JPH02154842A - Gear shift device for automatic transmission - Google Patents

Abstract

PURPOSE:To cope with various specification changes by connecting the double pinion type first planetary gear and single pinion type second and third planetary gears in series and connecting specific elements directly or via coupling means respectively. CONSTITUTION:The double pinion type first planetary gear 1 and single pinion type second and third planetary gears 2 and 3 are arranged coaxially with an input shaft 4 and an output shaft 5; the first and third ring gears 1R and 3R, the first carrier 1C and the second sun gear 2S, the second and third carriers 2C and 3C, the second ring gear 2R and the third sun gear 3S are connected invariably or selectively via coupling means. When the first carrier 1C and the second sun gear 2S are connected via a clutch K4 and clutches K1-K4 and brakes B1 and B2 are selectively coupled, for example, five forward speeds and one reverse speed are obtained, and shift stages of other specifications are obtained by position changes of the clutches. A shift shock is reduced, the power performance is improved, and various specification changes can be coped with.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of the Invention This invention relates to a gear transmission used in an automatic transmission for a vehicle, and more particularly to a gear transmission constructed by combining three sets of planetary gears.

As is well known in the art, a planetary gear has three elements: a sun gear, a ring gear, and a carrier that holds a pinion gear meshing with these elements. By setting the output element as an output element and fixing the remaining elements, the input rotation can be increased in speed, decelerated in forward rotation, or decelerated in reverse and output. Therefore, conventionally, generally, multiple planetary gears A gear transmission for an automatic transmission is constructed by combining these. In that case, depending on how the planetary gears are combined, the value of the gear ratio of the planetary gears (ratio of the number of teeth between the sun gear and the ring gear), and whether to use a single pinion type planetary gear or a double pinion type planetary gear, etc. The resulting gear ratios vary widely, but not all combinations are practical, and the possibility of practical use is determined by various conditions such as mountability on vehicles, manufacturing possibilities, transmission characteristics, and required power performance. Gear trains with are limited. In other words, a planetary gear train can be configured in a huge number of ways depending on the combination of i-star gears and how to set the gear ratio, so it satisfies the conditions required for an automatic transmission for a vehicle. Creating 61 things involves great difficulties.

Conventionally, a large number of gear transmission devices devised under such a rear end have been proposed, and among them, a device using three sets of planetary gears is disclosed in, for example, Japanese Patent Laid-Open Nos. 5,117,767 and 5.
Publication No. 1-48062, Publication No. 51-108168,
It is described in JP 51-108170 and JP 51-127968.

Problems to be Solved by the Invention However, in a gear transmission in which a plurality of sets of planetary gears are roughly combined, it is difficult to determine how to connect each planetary gear, which element to connect to the input shaft, or which element to fix. The number of gears that can be set and the gear ratio at each gear vary depending on the vehicle.

Therefore, in practical use, the relationship with engine output and the i11! Gear transmissions are selected based on the intended use of the vehicle or the required characteristics.

In that case, if not only the arrangement of the clutch A5 brake but also the configuration of the gear train is to be different from the existing gear transmission, the type of gear transmission to be prepared will be the same as the type of vehicle. Not only will the number increase, but the productivity of gear transmissions, including design and manufacturing, will deteriorate.
In particular, the basic design has to be revised for each gear shift position with different specifications, and the production process cannot be standardized, resulting in poor productivity.

On the other hand, as mentioned above, in a gear transmission that combines multiple sets of planetary gears, the gear ratio that can be set varies greatly depending on how each element is connected and the arrangement of clutches and brakes. The way the elements are connected to each other is fixed regardless of whether it is connected constantly or through a clutch, and the number of clutches for input and brakes to fix the elements in a gear train with such a configuration is fixed. It is technically possible to appropriately determine the number of settable gear stages and their gear ratios depending on the gear position and arrangement, and in this way, even if gear transmissions have different specifications, the basic gear train It is thought that the above-mentioned problems can be solved to some extent by making them common. In that case, the basic gear train configuration should be small and light as a whole;
It is easy to manufacture, the gear ratios that can be set have a relationship close to a geometric series, it is advantageous in reducing shift shock, it is possible to set a gear ratio of "1" or less if necessary, and the maximum gear ratio It is preferable that the requirements such as a wide range between the minimum speed ratio and the minimum speed ratio be satisfied.

When considering the above-mentioned conventional gear transmissions from the viewpoint of obtaining a gear train with a wide range of so-called versatility, it is found that all of the above-mentioned conventional gear transmissions have a so-called overdrive gear ratio of ゛'1'' or less. It is said that the drive gears are set and one harp is operated, and there is no description of how to change the arrangement of clutches and brakes in order to change the settable gears, and furthermore, the gear ratio is not necessarily a geometric series. The relationship is not close to , and there may be disadvantages such as requiring special consideration to reduce shift shock or making driving difficult.

This defense was made in response to the above circumstances, and the automatic transmission has a basic configuration that can be easily changed to various specifications and can also satisfy multiple conditions. The purpose is to facilitate the use of gear transmissions.

Means for Solving the Problems This invention provides a first gear set, a first ring gear, and a first ring gear.
a first planetary gear having a first carrier holding a pinion gear that meshes with the sun gear and another pinion gear that meshes with the pinion gear and the first ring gear; a second sun gear; a second ring gear; a second sun gear;
a second M star gear having a second carrier holding a pinion gear meshing with the ring gear; a third sun gear;
A third planetary gear having a ring gear and a third sun gear and a third crystal gear holding a ring gear that meshes with the third ring gear, the first ring gear and the third ring gear are always connected or are connected through an engagement means. the first carrier and the second sun gear are connected at all times or are selectively connected via a retaining means, and the second carrier and the third carrier are connected at all times or through an engagement means. The second ring gear and the third sun gear are selectively connected via an engagement means, and the second ring gear and third sun gear are always connected or selectively connected via an engagement means.

Function: In the device of the present invention, each of the elements connected to each other as described above is integrally or individually used as an input element, an output element, or a fixed element, respectively,
Furthermore, an independent element such as the first sun gear is used as an input element, an output element, or a fixed element. Its unity,
Each of the planetary gears works together or independently to increase or decrease the speed of the input shaft, and transmits the rotation of the input shaft to the output shaft either directly or in reverse. In that case, the gears are set to, for example, 5 forward gears and 1 reverse gear, or are set to lower gears, and the range between the largest and smallest gear ratio is wide, and each gear ratio is The values are in a relationship close to a geometric series.

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 a first planetary gear 1 constituted by a double-binion type planetary gear, and
The second planetary gear 2 and the third MIJi gear 3 are each constituted by a single binion type 21-tooth gear, and each element in each of these M star gears 1°2.3 is connected as follows. has been done. In other words, the 1y1 star gear 1 includes the sun gear 1S, the ring gear 1R, and these gears 1.
S.

The main element is a carrier 1C that holds at least one pair of pinion gears disposed between the pinion gears 1R and meshing with each other. On the other hand, the 2′F1 star gear 2
The main elements are a sun gear 2S, a ring gear 2R arranged concentrically with the sun gear 2S, and a carrier 2C that holds a pinion gear that meshes with these gears 2S and 2H. Similarly to the second planetary gear 2, the third planetary gear 3 holds a sun gear 3S, a ring gear 3R arranged concentrically with respect to the sun gear 3S, and a pinion gear that meshes with these gears 3S and 3R. The main element is a carrier 3C. The ring gear 1R of the first M star gear 1 and the ring gear 3R of the third M star gear 3 are connected to rotate together, and the carrier 1C of the first planet gear 1 and the sun gear 2S of the second planet gear 2 are connected to each other so as to rotate together. It is selectively connected to the fourth clutch means via 4. Furthermore, the carrier 2C of the second planetary gear 2 and the carrier 3 of the third planetary gear 3
The ring gear 2R of the second planetary south gear 2 and the sun gear 3S of the second M star gear 3 are also connected so as to rotate together.

Note that as the V4 structure for connecting each of the above-mentioned elements, a connection structure employed 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. A first clutch means 1 is provided between the carrier 1C of the f-star gear 1 and the input shaft 4, and a ring gear 2R and a ring gear 2R of the second planetary south wheel 2 are connected to each other. A second clutch means 2 is provided between the sun gear 3S of the third service center 3 and the second clutch means 2 for selectively connecting these.

Furthermore, the input shaft 4 and the sun gear 1s of the 1″ i11 star gear 1
and a third clutch means for selectively connecting the two.
is provided. These clutch means 1, 2
, 3, and 4 are for selectively connecting and disconnecting each of the above-mentioned members. A wet multi-disc clutch that is engaged and released by
A one-way clutch, or a configuration in which these wet type multi-plate clutches and one-way clutches are arranged in series or in parallel, can be adopted 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 ring gear 2R and 3'T of the second; l star gear 2
A first braking means B1 for selectively blocking the rotation of the sun gear 3S of the L star gear 3 is provided between the ring gear 2R and the sun gear 3S and a transmission case (hereinafter simply referred to as the case) 6. Also number 1.
A second brake means B2 for selectively blocking the rotation of the sun gear 1S of the l-star gear 1 is provided between the sun gear 1S and the case 6. These braking means 81,
B2 can be configured with a wet multi-disc brake, a band brake, or a one-way clutch driven by a hydraulic servo mechanism conventionally used in general automatic transmissions, or a combination of these. In practical use, it is of course possible to interpose appropriate connecting members between these brake means B1, B2 and the respective elements to be fixed by these brake means 31, 32 or between the case 6.

An output shaft 5 that transmits rotation to a propeller shaft and a counter gear (not shown) is connected to a carrier 2C of the 21st star gear 2 and a carrier 3C of the 3rd M star gear 3, which are connected to each other.

The gear transmission configured as described above has five forward speeds and
It is possible to shift to one reverse gear, and each of these gears is controlled by the aforementioned clutch means Kl, K2.

K3. 4 and brake means 81, 82 as shown in Table 1.

Table 1 also shows the gear ratio of each gear and its specific value, and the specific value is for each y11 star gear 1.
2.3 gear ratio ρ1. ρ2. ρ3, ρ1 = 0.3
57, ρ2 = 0.400, ρ3: 0.409. Further, in Table 1, a circle mark indicates an engaged state, and a blank column indicates a released state. Each gear stage will be explained below.

(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 81 are engaged.

That is, the first Ill! The carrier 1C of the i-wheel 1 is connected to the input shaft 4, and the sun gear 2S of the second planetary gear 2 is connected to the input shaft 4 via the fourth clutch means 4 and the first clutch means 1, and the 21st star The ring gear 2R of the gear 2 and the sun gear 3S of the third planetary south wheel 3 are fixed. In this case, since the sun gear 1S is released from the input shaft 4 and the case 6, the first M star gear 1 does not particularly perform an increasing or decelerating action, and the third star gear 3 does not perform any acceleration or deceleration action. Since it is connected to the ring gear 1R of the first planetary gear 1, it does not particularly perform an increasing/decelerating action.

On the other hand, in the 23M star gear 2, the sun gear 2S rotates together with the input shaft 4 while the ring gear 2R is fixed, so the carrier 2C is decelerated relative to the input shaft 4 and rotates forward (input Rotation in the same direction as the shaft 4 (the same applies hereinafter) is transmitted to the output shaft 5. That is, the rotation of the input shaft 4 is decelerated by the second M star gear 2 and transmitted to the output shaft 5, and becomes the first speed in which the gear ratio is the largest in the forward gear.

The gear ratio is (1+ρ2) as shown in Table 1.
/ρ2, and its specific value is 3.500.

(Second forward speed) The first clutch means is engaged with the first and second brake means Bl and B2. That is, in the state of the first forward speed, the second brake means B2 is engaged instead of the fourth clutch means 4. In this case, since the fourth clutch means 4 is released, only the carrier 1C of the first planetary gear 1 is connected to the input shaft 4, and the sun gear 1S of the first M star gear 1 and the second planetary gear 2 are connected to the input shaft 4. ring gear A
-2R and the sun gear 3s of the third M star gear 3 are fixed. Therefore, in the first M star gear 1, since the carrier 1C rotates together with the input shaft 4 with the sun gear 1S fixed, the ring gear 1R is decelerated with respect to the input shaft 4 and rotates in the forward direction. 31i is transmitted to the ring gear 3R of the star gear 3. In the third planetary gear 3, since the ring gear 3R rotates forward at a lower speed than the input shaft 4 with the sun gear 3S fixed, the carrier 3C and the output shaft 5 connected thereto decelerate relative to the input shaft 4. rotates forward. In this case, the 211th star gear 2 is
+j＞Gi V2S is the first '! ! tMmWI 1 (7)
Since it is in a disconnected state with respect to the IJ gear 1C, no particular acceleration or deceleration action is performed. Therefore, as shown in Table 1, the gear ratio in this case is expressed as (1+ρ3)/(1-ρl), and its specific value is 2.191.

(Third Forward Speed) The first clutch means 1 and the third clutch means 3 are engaged with the first brake means B1. That is, in the state of the second speed, the third clutch means 3 is engaged instead of the second brake means B2. Therefore, both the carrier 1C and the sun gear 1S of the 1st wheel 1 are connected to the input shaft 4, and therefore the 1i-th star wheel 1 rotates forward as a whole at the same speed as the input shaft 4. . Accordingly, in the third M star gear 3, the ring gear 3R connected to the ring gear 1R of the first planetary gear 1 rotates forward at the same speed as the input shaft 4, and the sun gear 3S is fixed. 3C and the output shaft 5 connected thereto are decelerated relative to the input shaft 4 and rotate in the forward direction. In this case as well, the second M
As for the star gear 2, the sun gear 2S is the carrier 1 of the 11th star gear 1.
Since it is in a disconnected state with respect to c, no acceleration/deceleration action is performed during the waiting period. Therefore, in this case, the third
Only the planetary gear 3 performs a deceleration action, and its speed ratio is expressed as 1+ρ3, as shown in Table 1, and its specific value is 1.409.

(Moushin 4th speed) First to third clutch means Kl, K2, K
3 engages two clutch means, for example the first and third clutch means, 1°K3, and also engages the fourth clutch means 4. In other words, in the third speed state, instead of the first brake means B1, the fourth clutch means 4 is engaged, or the second clutch means 2 and the fourth clutch means 4 are engaged. 1st
and 1, K3 for the third and fourth clutch means.
, when K4 is engaged, the first M star gear 1 rotates as a whole in the same way as in the case of the third forward speed, and in addition, the second M tail gear 2 rotates as a whole, as in the case of the third forward speed. 2R is connected to the input shaft 4, so that the whole rotates as one. As a result, the third planetary gear 3 is
Since the ring gear 3R and the carrier 3C both rotate at the same speed as the input shaft 4, the entire ring gear 3R and the carrier 3C rotate in the forward direction at the same speed as the input shaft 4 as a whole. In other words, the entire gear train rotates in the forward direction at the same speed as the input shaft 4. In other words, the rotation of the input shaft 4 is directly transmitted to the output shaft 5.
Therefore, since no acceleration/deceleration action occurs, the gear ratio is '1''
becomes.

(Fifth forward speed) The second clutch means 2, the fourth clutch means 4, and the second brake means B2 are engaged. That is, in the fourth speed state described above, the second brake means 82 is engaged instead of the first clutch means 1.

In this case, number one! In! In the gear 1, since the sun gear 1s is fixed, the ring gear t 1 R and the carrier 1C rotate in the forward direction, and the rotational speed of the carrier 1c is faster than that of the ring gear 1R. In the 211u gear 2, the ring gear 2R rotates together with the input shaft 4, while the sun gear 2S rotates forward together with the carrier 1C of the first M star gear 1, so that the carrier 2C rotates forward faster than the ring gear 2R, that is, the input shaft 4. Further, in the third M star gear 3, the sun gear 3S rotates together with the input shaft 4, and the carrier 3C rotates in the forward direction faster than the sun gear 3S, so the ring gear 3R rotates forward at an even higher speed, and this rotates the ring gear 1R of the first M star gear 1. transmitted to. As a result, the 11i
In the star gear 1, the ring gear 1R and the carrier 1C rotate in the forward direction much faster than the input shaft 4, and accordingly, the entire gear train performs a speed increasing action, and the rotation of the input shaft 4 is transmitted to the output shaft 5 through amplification. be done. In other words, in this case, the gear ratio is ``“
It becomes an overdrive stage of 1" or less, and its gear ratio is expressed as 1-ρl-ρ2 (ρ1+ρ3) 1-ρ1=ρ2ρ3, as shown in Table 1, and its specific value is 0.702.

(Backwards) The third clutch means 3, the fourth clutch means 4, and the first brake means 81 are engaged. That is, while connecting the sun gear 1S of the first M star gear 1 to the input shaft 4,
The ring gear 2R of the second ¥1 star gear 2 and the sun gear 3S of the third ¥1 star gear 3 are fixed. Therefore, in the first planetary gear 1, since the ring gear 1R is subjected to a load from the output shaft 5, the sun gear 1S rotates together with the input shaft 4, causing the carrier 1C to rotate in the opposite direction (rotation in the opposite direction to the input shaft 4). (The same applies hereinafter) and this is transmitted to the sun gear 2S of the second planetary gear 2. In the 2nd!2nd star gear 2, the ring gear 2R is fixed, so when the sun gear 2S rotates in the opposite direction, the carrier 2C rotates in the opposite direction at a lower speed than the sun gear 2S.
transmitted to. And in the 3rd M star gear 3, the sun gear 3S
is fixed, the reverse rotation of the carrier 3C causes the ring gear 3R to reversely rotate faster than the carrier 3C, and this is transmitted to the ring gear 1R of the first planetary gear 1. That is, in the first planetary gear 1, the sun gear 1S rotates together with the input shaft 4, and the ring gear 111 and the carrier 1C rotate.
rotates in the opposite direction. As a result, the rotation of the input shaft 4 is decelerated and reversed and transmitted to the output shaft 5, resulting in a reverse gear. Therefore, the gear ratio in this case is expressed as 1+ρ1+ρ2 (ρ1+ρ3) ρ1ρ2 as shown in Table 1, and its specific value is -2,357.

As is clear from the above description of each gear, in the gear transmission shown in Figure 1, the gear ratios of each gear from 1st to 4th gear have a relationship close to a geometric series. , the ratio of the engine speeds before and after the gear shift is approximately constant, making it possible to provide an automatic transmission that is easy to drive. Furthermore, the gear ratio of the overdrive stage is approximately 0.702, which is an appropriate value within the practical range, so it lowers the engine speed during high-speed driving while ensuring power performance, improving fuel efficiency and quietness. It can be made into a good one. 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 can be changed by switching between the different engagement means, the gear change control is easy and the gear change shock can be reduced. On the other hand,
In the above gear transmission, three sets of planetary gears are sufficient, and the gear ratio of each planetary gear 1, 2.3 is 0.36 to 0.
Any value that allows for a well-balanced configuration of around ゜41 is sufficient, and accordingly 'l! The diameter of the single star gear does not increase, and therefore, according to the gear transmission described above, the overall configuration can be simplified and downsized.

By the way, as is known from Table 1, although the second clutch means 2 is engaged in the fourth and fifth forward speeds, in the fourth speed, the second clutch means 2 is engaged and the third clutch means is engaged. 3 can be set even if 3 is engaged. Therefore, if 2 is eliminated from the second clutch means, it is possible to create a transmission that can set 4 forward gears and 1 reverse gear without an overdrive gear. This is shown in Figure 2.

In addition, each planetary gear 1, 2, 3 does not perform an increasing/decelerating action at every gear stage, but the appropriate planetary gear performs an increasing/decelerating action depending on the engagement/release state of the clutch means and brake means. Therefore, each ¥1 star gear 1.2
．． Instead of achieving the basic connection relationship of each element in 3 (the connection relationship described in the section of the means for solving the problem) by, for example, constant connection using a connecting drum, the fourth clutch means described in 4. Even with a configuration in which this is achieved as needed by the latch means, the required gear stage can be obtained. An example is shown below.

FIG. 3 does not show the third embodiment of the eleventh embodiment, in which the fourth clutch means 4 in the configuration shown in FIG. and the carrier 3C of the third planetary gear 3.
It has been established. That is, the carrier 1C of the first planetary gear 1 is always connected to the first clutch means 1 and the sun gear 2S of the second planetary gear 2.
The carrier 2C of the Tl star gear 2 and the sun gear 3S of the third M star gear 3 are selectively connected to the fifth clutch means by 5. The other configurations are similar to those shown in FIG. The gear transmission having the configuration shown in FIG. 3 includes clutch means Kl and K2.

By engaging and disengaging K3 and K5 and the brake means 81 and 82 as shown in Table 2, it is possible to set five westward speeds and one reverse speed.

(This page, hereafter blank) Table 2 Also, in the gear shift position a of the configuration shown in Figure 3, the second
As is clear from the table, by eliminating 2 in the second clutch means, it is possible to create a transmission with 4 forward speeds and 1 reverse speed without an overdrive stage, an example of which is shown in Figure 4. .

Furthermore, the clutch means for connecting the elements in each planetary gear 1.2.3 is not limited to the fourth clutch means 4 and the fifth clutch means 5, as shown in FIG. 6 may be used as the clutch means. In other words, the gear transmission having the configuration shown in FIG. 5 eliminates 4 for the fourth clutch means in the configuration shown in FIG.
The carrier 1C of the M star gear 1 and the sun gear 2S of the second planetary gear 2 are always connected, and the 2nd %! 23! gear 2
6 is interposed in the sixth clutch means between the ring gear 2R of the third Mam vehicle 3 and the sun gear 3S of the third Mam car 3, and 2 is interposed in the second clutch means. It is connected to the ring gear 2R of the im star gear 2. Table 3 shows the working gear of the V-type gear transmission shown in FIG.

(This page, blank spaces below) Table Note that in the configuration shown in FIG. 5, the second clutch means 2 is not directly connected to the ring gear 2R of the second and first star gears 2,
As shown in FIG. 5, it may be configured to be directly connected to the sun gear 3S of the third planetary gear 3.

Also, in each gear transmission 8@ with the configuration shown in FIGS. 5 and 6, if 2 is eliminated as the second clutch means, 4 forward speeds and reverse speeds without overdrive speeds can be achieved for the same reason as described above. A gear transmission device that can set one gear stage can be used. An example is shown in FIG.

Each of the embodiments described above is an example using one clutch means for selectively connecting the elements in each 'M tail gear 2.3, but in this invention, each M star gear 1.2.3 A plurality of clutch means may be used to selectively connect the elements in the clutch, an example of which is shown below.

The gear transmission having the structure shown in FIG. 8 is an example in which 5 is used as the fifth clutch means and 6 is used as the sixth clutch means, and the sixth clutch means shown in FIG. 5 is used in the structure shown in FIG. It is configured by adding 6 to .

The gear transmission having the structure shown in FIG. 9 is constructed by adding six clutch means to the structure shown in FIG. 3 to the sixth clutch means shown in FIG.

Even if the gear transmission has the configuration shown in either of FIGS. 8 and 9, it is possible to set five forward speeds and one reverse speed.

Furthermore, if 2 is eliminated from the second clutch means from the configuration shown in FIGS. 8 and 9, it is possible to create a gear transmission capable of setting four forward speeds and one reverse speed without an overdrive speed. Figure 10 shows an example.

Although each of the embodiments described above uses two sets of brake means B1 and B2, the present invention can also be configured using three sets of brake means, and an example thereof is shown in the figure. As shown in Figure 11. That is, this first
The gear transmission having the configuration shown in FIG. 1 is constructed by interposing the third brake means B3 between the ring gear 2R of the second M star gear 2 and the case 6 in the configuration shown in FIG. 5 described above. be. The working clothes are shown in Table 4. With such a configuration, it is possible to reduce the transmission torque capacity of the sixth clutch means.

Table 1 By the way, in each of the embodiments described above, each clutch means has one
, 2 , 3 , 4 , 5 , and 6 are shown as symbols for multi-disc clutches, but in this invention, multiple clutch means are used to improve quietness, fuel efficiency, and alleviate shift shock. In addition to the plate clutch, a one-sided clutch or a combination of a multi-disc clutch and a one-sided clutch can be used, and the braking means 81, B2, and B3 are also similar to those in the above embodiments. In addition to the multi-disc brake shown, a one-way clutch, a band brake, or a combination of these may be used. Modifications of such latch means and brake means include Japanese Patent Application No. 63-1767270 and Japanese Patent Application No. 63-22 filed by the present applicant.
The specifications and drawings attached to the intercondylar section of No. 1670 can be adopted.

In FIG. 12, the first clutch means 1 and the fourth clutch means 4 are of the configuration shown in FIG. It has a configuration that combines a multi-disc brake and a directional clutch. That is, in the first clutch means 1, a one-sided clutch 10 and a multi-disc clutch 11 that are engaged when the input shaft 4 is about to rotate forward are arranged in series, and these combinations are connected to another multi-disc clutch 12. It is said that the configuration is arranged in parallel. Further, in the fourth clutch means 4, the carrier 1C of the 1'T1 star gear 1 is connected to the 2nd M
One-sided clutch 70 and multi-disc clutch 71 that engage when fJ-gear 2 attempts to rotate forward relative to sun gear 2S
It is constructed by arranging them in parallel. Further, the first braking means B1 includes a one-sided clutch 40 and a multi-disc brake 41 that are engaged when the ring gear 2R of the 2'i1 star gear 2 and the sun gear 3S of the 3rd TI star gear 3 are about to rotate in reverse.
It is constructed by arranging them in parallel. The second brake means B2 arranges in series a one-sided clutch 50 and a multi-disc brake 51, which are engaged when the sun gear 1S of the eleventh star gear 1 is about to rotate in reverse, and also It is constructed by arranging other multi-plate brakes 55 in parallel. Incidentally, in the configuration shown in FIG. 12, a multi-disc clutch or a multi-disc brake that is in a parallel relationship with the one-sided clutch is engaged when applying engine braking.

Although this invention has been described above by showing the first to twelfth 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 Problems'', and the connection form of the elements in each planetary gear may be selected through an engagement means such as a clutch, even if the elements are always connected. Further, the elements connecting the input shaft and the output shaft and the elements to be fixed may be appropriately determined as necessary.

DETAILED DESCRIPTION OF THE INVENTION According to the present invention, as described in detail, there is provided a gear transmission using one set of double pinion type Mu gears and two sets of single pinion type M star gears, which is compact and lightweight and reduces shift shock. Furthermore, it is possible to obtain a gear shift position for an automatic transmission that satisfies practical demands such as improvement in the power performance of a vehicle, and whose specifications can be easily changed.

[Brief explanation of the drawing]

1 to 12 are skeleton diagrams showing embodiments of the present invention, respectively. 1, 2.3... Planetary gear, 1S, 2S, 3S sun gear, 1C, 2C, 3C... Kireliya, It, 2R,
3R...Ring gear.

Claims (1)

[Scope of Claims] A first planetary gear having a first sun gear, a first ring gear, and a first carrier that holds a pinion gear that meshes with the first sun gear and another pinion gear that meshes with the pinion gear and the first ring gear. a second planetary gear having a second sun gear, a second ring gear, and a second carrier holding a pinion gear that meshes with the second sun gear and the second ring gear; a third sun gear; a third ring gear; a third planetary gear having a sun gear and a third carrier holding a pinion gear meshing with the third ring gear, the first ring gear and the third ring gear being connected at all times or selectively through an engagement means; , and the first carrier and the second sun gear are always connected or selectively connected via an engagement means, and the second carrier and the third sun gear are
The carrier is always connected or selectively connected through the engaging means, and the second ring gear and the third sun gear are always connected or selectively connected through the engaging means. Gear transmission device for automatic transmission.