JPH02240433A - Gear speed changer device for automatic transmission - Google Patents

Abstract

PURPOSE:To obtain a shift of forward 5-speed and reverse 1-speed by arranging between input and output shafts the first and second single pinion type and the third double pinion type planet gear mechanisms selectively engaging the first to fourth clutches and the first to third brakes. CONSTITUTION:The first and second planet gear mechanisms 1, 2 of single pinion type and the third planet gear mechanism 3 of double pinion type are coaxially arranged, connecting an input shaft 4 to the third sun gear 3s through clutches K1 to K3 further to the second sun gear 2s, first carrier 1c, second ring gear 2R and the first sun gear 1s through a clutch K4 while an output shaft 5 is connected to the third ring gear 3R. A shift of forward 5-speed and reverse 1-speed is obtained by selectively engaging the clutches K1 to K4 and brakes B1 to B3. Thus by selecting two selecting means, further without performing input selection, a speed change is performed with no large shock, and a speed change control can be facilitated.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application This invention relates to a gear transmission used in an automatic transmission for a vehicle, and particularly relates to a gear transmission device that is used in an automatic transmission for a vehicle, and in particular, it includes two sets of single pinion type planetary gears 11@ and one set of double pinion type planetary gears. This relates to an 8-position gear shift system which is a combination of three sets of planetary gear mechanisms.

Conventional technology The overall power performance and fuel efficiency of a vehicle are determined not only by the characteristics of the engine, but also by the characteristics of the transmission. It is necessary to use one that matches the characteristics of Therefore, in recent years, with the demand for higher performance vehicles and higher engine output and torque, there has been a demand for automatic transmissions that are more compact and have a large number of gears (for example, 5 gears). It's starting to look like this.

An example of an automatic transmission that can meet such demands is the one described in Japanese Patent Laid-Open No. 50-29963. This system is mainly composed of a gear train that combines two sets of single pinion type planetary gear mechanisms and one set of double pinion type planetary gear mechanisms. The second gear is a ring gear and a single pinion type planetary gear R structure.
Connecting the carrier of the planetary gear mechanism and the carrier of the third planetary gear mechanism which is a double pinion type planetary gear mechanism, and connecting the carrier of the first planetary gear mechanism and the ring gear of the second planetary gear mechanism, The sun gears of the second planetary gear mechanism and the third planetary gear mechanism are connected to each other, and the input shaft is selectively connected to the sun gear and its carrier of the first planetary gear mechanism and the carrier of the second planetary gear mechanism, and the input shaft is selectively connected to the sun gear of the first planetary gear mechanism and the carrier of the second planetary gear mechanism. The shaft is connected to a ring gear of a third planetary gear mechanism. The braking means includes a first braking means for selectively blocking the rotation of the sun gear of the first planetary gear mechanism, a first braking means for selectively blocking the rotation of the key τ/rear of the first planetary gear mechanism, and a ring gear of the second planetary gear mechanism. a second brake means for selectively inhibiting rotation of the ring gear of the first planetary gear Ij, a carrier of the second planetary gear assembly, and a carrier of the third planetary gear mechanism; and fourth braking means for selectively blocking rotation of the sun gears of each of the planetary gear mechanism and the third planetary gear mechanism.

Problems to be Solved by the Invention However, in the conventional transmission device described above, the load torque of each sun gear becomes larger than the input torque in the first and second forward speeds. If the diameter of the planetary gear IRII4 is increased, since the gear ratio of the planetary gear mechanism is fixed, a problem arises in that not only the planetary gear IRII4 itself but also the entire transmission becomes large in diameter.

In addition, in the conventional gear shift position described above, from the first forward speed to the third forward speed,
When shifting from one speed to the next, the fixed elements are left as they are, and the elements connected to the input shaft are sequentially switched, so-called input switching, so it is possible to shift without worsening the shift shock. There are problems such as extremely difficult control.

The present invention has been made in view of the above circumstances, and it is an object of the present invention to provide a gear transmission device in which the torque applied to the sun gear can be suppressed to a small level and speed change control can be easily performed.

Means for Solving the Problems In order to achieve the above object, the present invention provides a first planetary gear mechanism and a second planetary gear mechanism of a single pinion type, and a third planetary gear mechanism of a double pinion type! ! The ring gear of the first planetary gear mechanism, the carrier of the second planetary gear mechanism, and the carrier of the third planetary gear mechanism are always connected, and the ring gear of the first planetary gear mechanism is always connected to the carrier of the third planetary gear mechanism. The carrier, the ring gear of the second planetary gear mechanism, the sun gear of the second planetary gear mechanism, and the third. ! One of the two kings of the star gear mechanism and the sun gear is selectively connected to each other through a clutch means, and the other king is selectively connected or constantly connected to one another through another clutch means, and 1st
．． The sun gear and carrier of the one-star gear mechanism and the sun gear of the third planetary gear mechanism are selectively connected to the input member, and the output member is connected to the ring gear of the third planetary gear mechanism. be.

Function: The gear transmission of the present invention allows setting of five forward speeds and one reverse speed. That is, for example, by connecting the sun gear to the input member while the carrier of the third planetary south wheel system is fixed, the first speed, which has the largest transmission ratio in the forward speed, is set.

Further, if the sun gears of the 21st star gear mechanism and the third planetary gear mechanism are connected to the input member while the ring gear of the 21st star gear mechanism is fixed, the second forward speed is achieved. If the sun gear of the second planetary gear mechanism and the third planetary gear mechanism are connected to the input member with the sun gear of the first planetary gear R@ being fixed in place of the ring gear of the second ¥1 star gear R411, the third forward speed can be achieved. becomes. In addition, by rotating the first to third planetary gear mechanisms as a whole, the gear ratio can be set to "1".
This is the fourth gear. Furthermore, if the sun gear of the first planetary gear mechanism is fixed and its carrier is connected to the input member, and the sun gear of the third planetary gear mechanism is connected to the input shaft, the rotation of the input member is caused by the rotation of the first planetary gear mechanism. Then, the speed is increased by the third planetary gear mechanism and transmitted to the output member, resulting in the fifth speed, which is an overdrive stage. On the other hand, while the sun gears of the 211th star gear mechanism and the 31st star gear ilI are connected, the carrier of the first planetary gear mechanism and the ring gear of the 2.1st star gear system are fixed, and the When the sun gear of the structure is rotated together with the input shaft, the rotation of the input member is reversely decelerated by the first to third planetary gear mechanisms and transmitted to the output member, resulting in a reverse gear.

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 is a first planetary gear transmission.
I41 and the second planetary gear mechanism 2 are each constituted by a single pinion type planetary gear R structure, and the third planetary gear 14f43 is constituted by a double pinion type planetary gear mechanism. 3
It is constructed by connecting each element in the following way.

Zunawachi 1st M star I! The fI city organization 1 has a sun gear 1S and a ring gear 1R arranged concentrically with the sun gear 1S.
The main elements are a carrier 1C that holds a pinion gear that meshes with these gears ls and iR. Further, the second planetary gear mechanism 2 is connected to the first planetary gear mechanism 1.
Similarly, a sun gear 2S, a ring gear 2R arranged concentrically with respect to the sun gear 2S, and these gears 2S
, key ↑・su V2 that holds the pinion gear meshing with 2H
It is composed of C as the main element. On the other hand, the 3'f1 star gear [3 mainly includes a sun gear 3S, a ring gear 3R, and a carrier 3C that holds at least one pair of pinion gears disposed between these gears 3S and 3R and meshing with each other. It is structured as an element. Then, the ring gear 1R of the first planetary gear 11W1, the carrier 2C of the second planetary gear mechanism 2, and the carrier 3C of the third planetary gear mechanism 3 are connected so as to rotate as one,
Further, the carrier 1C of the first planetary gear mechanism 1 and the ring gear 2R of the second planetary gear mechanism 2 are connected to rotate together. Further, a fourth clutch means 4 is provided between the sun gear 2S of the 2'TI star gear IIf42 and the sun gear 3S of the third planetary gear mechanism 3 to selectively connect them.

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 is connected to the sun gear 3S of the third planetary gear mechanism 3. There is a first link that selectively connects the two.
A clutch means 1 is provided, and a second clutch means 2 is provided between the input shaft 4 and the carrier 1C of the first planetary gear dawn structure 1 to selectively connect the two. A third clutch means 3 is provided between the first planetary gear dawn structure 1 and the sun gear 1S to selectively connect the two.

1, K2, K3,
K4 is for selectively connecting and disconnecting each of the above-mentioned members, for example, hydraulic servo R4.
! Wet type multi-disc clutches that are engaged and released by a structure conventionally used in automatic transmissions such as 4, one-way clutches, or these wet-type multi-disc clutches and one-way clutches arranged in series or parallel. This configuration can be adopted as needed. In addition, in practical use, since there are restrictions on the arrangement of each component, it is not possible to interpose an appropriate intermediate member such as a connecting drum as a connecting member for each clutch means 1, 2, 3, and 4. Of course.

Further, a first brake means B1 selectively blocks the rotation of the ring gear 1R of the first planetary gear i-structure 1, the carrier 2C of the second TI star gear i-structure 2, and the carrier 3C of the third planetary gear mechanism 3, which are connected to each other. , are provided between these ring gears 1R or carriers 2C, 3C and a transmission case (hereinafter simply referred to as a case) 6.

Further, a second brake hand Pj82 that selectively blocks the rotation of the carrier 1C of the first Mu gear $111 and the ring gear 2R of the second planetary gear mechanism 2, which are connected to each other, is configured to prevent the carrier 1C or the ring gear 2R from rotating between the carrier 1C or the ring gear 2R and the case 6. is provided in between. And also the first planetary gear mechanism 1
A third brake means B3 is provided between the sun gear 1S and the case 6 to selectively prevent rotation of the sun gear 1S. These braking means B1, 82 . B3 is
Yuko servo R#, which is conventionally used in general automatic transmissions
1, a wet multi-disc brake, a band brake, a one-way clutch, or a combination of these.In practical use, these brake means 31°B2.83 and these Brake means 81 , 82 .

Between each element to be fixed by B3 or case 6
Of course, an appropriate connecting member may be interposed between the two.

An output shaft 5 that transmits rotation to a propeller shaft and a counter gear (each not shown) is connected to a ring gear 3R of the 3rd Y1 star gear mechanism 3.

The gear transmission configured as described above has five forward speeds and
It is possible to shift to one reverse speed, and each of these speeds is controlled by the clutch means 1 and K2.

K3, 4 and brake means 31, 32, 33
This is achieved by engaging 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 for each planetary gear 1.2
．． 3 gear ratio ρ1. ρ2. ρ3, ρ1 = 0.30
1, ρ2 = 0.361, and ρ3 = 0.304. 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.

(First Forward Speed) The sun gear 3S of the third planetary gear machine M43 is connected to the input shaft 4 while the carrier 3C of the third planetary gear machine M43 is fixed.

That is, by engaging the first clutch means 1, the third) 62
While the sun gear 3S of the star gear mechanism 3 is connected to the input shaft 4, the first brake means B1 is engaged and the third planetary gear 11 is connected.
11913 carrier 3C is fixed. In this case,
4 may be engaged with the fourth clutch means, and when 4 is not engaged with the fourth clutch means, 2, 3, or the second or third brake may be engaged with the second or third clutch means. Means 32, B3 may be engaged.

The first and fourth clutch means 1. 4 and the first brake means B1, in the third planetary gear mechanism 3, while the sun gear 3S rotates together with the input shaft 4 with the carrier 3C fixed, the ring gear 3R and the first brake means B1 are engaged. A certain output shaft 5 is decelerated relative to the input shaft 4 and rotates forward (rotation in the same direction as the input shaft 4; the same applies hereinafter).

In addition, since the sun gear 1S of the eleventh star gear mechanism 1 is not connected to the input shaft 4 and the case 6, it does not perform any particular acceleration/deceleration action, and the second planetary gear mechanism 2 , the sun gear 2S is connected to the input shaft 4, but the ring gear 2R is connected to the input shaft 4 and the case 6.
Since it is in a non-coupled state, it does not particularly participate in the acceleration/deceleration action. Therefore, in this case, substantially only the third early idle gear II43 performs the deceleration action, and as a result,
The first speed has the largest gear ratio in the progression stage, and the gear ratio is expressed as 1/ρ3, as shown in Table 1, and its specific value is 3.286. In this case, no power circulation occurs.

(Second forward speed) 2. Rotate the sun gears t'2s and 3s of the first star gear mechanism 2 and the third planetary gear mechanism 3 together with the input shaft 4, and
The ring gear 2R of the planetary gear mechanism 2 is fixed. That is, by engaging 1 with the first clutch means while 4 is engaged with the fourth clutch means, the second planetary gear mechanism 2
The sun gears 2S and 3S of the third planetary gear grip @3 are connected to the input shaft 4, and the second brake means B2 is engaged, so that the second ring gear 2R of the second planetary gear mechanism and the first planetary gear prosthetic structure 1 are connected. Fix carrier 1C. In other words, the first
In the first speed state in which the fourth clutch means Kl and the first brake means B1 are engaged, the second brake means B2 is engaged instead of the first brake means B1. Therefore, in the second planetary gear mechanism 2, since the sun gear 2S rotates together with the input shaft 4 while the ring gear 2R is fixed, the carrier 2C is decelerated with respect to the input shaft 4 and rotates in the forward direction. The signal is transmitted to the carrier 3C of the gear structure 3. As a result, the third planetary gear machine tI43
Now, since the carrier 3C rotates forward at a lower speed than the input shaft 4 while the sun gear 3S is rotating together with the input shaft 4,
The ring gear 3R is decelerated relative to the input shaft 4 and rotates in the normal direction, and this is transmitted to the output shaft 5.

In this case, the first 'l! Since the sun gear 1S of the one-star gear mechanism 1 is not connected to the input shaft 4 and the case 6, it does not perform any particular acceleration or deceleration action. Therefore, in this case, the second planetary gear 1 mechanism 2 and the third planetary gear mechanism $
3 performs a deceleration effect and decelerates the rotation of the input shaft 4 and transmits it to the output shaft 5. As shown in Table 1, the gear ratio is expressed as (1 + ρ2) / (ρ2 + ρ3), and its specific value is becomes 2.046. In this case as well, no power circulation occurs.

(Third forward speed) The sun gears 2S and 3S of the second planetary gear mechanism 41!12 and the third planetary gear R mechanism 3 are rotated together with the input shaft 4, and the sun gear 1S of the first planetary gear mechanism 1 is fixed. That is, by engaging 1 with the first clutch means while 4 is engaged with the fourth clutch means, the 1st!2nd star gear mechanism 2
．． The sun gears 2s and 3s of the and third planetary gear mechanism 3 are connected to the input shaft 4, and the third brake means B3 is engaged to fix the sun gear 1S of the first planetary gear mechanism 1. In other words, in the second speed state, the third brake means B3 is engaged instead of the second brake means B2. In this case, in the first planetary gear mechanism 1, since the sun gear 1S is fixed, its carrier 1C and ring gear 1R rotate in the forward direction, and the ring gear 1R rotates faster than the carrier IC. Further, in the 2′f1 star gear mechanism 2, the sun gear 2S rotates together with the input shaft 4, and the 111th star gear 814i1
The ring gear 2R connected to the carrier 1C of 41 is the first
It rotates forward at a lower speed than the carrier 2C connected to the ring gear 1R of the ¥1 star gear mechanism 1. Furthermore, the first planetary gear t14
In M3, while the sun gear 3S rotates together with the input shaft 4, the kitria 3C connected to the carrier 2C of the second planetary gear mechanism 2 rotates forward at a lower speed than the input shaft 4, and as a result, the ring gear t3R rotates slightly more than the input shaft 4. Rotates forward at low speed. That is, each planetary gear machine 4111.2.3 performs a deceleration action to decelerate the rotation of the input shaft 4 and transmit it to the output shaft 5, forming the forward cylinder 3M, whose speed ratio is as shown in Table 1. ρl+ρ2+ρ! It is expressed as ρ2 ρ2+ρ1ρ3+ρ1ρ2, and its specific value is 1.374. In this case too, no power circulation occurs.

(Fourth forward speed) The entire gear train consisting of the first to third TI star gear mechanisms 1, 2.3 is rotated as one. That is, at least any three of 1 to 4 are engaged with the first to fourth Clara means. In other words, in the above-mentioned third speed state, for example, the second clutch means 2 is engaged instead of the third brake means B3. Therefore, in this case, for example, 1 is applied to the first clutch means, 2 is applied to the second clutch means, and 4 is applied to the second clutch means.
When three elements 4 are engaged with the clutch means, in the second planetary gear mechanism 2, two elements, the sun gear 2S and the ring gear 2R, are connected to the input shaft 4, so that the entire structure is integrated. The sun gear 3S connected to the input shaft 4 and the carrier 3C connected to the carrier 2C of the second planetary gear mechanism 2 rotate at the same speed as the input shaft 4 in the third planetary gear mechanism 3. Since the carrier 1C is connected to the input shaft 4 in the first planetary gear mechanism 1, and the carrier 1C is connected to the input shaft 4 in the first planetary gear mechanism 1, the carrier 1C is connected to the input shaft 4, and Since the ring gear 1R connected to the carrier 2C rotates forward at the same speed as the input shaft 4, the entire ring gear 1R rotates forward at the same speed as the input shaft 4 as a unit. In other words, the entire gear train rotates as one. This situation is the same even if the three clutch means to be engaged are different, and in the end, the rotation of the input shaft 4 is transmitted as it is to the output shaft 5, and no acceleration/deceleration action occurs, and the gear ratio is changed. becomes “1”. Therefore, no power circulation occurs in this case as well.

(Fifth forward speed) While the sun gear 1S of the first star gear mechanism 1 is fixed, its carrier 1C is rotated together with the input shaft 4, and the third
The number gear 3S of the planetary gear RII3 is rotated together with the input shaft 4. That is, the third brake means B3 causes the eleventh
With the sun gear 1S of the two-star gear mechanism 1 fixed, the carrier 1C is connected to the input shaft 4 by the second clutch means 2, and at the same time, the sun gear 3S of the third star gear mechanism 3 is connected by the first clutch means 1. is connected to the input shaft 4. In other words, 1 for the first clutch means, 2 for the second clutch means,
4 in the 4th speed state where the 4th clutch means is engaged.
Third brake means B3 is engaged instead of clutch means 4. Therefore, in the first planetary gear mechanism 1, the carrier 1C rotates together with the input shaft 4 with the sun gear 1S fixed, so the ring gear 1R is accelerated with respect to the input shaft 4 and rotates in the forward direction, which is then rotated in the third planetary gear mechanism. 3 carrier 3
As a result, in the third planetary gear mechanism 3, the carrier 3C rotates forward at a higher speed than the input shaft 4 while the sun gear 3S is rotating together with the input shaft 4, so the ring gear 3R rotates with the sun gear 3S. It rotates forward at a speed intermediate to that of the carrier 3C. Therefore, the output shaft 5 connected to the ring gear 3R of the 312th star gear mechanism 3 rotates in the positive direction at a higher speed than the input shaft 4, resulting in an overtoy live stage. In addition, the second
Since the sun gear 2S of the planetary gear mechanism 2 is not connected to the input shaft 4, no particular acceleration or deceleration action is performed. The gear ratio in this case is 1/(1+ρI−ρ
Iρ3), and its specific value is 0.827. In this case too, no power circulation occurs.

(Reverse) The carrier 1C of the first planetary gear mechanism 1 and the ring gear 2R of the second planetary gear mechanism 2 are fixed, and the sun gear 2S of the 211th planetary gear mechanism II42 and the sun gear 3S of the third planetary gear mechanism #13 are fixed. In the connected state, the sun gear 1S of the 11th!21st gear mechanism 1 is rotated together with the input shaft 4. That is, by engaging the second brake means B2, the first planetary gear l1
The carrier 1C of 14111 and the ring gear 2R of the second planetary gear mechanism 2 are fixed, and 4 is engaged with the fourth clutch means to connect the second planetary gear II@2 and the third y! The sun gears 2S and 3S of the 1-star gear mechanism 3 are connected to each other, and the third clutch means 3 is engaged to connect the sun gear 1S of the 131st star gear mechanism lateral 1 to the input shaft 4. Therefore, in the first planetary gear mechanism 1, since the sun gear 1S rotates together with the input shaft 4 while the carrier 1C is fixed, the ring gear 1R
rotates in the opposite direction (rotates in the opposite direction to input shaft 4. The same applies hereinafter),
This is the second planetary gear mechanism 2 and the third planetary gear mechanism 3.
The signal is transmitted to the carriers 2C and 3C. Therefore, in the second planetary gear mechanism 2, the carrier 2C rotates in the opposite direction with the ring gear 2R fixed, so the sun gear 2S
It rotates in reverse at a higher speed than C, and this is transmitted to the sun gear 3S of the 3rd yen star gear mechanism 3. As a result, in the third planetary gear mechanism 3, the carrier 3C rotates in the opposite direction, and the sun gear 3S
rotates in reverse at a higher speed than that, so ring gear 3R rotates in reverse at a speed intermediate between that of carrier 3C and sun gear 3S. Therefore, the rotation of the input shaft 4 is reversely decelerated by the first to third planetary gears 114M1.2.3 and transmitted to the output shaft 5, resulting in a reverse gear. As shown in Table 1, the gear ratio is ρ2 (1+ρr)/ρs (1+ρ2)(ρ3X
It is expressed as (1 + ρl) 10ρ2 (1-ρ3)), and its specific value is -1,800. In this case too, no power circulation occurs.

As is clear from the above description of each gear, there is no need to perform so-called input switching in which all the elements connected to the input shaft 4 are completely disconnected when changing gears, and the Since only two methods are required,
Shift shock is not worsened, and shift control becomes easier. Further, since a torque exceeding the input torque is not applied to the sun gear of each planetary gear mechanism, the diameter of each planetary gear mechanism does not become particularly large, and therefore the entire planetary gear mechanism can be made compact. Furthermore, in the gear transmission shown in Fig. 1, in addition to the above effects, there is no power circulation at each gear stage, so it is highly efficient, and each planetary gear!
Since the gear ratio of the l-structure is set to a practically appropriate value, the overall structure can be made more compact.The gear ratio in the forward gear has a relationship close to a geometric series, which improves power performance, and in the overdrive gear, fuel efficiency and It is possible to achieve both quietness, power, and performance; durability is improved because the rotational speed of each planetary gear mechanism element and the relative rotational speed of the pinion gear are lower; and the torque applied to the clutch means is small, so it can be made more compact. effect can be obtained.

By the way, in the embodiment shown in FIG.
Sun gear 2S and sun gear 3S of the 311th star gear mechanism 3
In this invention, the sun gear 2S of the 2nd''!2 star gear mechanism 2 and the 31st
The sun gear 3S of the 11-star gear mechanism 3 may be connected at all times, and instead of this, the carrier 1C of the first planetary gear mechanism 1 and the ring gear 2R of the second planetary gear mechanism 2 may be selectively connected by a clutch means. FIG. 2 shows an example of this, and the gear transmission shown here is such that the sun gear 2S of the second planetary gear mechanism 2 and the sun gear 3S of the third planetary gear mechanism 3 are always connected, and the first planetary gear The configuration is the same as that shown in FIG. 1, except that 5 is disposed between the carrier 1C of the gear wheel 1 and the ring gear 2R of the second planetary gear mechanism 2 in the fifth clutch means that selectively connects the two. The same is true. Gear shift 1 shown in this Figure 2! Table 2 shows the working clothes for the machine.

Table 1 By the way, in each of the embodiments described above, each clutch means has one to one
5 is shown with the symbol of a multi-disc clutch, but in this invention, in order to improve quietness, fuel efficiency, and alleviate shift shock, a one-sided clutch is used in addition to the multi-disc clutch, or a multi-disc clutch is used as the clutch means. It is possible to use a combination of a plate clutch and a one-sided clutch, and for the brake means 81 and B2.83, in addition to the multi-plate brake shown in each of the above embodiments,
A one-way clutch, a band brake, or a combination of these can be used. Modifications of such latch means and brake means include those described in the Mei 11I figures and drawings attached to the patent application No. 1767270/1983 filed by the present applicant and the application form 221670/1983. can be adopted.

As described in detail, the present invention includes two sets of single pinion type planetary gear mechanisms and one set of double pinion type planetary gear mechanisms, and can set five forward speeds and one reverse speed. The present invention is a gear transmission, and can change speed by switching and controlling two engaging means, and since there is no so-called input switching during the speed change, there is no risk of worsening the speed change shock. ,
A gear transmission with easy speed change control can be obtained. In addition, since torque exceeding the input torque is not applied to each sun gear, there are no members that need to be made particularly large in diameter in order to maintain strength and durability, so the overall configuration can be made compact. .

[Brief explanation of drawings]

FIGS. 1 and 2 are skeleton diagrams showing embodiments of the present invention, respectively. 1.2.3...Planetary gear mechanism, 1S, 2S, 3S.
...Sun gear, IC, 2C, 3C...Carrier, I
R, 2R, 3R...Ring gear, 4...Input shaft, 5
...output shaft, Kl, 2, 3, 4, 5...clutch means. Applicant: Toyota Motor Corporation Representative Patent Attorney: Hisashi Takeshi (one idiot)

Claims (1)

[Claims] It includes a first planetary gear mechanism and a second planetary gear mechanism of single pinion type, and a third planetary gear mechanism of double pinion type, and the ring gear of the first planetary gear mechanism, the carrier of the second planetary gear mechanism, and the third planetary gear mechanism. The carrier of the mechanism is always connected to the carrier, and the carrier of the first planetary gear mechanism and the ring gear of the second planetary gear mechanism, the sun gear of the second planetary gear mechanism, and the sun gear of the third planetary gear mechanism. one of the two is selectively coupled via a clutch means, and the other two are selectively coupled or constantly coupled via another clutch means, and the first planet For an automatic transmission characterized in that the sun gear and carrier of the gear mechanism and the sun gear of the third planetary gear mechanism are selectively connected to an input member, and the output member is connected to the ring gear of the third planetary gear mechanism. Gear transmission.