1.2.3. ρ2. ρ3, ρ1
=o, 456, ρ2 = 0,51◇, ρ3 = 0
．． This is the value when it is set to 398. Further, in Table 1, the ○ mark indicates the engaged state, and the x mark indicates the released state. Hereinafter, the case where five forward gears and one reverse gear are set will be described first, and then two gear stages that can be added thereto will be explained.

(This page, hereafter in the margin) (First forward speed) The first clutch means 1 and the fourth clutch means 4 and the first brake means B1 are engaged.

In other words, the 131st! The ring gear 1R of the star gear mechanism 1 is connected to the input shaft 4, and the sun gear 1S of the first star gear mechanism 1 and the sun gear 2S of the second planetary gear mechanism 2 are connected to the fourth clutch means by 4 to 1! The carrier 2C of the second planetary gear mechanism 2 and the third
The sun gear 3S of the planetary gear mechanism 3 is fixed. Therefore, in the first planetary gear mechanism 1, as the ring gear 1R rotates together with the input shaft 4, the carrier 1C rotates in the forward direction (rotation in the same direction as the input shaft 4; the same applies hereinafter), and the sun gear 1S rotates in the same direction as the input shaft 4.
The input shaft 4 rotates in the opposite direction. The same applies below. As a result, in the second planetary gear mechanism 2, the ring gear 2R is connected to the carrier 1C of the first planetary gear mechanism 1,
In addition, since the carrier 2C is fixed, the sun gear 2S rotates in the opposite direction together with the sun gear 1 of the first planetary gear mechanism 1, and in the 3rd:i star gear mechanism 3, the sun gear 3S is fixed and ! Sun gear 1S of 1ri gear mechanism 1
Since the ring gear 3R connected to the ring gear 2R of the second planetary gear mechanism 2 rotates in the forward direction, the carrier 3C is decelerated relative to the input shaft 4 and rotates in the forward direction. In the end, the third ¥1
The output shaft 5 connected to the carrier 3C of the star gear mechanism 3 is
It is decelerated with respect to the input shaft 4 and rotates in the forward direction, and becomes the first speed in which the gear ratio is the largest in the forward gear. And the gear ratio is the first
As shown in the table, (1+ρ3) 10ρ1 (1+ρ2)
It is expressed as (1+ρ3)/ρ2, and its specific value is 3.2
It becomes 85. In this case, no power circulation occurs.

(Second Forward Speed) In addition to engaging the first clutch means 1, at least any two of the second clutch means 2, the first brake means B1, or the second brake means 82 are engaged. That is, in the state of the first forward speed, the fourth clutch means is
Instead, the second clutch means 2 is engaged, the second brake means B2 is engaged, or the second clutch means is engaged with both 2 and the second brake means B2. Therefore, for example, when the first clutch means 1 and the first and second brake means at and B2 are engaged, in the first planetary gear structure 1, the ring gear 1R is fixed with the sun gear 1S fixed. Since the carrier 1C rotates together with the input shaft 4, the carrier 1C is decelerated relative to the input shaft 4 and rotates in the forward direction.
transmitted to.

In the 312th ring gear mechanism 3, since the ring gear 3R rotates in the forward direction with the sun gear 3S fixed, the carrier 3C is decelerated relative to the ring gear 3R and rotates in the forward direction. In this case, since the sun gear 2S of the second planetary gear mechanism 2 is not connected to the input shaft 4 and the case 6, no particular acceleration/deceleration action is performed. As a result, the rotation of the input shaft 4 is as follows. Substantially, the speed is reduced by the 111th ring gear mechanism 1 and the 3rd planet @11 mechanism 3 and transmitted to the output shaft 5, and the gear ratio is (1+ρ1) as shown in Table 1.
)(1+ρ3>, and its specific value is 2.035. In this case as well, no circulation of power occurs.

Furthermore, if the second clutch means 2 and the second brake means B2 are engaged in addition to the first clutch means 1, the second clutch means 2 and the second brake means B2 can be engaged.
2 in the clutch means, the carrier 2 of the second planetary gear mechanism 2
C and the sun gear 3S of the third gear mechanism 3,
Since these are connected to the sun gear 1S of the first planetary gear mechanism 1 which is fixed by the brake means B2, B2 acts on the second clutch means as a brake, and the second clutch means moves forward in the same way as described above. '1M is set.

(Third Forward Speed) The first clutch means 1 and the third clutch means 3 are engaged with the first brake means B1. That is, the second speed is set to the first clutch means B1 and the first brake means B1,
The second clutch means is set to engage 2 or the second brake means B2, and from that state, the second clutch means 2 or the third clutch means 3 is engaged instead of the second brake means B2. let Therefore, in the first planetary gear mechanism 1, since both the ring gear 1R and the sun gear 1S rotate together with the input shaft 4, the whole rotates together with the input shaft 4, and the rotation of the carrier IC is caused by the rotation of the carrier IC.
The signal is transmitted to the ring gear 3R of the 11-star gear mechanism 3. In the third planetary gear mechanism 3, since the sun gear 3S is fixed, the carrier 3C is decelerated relative to the ring gear 3R and rotates in the normal direction. In addition, the 2'11th! ! Since the gear mechanism 2 is not connected to the input shaft 4 and the case 6 as in the case where the sun gear 2S is in the second speed, the gear mechanism 2 does not perform any particular acceleration or deceleration action. As a result, in actual use, only the third planetary gear mechanism 3 performs a deceleration action and transmits the rotation of the input shaft 4 to the output shaft 5. As shown in Table 1, the gear ratio is expressed as (1+ρ3), and its specific value is 1.398. Also, no power circulation occurs.

(Forward No. 431!> 1, K2, K for the 11th to 4th clutch means
3, engages at least any three of 4 with
and release the brake means 31,32.

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 clutches are engaged, such as engaging the first to third clutch means 1 to 3, or engaging the first and third and fourth clutch means Kl, 3, and 4. If you engage the means, I! III
Since the entire row rotates together with the input shaft 4 and no acceleration/deceleration action occurs, the gear ratio is "1". For example, 1. 2, 3
By engaging the input shaft 4 without generating a power ring,
The driving force from can be transmitted to the output shaft 5.

(Forward 5311> Engage the second and third clutch means 2, 3, and the third brake means B3. That is, in the fourth speed state described above, the first to third clutch means 1 to 3 are engaged. 3 is engaged, and from that state, the third clutch means B3 is engaged in place of 1 in the first clutch means.Therefore, since 2 is engaged in the second clutch means, the third clutch means B3 is engaged instead of 1 in the first clutch means. The carrier 2C of the 2M star gear machine I!42 and the sun gear 3S of the third planetary gear mechanism 3 are connected to the input shaft 4, and the sun gear 2S of the 2M star gear mechanism I!42 is fixed, so the 2111th star In the gear mechanism 2, the ring gear 2R is accelerated relative to the input shaft 4 and rotates in the forward direction, and this is transmitted to the ring gear 3R of the 311th gear mechanism 3.As a result, in the third planetary gear mechanism 3, the sun gear 3S rotates. Since the ring gear 3R rotates in the forward direction at a higher speed than the input shaft 4 while rotating in the forward direction together with the input shaft 4, the carrier 3C rotates in the forward direction at an intermediate speed between the sun gear 3S and the ring gear 3R. Mechanism 1 has its ring gear 1R
Since it is not connected to the input shaft 4, the sun gear 1S does not particularly perform an acceleration/deceleration action. It acts as a connecting transmission member. That is, in this case, the carrier 2C of the second planetary gear mechanism 2 and the third M
The sun gear 3S of the star gear mechanism 3 is indirectly connected to the input shaft 4, and these 12-mile gear mechanisms 2 and 3 perform an acceleration/deceleration action to increase the rotation speed of the input shaft 4 and rotate the output shaft 5.
The transmission is transmitted to 5th forward speed, which is an overdrive stage. Further, the carrier 2C of the second planetary gear mechanism 2 and the third
Without directly connecting the sun gear 3S of the idle Nm wheel mechanism 3 to the input shaft 4, the first planetary tooth I! Since the mechanism 1 is connected to the input shaft 4 via the sun gear 1S, the rotation speed of the sun gear 1S and the relative rotation speed of the pinion gear with respect to the carrier 1C are reduced in the first idler gear structure 1, which improves durability. will be advantageous. The gear ratio in this case is expressed as (1+ρG)/(1+ρ2+ρa> as shown in Table 1), and its specific value is 0.733.Also in this case, no power circulation occurs.

(Reverse) Engage the third and fourth clutch means 3. to 4 and the first brake means B1. That is, the sun gear 2S of the second idler gear mechanism 2 and the sun gear 1 of the 11i-th gear mechanism 1
The S arm is connected to the input shaft 4, and the carrier 2C of the second idling gear mechanism 2 and the sun gear 3S of the 3rd M id gear mechanism 3 are fixed.

In this case, since the ring gear 1R of the first idler gear mechanism 1 is not connected to the input shaft 4,
As in the case of speed, the first planetary gear mechanism 1 is not particularly involved in the acceleration/deceleration action.In the second planetary gear mechanism 2, the sun gear 2S rotates together with the input shaft 4 while the carrier 2C is fixed. The ring gear 2R rotates in the opposite direction at a lower speed than the input shaft 4, and this is the ring gear 3 of the 31st ring gear mechanism 3.
Further, in the third planetary gear mechanism 3, the ring gear 3R rotates in the reverse direction with the sun gear 3S fixed, so that the carrier 3C rotates in the reverse direction at an even lower speed.

That is, in this case, the rotation of the input shaft 4 is substantially the same as the second one.
The speed is decelerated and reversed by the planetary gear mechanism 2 and the third M star gear mechanism 3, and is transmitted to the output shaft 5, resulting in a reverse gear. The gear ratio in this case is expressed as -(1+ρa)/ρ2 as shown in Table 1, and its specific value is -2,741. Note that, in this case as well, no circulation of power occurs.

As is clear from the above description of the first to fifth forward speeds and the reverse speeds, in the gear transmission shown in Fig. 1, when setting five forward speeds and one reverse speed, Since the gear ratio in the forward gear can be set in a relationship close to a geometric series, there is no significant drop in driving force before and after gear shifting, and the vehicle's power performance can be improved. ! Gear ratio of llI mechanism 1.2, 3 is 0.39
It can be set to an appropriate value of ~0.51, so:
Since the diameter of the III@II mechanism does not increase and it can be configured mainly with three sets of single-binion planetary gear mechanisms, a compact gear transmission can be achieved. Furthermore, as mentioned in the explanation of each gear, when shifting to another adjacent gear, it is only necessary to release one of the engagement means and engage the other engagement means. Since the gear shift can be performed by switching between the two engaging means, the gear shift control is easy, and at the same time, it can be advantageous in reducing shift shock.

Because there is no power circulation, the transmission efficiency of driving force is good (,
Moreover, the gear transmission device is highly durable and compact due to the low relative rotational speed of the pinion gear to the carrier, the low load torque of each gear and each engagement means, and the low rotational speed of each gear. I can do it.

In addition, the gear ratio in the overdrive gear is set to about 0.733, which improves power performance, fuel efficiency, and quietness at high speeds, and the gear ratio in the reverse gear can be set to -
Sufficient driving force can be ensured by setting it to about 2,741. Since the input shaft 4 and output shaft 5 can be arranged on the same axis, FR vehicles (front engine rear wheel drive vehicles)
It can be a gear transmission suitable for.

In addition, in the configuration shown in FIG. 1, two more gears can be set in addition to the gears mentioned above, and the values of the gear ratios of the two gears are between the second gear and the third gear. and the value between 3rd and 4th speeds, which are shown in the lower row of Table 1 for 2.5th speed (2,5til) and 3.5th speed (3,5til).
5th).

(2nd and 5th forward speed) This gear is a gear that corresponds to the above-mentioned 2nd and 3rd forward speed, and the first and second clutches are connected to the first clutch means.
Brake means B2 and third brake means B3 are engaged. That is, the ring gear 1 of the first gear mechanism 1
R to the input shaft 4, and the first M star gear mechanism 1
The sun gear 1S of the second planetary gear mechanism 2 and the sun gear 2S of the second planetary gear mechanism 2 are fixed. Therefore the 1st y! ! At Satonan Vehicle Organization 1,
Since the ring gear 1R rotates forward together with the input shaft 4 while the sun gear 1S is fixed, the carrier 1C is decelerated relative to the input shaft 4 and rotates forward, and this causes the 21i ring gear mechanism 2
and is transmitted to the ring gears 2R, 3R of the third idler gear mechanism 3. In addition, in the second planetary gear mechanism 2, the sun gear 2S
Since the ring gear 2R rotates forward at a lower speed than the input shaft 4, the carrier 2C rotates forward at a lower speed, and this is transmitted to the sun gear 3S of the third M star gear mechanism 3. As a result, in the third planetary gear mechanism 3, the ring gear 3R rotates forward at a slower speed than the input shaft 4, and the sun gear 3S rotates forward at an even slower speed.
The carrier 3C and the output shaft 5 connected thereto are greatly decelerated relative to the input shaft 4 and rotate in the forward direction. That is, each planetary gear mechanism 1.degree. 2.3 performs a deceleration action, decelerating the rotation of the input shaft 4 and transmitting the rotation to the output shaft 5. As shown in Table 1, the value of the gear ratio is expressed as 1+ρ2 +ρ3, and its specific value is 1.611. In this case as well, no power circulation occurs.

(3rd and 5th forward speed) This speed corresponds to the above-mentioned 3rd and 4th forward speed, and the first and third clutch means have 1, 3 and 3 clutch means. The brake means 83 is engaged. That is, the ring gear 1R and sun gear 1S of the first planetary gear mechanism 1 are connected to the input shaft 4, and the sun gear 2s of the second planetary gear mechanism 2 is fixed. Therefore, since the two elements of the first planetary gear mechanism 1 rotate together with the input shaft 4, the whole unit rotates positively at the same speed as the input shaft 4, and accordingly, the second planetary gear mechanism 2 and the third M Ring gears 2R and 3R of the star gear mechanism 3 rotate forward at the same speed as the input shaft 4.

In addition, in the second planetary gear mechanism 2, the ring gear 2R rotates forward at the same speed as the input shaft 4 with the sun gear 2S fixed, so the carrier 2C rotates forward at a lower speed than the input shaft 4, which causes the third planetary gear mechanism 3 to rotate forward at a lower speed than the input shaft 4. As a result, in the third planetary gear mechanism 3, the ring gear 3R is transmitted to the input shaft 4.
Since the sun gear 3S rotates forward at a constant speed, the sun gear 3S rotates forward at a lower speed than the input shaft 4, so that the carrier 3C and the output shaft 5 connected thereto are connected to the second planetary gear mechanism 2 and the input shaft 4. It rotates forward at a speed reduced by the third planetary gear mechanism 3.

Therefore, the gear ratio is (1+ρ
2) It is expressed as (1+ρ3)/(1+ρ2+ρ3), and its specific value is 1.106. In this case as well, no power circulation occurs.

By the way, in the embodiment shown in FIG. 1, as is clear from Table 1, the second idlerity mechanism 2 is substantially involved in shifting in the second and third speeds of curve movement, so in this case Furthermore, it is preferable to reduce the rotation of the elements of the second planetary gear mechanism 2 as much as possible.

From this point of view, the example shown in FIG. 2 connects the ring gear 2R of the second planetary gear mechanism 2 with the carrier 1S of the 1'M star south wheel mechanism 1 and the ring gear 3R of the third planetary gear mechanism 3. It is configured to be solved in the second and third forward speeds. In other words, the configuration shown in FIG.
Of the configuration shown in the figure, the ring gear 2R of the second planetary gear mechanism 2, the carrier 1C of the 1' planetary gear mechanism 1, and the third
5 is set as fF@ for the fifth clutch means that selectively connects and releases the ring gear 3R of the planetary gear mechanism 3. Even with the configuration shown in FIG. 2, each gear stage can be set without causing power circulation, and the operating gears thereof are as 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 311th forward speed, and the 3.5th forward speed corresponds to the 5th forward speed.

(This page, hereafter in the margin) Table +631: At least any two of these three should be engaged.

Further, in this invention, it is not particularly necessary to always connect the carrier 2C of the 231ii star gear mechanism 2 and the sun gear 3S of the third planetary gear mechanism 3, and these carrier 2C and sun gear 3S can be connected as necessary. They may be configured to be connected and uncoupled.

FIG. 3 shows an example of this, and the configuration shown here is between the carrier 2C of the 2' planetary gear mechanism 2 and the sun gear 3S of the 3M planetary gear mechanism 3 in the configuration shown in FIG. 6 is interposed in the sixth clutch means, and the first brake means B1 is connected to the sun gear 3S of the 31st star south wheel mechanism 3 and the case 6.
It is placed between. Even with the gear transmission with the configuration shown here, there are 5 forward gears and 1 reverse gear without any power circulation.
7 forward speeds and 1 reverse speed can be set, and the operating gears are shown in Table 3.

(This page, below margin) No. table An example is shown in FIG.

Along with additionally installing 6 in the above-mentioned sixth clutch means, it is also possible to further add a brake means for independently fixing the carrier 2C of the second planetary gear mechanism 2, and its configuration is shown in FIG. It is as follows. That is, the configuration shown here is a configuration in which the fourth brake means B4 is interposed between the carrier 2C of the 21st ring gear mechanism 2 and the case 6 in the configuration shown in FIG. 3 above. The operating gear of this gear transmission is as shown in Table 4, and the gears can be set to 5 forward speeds and 1 reverse speed, or 7 forward speeds and 1 reverse speed. Further, in the configuration shown in FIG. 4, in the reverse gear, the sun gear 3S of the third planetary gear mechanism 3 is fixed by the first brake means B1, and the carrier 2C of the second planetary gear mechanism 2 is fixed by the fourth brake means B4. As a result, no load torque is applied to the sixth clutch means 6, and the sixth clutch means 6 can be made compact with a small capacity.

(This page, blank space below) Table 4 In addition, by additionally installing the sixth and fourth brake means B4 in the sixth clutch means, the second brake means B2 can be omitted. Please show an example of this. This is as shown in FIG. The working clothes are shown in Table 5.

No. 5 table No. table An example is shown in FIG.

Further, the example shown in FIG. 6 includes the carrier 1C of the first planetary gear mechanism 1, the second planetary gear mechanism 2, and the third M planetary gear mechanism 3.
Another clutch means (7> is provided in the seventh clutch means) between the ring gears 2R and 3R. An example of its operating gear is shown in Table 6.

As is known from Table 6, the first clutch means has a
can be connected at all times, so 1 can be removed from the first clutch means and the input shaft 4 and the first planetary gear mechanism 1 can be connected to each other.
It is also possible to have a configuration in which the ring gear 2R and the ring gear 2R are always connected. In that case, the working clothing will be the same as in Table 6 above, with column 1 removed. Furthermore, the number of possible engagement/release combination patterns for setting each gear stage is reduced by omitting one for the first clutch means.

Here, the combinations of engagement and disengagement of each clutch means and brake means for setting each gear stage are summarized in FIG. 7. In FIG. 7, the mark Q indicates engagement, the blank space indicates release, and the mark * indicates engagement. Further, FIG. 7 is useful as an operating device for the gear transmission having the configuration shown in FIG. 4 described above.

As can be seen from FIG. 7, the first brake means BI
F3, the second brake means B2, and the fourth brake means B4 can be released at any gear depending on the combination of engagement and release of the other clutch means and brake means. Any one or two of the brake means 31°B2°B4 can be eliminated. Various modifications of the invention can be easily inferred from FIG. 7.

By the way, in each of the embodiments described above, each clutch means has one to
7 and each of the brake means 81 to B4 are shown with symbols of multi-disc clutches or multi-disc brakes. However, in this invention, clutch means and brake means are used to facilitate shift control and to alleviate shift shock. An engagement means having unidirectional characteristics can be used. Here, the engagement means having one-way characteristics includes well-known one-way clutches equipped with rolling elements such as sprags, band brakes whose torque capacity differs depending on the direction of load, and the like. By using the engagement means alone or in combination with a multi-disc clutch or multi-disc brake, it is possible to reduce the number of engagement means that have to perform engagement/disengagement switching control during gear shifting, and to reduce load torque. Since the engaged/disengaged state is automatically switched depending on the change, shift shock is improved. 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 the two elements that are directly connected by the unidirectional engagement means, and the two elements that are connected through another element that rotates in the same manner before shifting. It may be between. The unidirectional engagement means is provided at a position where the clutch means (6 for the sixth clutch means) selectively connects the carrier 2C of the second planetary gear mechanism 2 and the sun gear 3S of the third planetary gear mechanism 3. There is a difference between cases where the clutch means is provided and cases where the clutch means is not provided, and there are differences depending on the shift pattern, including so-called jump shifting other than shifting to adjacent gears. As shown in FIG. 6, the position where the unidirectionality securing means is provided is exemplarily shown in the case where the sixth clutch means is provided with 6.

Regarding the shift between the first speed and the second speed, between the sun gear 1S of the first planetary gear mechanism 1 and the sun gear 2S of the second planetary gear mechanism 2, and between the carrier 2C of the second planetary gear mechanism 2 and the third
If a one-way engagement means such as a one-way clutch is interposed between the sun gear 3S of the planetary gear mechanism 3 or between the carrier 2C of the second planetary gear mechanism 2 and the case 6. good. Regarding the shift between the 1st speed and the 2.5th speed, the carrier 2C of the second planetary gear mechanism 2
A unidirectional engagement means may be provided between the case 6 and the sun gear 3S of the third planetary gear mechanism 3, or between the case 6 and the sun gear 3S of the third planetary gear mechanism 3.

Regarding the shift between the first speed and the third speed, between the sun gear 1S of the first planetary gear mechanism 1 and the sun gear 2S of the second planetary gear mechanism 2, and between the carrier 2C of the second planetary gear mechanism 2 and the 3
A unidirectional engagement means may be provided at least at one location between the sun gear 3S of the planetary gear mechanism 3 and between the carrier 2C of the second planetary gear mechanism 2 and the case 6. Regarding the shift between the 1st speed and the 3.5th speed, the sun gear 1S of the 1st M star gear mechanism 1 and the sun gear 2 of the 2nd planetary gear mechanism 2
S, between the carrier 2C of the second planetary gear mechanism 2 and the case 6, and between the sun gear 3S of the third planetary gear mechanism 3 and the case 6. All you have to do is intervene. 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. 1st gear and 4th gear
Regarding the speed change between the speed and the
A unidirectional engagement means may be interposed between at least one of the sun gear 3S and the case 6. Regarding the shift between the first speed and the fifth speed, between the sun gear 1S of the first planetary gear mechanism 1 and the sun gear 2S of the second planetary gear mechanism 2, the carrier 2C of the second planetary gear mechanism 2 and the case 6 between the sun gear 3S of the third planetary gear mechanism 3 and the case 6, and between the ring gear 1R of the 11th planetary gear mechanism 1 and the input shaft 4.
A unidirectional engagement means may be interposed at at least one location between the two. In this case as well, there are shift patterns that require multiple shifts.

Regarding shifting between 2nd speed and 2.5th speed, 13g
A unidirectional engagement means is interposed between the sun gear 1S of the satellite gear mechanism 1 and the sun gear 3S of the third planetary gear mechanism 3 or between the sun gear 3S of the 3111th gear mechanism 3 and the case 6. That's fine. Regarding the shift between the second speed and the third speed, between the sun gear 1s of the first freewheeling gear mechanism 1 and the sun gear 3s of the third planetary gear mechanism 3, or between the sun gear 1S of the first freewheeling 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 2nd speed and 3.5th speed, between the sun gear 1S of the first planetary gear mechanism 1 and the sun gear 3s of the third planetary gear mechanism 3, the 1!2nd radial tooth iti*
Between the sun gear 1S of structure 1 and case 6, there is a third play tis*
A unidirectional engagement means may be interposed at at least one location between the sun gear 3s of the mechanism 3 and the case 6.

In this case, there is a shift pattern that requires multiple shifts. Second
Regarding the shift between speed and fourth speed, at least either between the sun gear 1S of the first planetary gear mechanism 1 and the case 6 or between the sun gear 3S of the third N-gear mechanism 3 and the case 6. A unidirectional engagement means may be provided.

Regarding the shift between the second speed and the fifth speed, between the sun gear 1S of the first planetary gear mechanism 1 and the case 6, between the sun gear 3S of the third planetary gear mechanism 3 and the case 6, and between 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 1R of the gear mechanism 1 and the input shaft 4. In this case as well, there is a shift pattern that requires multiple shifts.

Regarding the shift between 2.5th speed and 3rd speed, between the sun gear 1S of the first planetary gear mechanism 1 and the sun gear 2S of the second planetary gear *@2, the sun gear of the first planetary gear mechanism 1 Between 1S and case 6, sun gear 2S of 2nd yen gear mechanism 2
A unidirectional engagement means may be interposed at at least one location between the case 6 and the case 6. In this case, there is a shift pattern that requires multiple shifts. 2.5th gear and 3.5th gear
Regarding the speed change, between the sun gear 1S of the first Wi star gear mechanism 1 and the sun gear 2S of the second A unidirectional engagement means may be interposed in at least one of them. Regarding the shift between 2.5th speed and 4th speed, between the sun gear IS of the first planetary gear mechanism 1 and the case 6 or the sun gear 2 of the second M planetary gear mechanism 2.
A unidirectional engagement means may be interposed between at least one of S and the case 6. Regarding the shift between the 2.5th speed and the 5th speed, between the sun gear 1S of the first planetary gear mechanism 1 and the sun gear 2S of the second planetary gear mechanism 2, the first
Between the sun gear 1S of the planetary gear mechanism 1 and the case 6, the first
A unidirectional engagement means may be interposed at at least one location between the ring gear 1R of the iI ring gear mechanism 1 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 3S of the third planetary gear mechanism 3 and the case 6. What is necessary is to intervene with a combining means. Regarding the shift between 3rd speed and 5th speed, between the sun gear 3S of the third planetary gear mechanism 3 and the case 6, and between the sun gear 1S of the first planetary gear mechanism 1 and the carrier 1C.
or between the ring gear 1R or the ring gear 3R of the third planetary gear mechanism 3, or between the input shaft 4 and the carrier 1C of the first planetary gear mechanism 1, the ring gear 1R, or the ring gear 3R of the third planetary gear mechanism 3. A unidirectional engagement means may be provided at one location. In this case as well, there is a shift pattern that requires multiple shifts.

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

Regarding the shift between 4th and 5th speeds, the entire gear train rotates as a unit in 4th speed, so each of the three elements of each planetary gear mechanism 1, 2, and 3 has only one direction. Sexual engagement means may be provided. That is, regarding the sun gear IS of the first planetary gear mechanism 1, the first planetary gear mechanism 1
carrier 1C and ring gear 1R, second planetary south wheel 1
112 sun gear 2S (15 and ring gear 2R, 3rd
A unidirectional engagement means may be interposed between the carrier 3C and the ring gear 3R of the No. 11 gear mechanism 3. Regarding the carrier 1C of the first planetary gear mechanism 1, the second
Ring gear 2R and third planetary gear m of planetary gear mechanism 2
A unidirectional engagement means may be interposed between the ring gear 3R of the structure 3 and any other element (including the input shaft 4) other than the case 6. Each of the ring gear 1R of the first planetary gear mechanism 1 and the sun gear 2S of the second planetary gear mechanism 2 has a unidirectional relationship with any other element (including the input shaft 4) other than the case 6. What is necessary is to intervene with a combining means. Regarding the carrier 2C of the second planetary gear mechanism 2, the carrier IC and ring gear 1R of the first planetary gear mechanism 1, the sun gear 2S and ring gear 2R of the second planetary gear mechanism 2, and the carrier 3C and ring gear 3R of the third planetary gear mechanism 3. A unidirectional engagement means may be interposed between either of them. Regarding the ring gear 2R of the second idling gear mechanism 2, the carrier IC of the first idling gear mechanism 1
and any other elements other than the ring gear 3R of the third planetary gear mechanism 3 and the case 6 (including the input shaft 4)
A unidirectionality ensuring means may be interposed between the two. 33rd
1! Regarding the sun gear 3S of the il gear mechanism 3, the carrier 1C and ring gear 1R of the first planetary gear mechanism 1, the sun gear 2S and the ring gear 2R of the second planetary gear mechanism 2
, the carrier 3C of the third planetary wheel mechanism 3 and the ring gear 3R may be interposed with a unidirectionality securing means. Regarding the carrier 3C of the 3'M skewer mechanism 3, a unidirectional engagement means may be interposed between it and other elements (including the input shaft 4) other than the case 6. and the third
Regarding the ring gear 3R of the idler gear mechanism 3, the 1st:1
! Carrier 1C of gear mechanism 1 and second M star gear mechanism 2
Other elements except ring gear 2R and case 6 (
(including the input shaft 4) may be provided with a unidirectional engagement means.

In addition, in the structure in which the carrier 2C of the 21st star gear mechanism 2 and the sun gear 3S of the first planetary gear mechanism 3 are always connected without providing the sixth clutch means 6 as shown in FIGS. 1 to 3, The locations where the unidirectional engagement means can be installed are more restricted than in the above case, such as not being able to install the unidirectional engagement means between these three parties, and the locations where the unidirectional engagement means can be installed must be selected appropriately. good.

Furthermore, the method of using the unidirectional engagement means is described in the specifications and drawings attached to Japanese Patent Application No. 63-'l 76270 and Japanese Patent Application No. 63-221670 filed by the present applicant. The following is an example in which what has been described can be adopted and such improvements are made to the engagement means.

The example shown in FIG. 8 is of the configuration shown in FIG. 5 described above.
The fourth clutch means 4 is constituted by a multi-disc clutch 10 and a one-way clutch 11 which are arranged in parallel with each other, and the first brake means B1 is constituted by a multi-disc brake 20 and one-way clutch 21 which are arranged in parallel with each other. Further, the third brake means B3 is constituted by a multi-disc brake 30 and a one-way clutch 31 arranged in series with each other, and a multi-disc brake 32 arranged in parallel with these, and the fourth brake means B4 is arranged in series with each other. It is composed of a multi-disc brake 40 and a one-way clutch 41 that are in parallel relationship. Table 7 is an example of an operation table for shifting gears having the configuration shown in FIG. 8. In addition, in the operation table below, the O mark indicates the engaged state and the X mark indicates the disengaged state, which is the same as the operation table above.In addition, in the operation table below, the O 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 engagement/release combinations for setting the gear. The combination of engagement and release may be changed in this order, or any combination of engagement and release may be selected.

Table 7 The example shown in Figure 9 is the third example of the configuration shown in Figure 8 above.
This is constructed by replacing one multi-plate brake 32 in the brake means B3 with a band brake 33. The working clothes are the same as those in Table 7 above, with code 32 in column B3 replaced with code 33.

In the example shown in FIG. 10, the third brake means B3 of the configuration shown in FIG. 9 described above is configured by only the band brake 33. An example of such working clothing is shown in Table 8.

(This page, the following is a margin) The example shown in Table 11 shows the configuration shown in FIG. 27, the first brake means B2 is provided, the fourth brake means B4 is constituted by a single multi-disc brake, and the first brake means B1 is constituted by a one-way clutch 21 and a band brake 22,
Other configurations are similar to those shown in FIG. 10.

Table 9 shows an example of the operating gear of the gear transmission having the configuration shown in FIG. 11.

(This page, hereafter in the margin) The example shown in Table 12 shows that the third brake means B3 in the configuration shown in FIG. Instead of a configuration consisting of a plate brake 30, a one-way clutch 31, and a band brake 33 in a parallel relationship to the combination thereof,
The other configurations are similar to those shown in FIG. 11. An example of the working clothing is shown in Table 10.

In the example shown in FIG. 13, the structure shown in FIG. 13 is changed from the structure shown in FIG. 10 described above to the first brake means B1, the fourth brake stage B4, and the sixth clutch means. . That is, the first brake means B1 is constituted by a one-way clutch 21 and a band brake 22 which are in a parallel relationship with each other, the fourth brake means 84 is constituted by a single multi-disc brake, and the sixth clutch means B1 is constituted by a single multi-disc brake.
is composed of a multi-disc clutch 51 and a one-way clutch 52 which are in parallel relationship with each other, and the other configurations are similar to the configuration shown in FIG. 10. An example of the working clothing is shown in Table 11.

(This page, hereafter in the margin) The example shown in FIG. 14 is an improved version of the configuration shown in FIG. 10 described above. That is, the fourth brake means B4 is
The first brake means B1 is composed of a multi-disc brake 40 and a small-diameter one-way clutch 41 disposed on the inner circumferential side thereof, and the first brake means B1 is a one-way clutch disposed between the sun gear 3S of the third planetary gear lHf13 and the case 6. 21 and a band brake 22. The other configurations are the same as the configuration shown in FIG. Therefore, this 14th
The configuration shown in the figure is equivalent to the configuration shown in Figure 10 when purchased, but with a different arrangement, so the operating clothing may be obtained by replacing the code 20 in Table 8 above with the code 22, for example. It will be similar.

In the example shown in FIG. 15, among the configurations shown in FIG. The arrangement of the brake 22 and the sixth clutch means 6 is changed, and the other configurations are the same as the configuration shown in FIG. 14. An example of the created vJ table is shown in Table 12. As is known from Table 12, in the configuration shown in FIG. 15, when shifting from 3rd speed to 4th speed, the engagement/disengagement pattern shown in column b for 3rd speed is interposed. Therefore, it is possible to perform a smooth speed change by simultaneously operating the one-way clutch while switching between the two engaging means.

In addition, in the configuration shown in FIG. 15, in order to set the reverse gear, the band brake 22, tlj of the first brake means B1 and the sixth clutch means 6 are engaged, and the sun gear 2S and the third gear of the second planetary gear mechanism 2 are engaged. 3! Sun gear 3 of 2 star gear mechanism 3
Since S is fixed, θ acts as a brake on the sixth clutch means, and a large torque is applied to it. Therefore, in the configuration shown in FIG. 15, it is preferable to reduce the engine output or the input torque to the gear transmission in the reverse gear, and by doing so, the sixth clutch means 6 can be made smaller and its durability can be improved. can be improved.

(This page, the following is a margin) Table 12 The arrangement of 6 is changed to the sixth clutch means, and the multi-disc brake 61 is used as the second brake means B2 for independently fixing the sun gear 1S of the first planetary gear mechanism 1. and a one-way clutch 62 in series therewith are provided between the sun gear 1S of the first planetary gear mechanism 1 and the case 6. The rest of the configuration is similar to the configuration shown in FIG. 15. An example of the working clothing is shown in Table 13.

(This page, blank space below) In the example shown in Fig. 16, in the configuration shown in Fig. 15 above, the fourth brake means B4 is replaced with a single multi-disc brake, and the first brake means B1 and Table 13 are replaced with a single multi-disc brake. Although this invention has been described above by showing the first to fifteenth embodiments, it goes without saying that this invention is not limited to each of the above-mentioned embodiments. It is sufficient to have the configuration described in the section ``Means for Solving the Problem'', and the connection form of the elements in each M star gear mechanism may be such that even if the elements are constantly connected, it may be necessary to use a locking means such as a clutch. Further, the elements for connecting the input shaft and the output shaft and the elements to be fixed may be determined as necessary. Further, in the present invention, the one-way engagement means such as a one-way clutch may be employed in any one clutch means or brake means, or in a plurality of brake means or clutch means.

DETAILED DESCRIPTION OF THE INVENTION According to the present invention, as described in detail, there is provided a gear change device using three sets of single pinion type planetary gear mechanisms, which can shift from five to seven forward speeds using a small number of engagement means. In addition, when shifting 5 forward gears and 1 reverse gear, the gear ratio of each gear in the forward gear has a relationship close to a geometric series, and the gears of each M star gear mechanism The ratio is appropriate and the outer diameter of the device is small. Therefore, according to the present invention, it is possible to obtain a compact gear transmission device for an eye movement transmission, which has good power performance, shift shock, and shift control.

[Brief explanation of drawings]

Figures 1 to 6 are skeleton diagrams showing embodiments of the present invention, and Figure 7 summarizes engagement/release combinations that can be set to set each gear in the configuration shown in Figure 4. The operation table shown in FIGS. 8 to 16 are skeleton diagrams showing other embodiments of the present invention. 1゜2.3-1 [Til car ins, IS, 2S, 3S
...Sun gear, IC, 2C, 3G...Carrier,
1R, 2R, 3R...Ring gear, 4...Input shaft.

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 carrier of the first planetary gear mechanism and the second planetary gear mechanism. The ring gear of the gear mechanism and the ring gear of the third planetary gear mechanism are constantly connected or selectively connected via an engagement means, and the sun gear of the first planetary gear mechanism and the sun gear of the second planetary gear mechanism The carrier of the second planetary gear mechanism and the sun gear of the third planetary gear mechanism are always connected or selectively connected through the engagement means. A gear transmission device for an automatic transmission characterized by: