JPS6145139A - Planetary gear train of automatic transmission gear - Google Patents

Abstract

PURPOSE:To facilitate multistage shifting of a gear, by a method wherein 3 planetary gear trains are coupled to the same shaft, an input shaft is coupled to the internal gear of a first planetary gear train, and a pinion carrier to a third planetary gear train. CONSTITUTION:In a transmission gear employing a planetary gear mechanism, 3 planetary gear trains 1, 2, and 3 are coupled to the same shaft, an input shaft 4 is coupled to an internal gear 1R of a first planetary gear train, and an output shaft 5 to a pinion carrier 3c of a third planetary gear trains. The first planetary gear train can be interlocked by means of a first clutch C1, and a pinion carrier 1c of the first gear train can be coupled to a pinion carrier 2c of a second gear train by means of a third clutch C3, and can be coupled to an internal gear 2R of the second gear trains by means of a fourth clutch C4.

Description

Detailed Description of the Invention (Industrial Application Field) The present invention relates to a planetary gear train constituting a power train of an automatic transmission, and particularly to a planetary gear train that enables multi-stage formation.0 (Prior art) Conventionally, a planetary gear train for an automatic transmission uses two planetary gear sets to form a four-speed forward automatic transmission, and is manufactured by GM, USA, as shown in FIG. 5, for example.

This planetary gear train consists of two planetary gear sets G, sun gears S and S of G2, internal gear R and R3,
And pinion carrier PO work and PO□, input work,
Clutch C1 construction with 0.4 output shaft.

012, 018 and OJ, two brake BR works
・BIB R2 and two one-way clutches OWO□
The planetary gear train of this automatic transmission is connected to clutch C! and 0WO2 as shown in the figure. ,.

ai, ai8 and C1, brake BR work and BR
,, and one-way clutch oWO construction and OWO2,
By selectively operating as shown in the table below (O mark is activated), four forward speeds and one reverse speed can be obtained.

(Problems to be Solved by the Invention) However, in the planetary gear train of the conventional automatic transmission as described above, in the 1st, 2nd and 8th speeds, the rotational force of the input work is applied to the clutch ○, One way clutch OW
The input power is input manually to the sun gear S through the clutch CI, and when moving in reverse, the rotational force of the input work is applied to the sun gear S through the clutch CI.
The first problem is that the stress acting on the teeth of the sun gear S and S2, which have relatively small diameters, becomes large, which limits the allowable input torque. Also, the fourth
At high speed, the sun gear S0 is approximately 2.
Since it rotates at five times the rotational speed, there was a second problem in that it was necessary to consider the strength of the members connected to the sun gear S0 and the durability of the bearings that support it. A part of the rotational force inputted from the input work circulates between the idling gear set G and 08, reducing the power transmission efficiency, and is also preferable from the viewpoint of the durability of the idling gear set G and G. There was a third problem: there was no such thing.

On the other hand, there is a tendency for automatic transmissions to be required to have more gears, but the conventional planetary gear train described above cannot meet this demand.0 (Means for solving the problem) The present invention develops the Simpson gear train. In this way, we have proposed a planetary gear train that can meet the above-mentioned multi-stage requirements without causing the above-mentioned eight problems. a second planetary gear set including a second sun gear, a second internal gear, and a second pinion carrier; a third sun gear, a third internal gear, and a third planetary gear set;
A third planetary gear set consisting of a pinion carrier is coaxially provided, the first internal gear is integrally connected to the input shaft, the third pinion carrier is integrally connected to the output shaft, and the first planetary gear set is appropriately connected to the first clutch by the first clutch. The second sun gear can be interlocked, the second sun gear can be appropriately fixed by the first brake, and the second sun gear can be connected to the first sun gear by the second clutch, and the first pinion carrier can be connected to the second pinion carrier by the third clutch as appropriate. If the second internal gear can be connected to the second internal gear as appropriate by the fourth clutch, the second internal gear can be integrally connected to the third sun gear, and the second pinion carrier can be connected to the third internal gear as appropriate by the fifth clutch. In both cases, the third internal gear can be appropriately fixed by the second brake.

(Function) In this configuration, the first forward speed is changed by the operation of the fourth clutch.
The second forward speed is activated by the operation of the fourth clutch and the first brake.
The third forward motion is activated by the operation of the first and fourth clutches and the first brake.
4th forward speed is achieved by the operation of the 4th and 5th clutches and the first brake; 5th forward speed is achieved by the operation of the 3rd and 5th clutches and the first brake; The 6th forward speed is activated by the operation of 'ig1, 3rd, 5th clutch
7th forward speed can be obtained by operating the brake, and 1st, 2nd,
Reverse movement can be achieved by operating the fifth clutch and second brake, and further multi-stage operation is possible.

In any gear stage, the rotation of the input shaft is not input to the first, second, or third sun gear, which increases the allowable input torque. There is no member that rotates at a higher speed than the input shaft, there is no need to pay special consideration to the strength of the rotating member and the durability of its bearing, and there is no need to give any special consideration to the strength of the rotating member and the durability of its bearing. First, it is possible to improve the power transmission efficiency and the durability of each planetary gear set.

(Example) Hereinafter, embodiments of the present invention will be described in detail based on the drawings.

FIG. 1 shows an embodiment of the planetary gear train of the present invention, and 1 in the figure shows the first gear train.
A planetary gear set, 2 indicates a second planetary gear set, and 8 indicates a third planetary gear set, are arranged coaxially between the input shaft 4 and the output shaft 5 in order from the input shaft 4 side.

The first planetary gear set 1 is a first internal gear IR.

1st sun gear IS1 1st pinion IP meshing with these
and a first pinion carrier 10 that rotatably supports this pinion, and the second planetary gear set 2 and the third planetary gear set 3 similarly have second and third internal gears 2.
R, 8R, second and third sun gears 2S, 8S, and second,
3rd pinion 2P.

3P and the second and third pinion carriers 20 and 80 are integrally connected to the input shaft 4, and the third pinion carrier 8o is integrally connected to the output shaft 5, respectively, and the first planetary gear Set 1 can be interlocked as needed by the first clutch C. In addition, in the case of figure $1, this first clutch C0 connects the first internal gear IR and the Nl sun gear 1s, and is interlocked so that all the elements of the first planetary gear set 1 rotate together. However, instead of this, the first internal gear IR and the first pinion carrier IC may be interlocked by combining the first internal gear IR and the first pinion carrier IC as shown in FIG. 3, or the first pinion carrier 10 may be interlocked as shown in FIG. It is also possible to interlock the first planetary gear set 1 by combining the first sun gear 1s and the second sun gear 1s.Then, the second sun gear 2s can be fixed as appropriate by the M1 brake B, and the second clutch C2 can be used as appropriate. 3@1 The first sun gear 1s can be coupled to the sun gear 1s, and the first sun gear 1s can be rotated relative to the second sun gear 2s in the same direction as the input shaft 4 through the one-way clutch 0/C. Carrier IC is third clutch C8
It can be coupled to the second hinion carrier 2C as appropriate via
2nd internal gear 2R as appropriate via the 4th clutch C1
can be combined with Note that the second internal gear 2R is integrally coupled to the third sun gear 8S. The second pinion carrier 20 can further be coupled to the third internal gear 3R by the fifth clutch C5, and can be rotated relative to the third internal gear 8R only in the same direction as the input shaft 4 by the one-way clutch o/C2. ◇ The third internal gear 8R can be fixed appropriately by the second brake B2, and the one-way clutch o
/C8 allows rotation only in the same direction as the input shaft 4, and prevents rotation in the opposite direction.

The operation of the above embodiment will be explained next. The planetary gear train shown in Fig. 1 can be constructed by selectively operating the first to fifth clutches C0 to O, and the first and second brakes B, B2 in combinations shown in the table below. It is possible to provide seven forward speeds and one reverse speed with the reduction ratio as shown.

In this table, the ○ mark indicates the operation, α is the ratio of the number of teeth of the first sun gear IS to the first internal gear IR, α2 is the ratio of the number of teeth of the second sun gear 2s to the second internal gear 2R, and α is 3rd for 3rd internal gear 3R
This is the tooth ratio of sun gear 8S, and an example of the reduction ratio is α, = 0.
45, α = 0.4, α, = 0.8, the numerical values are 0.Also, in the table, (◯) indicates those that operate but do not participate in power transmission.

・When selecting 1st speed in the forward automatic transmission range (D), operate the 4th clutch C1. At this time, the input shaft 4
The power transmitted from the first internal gear IR to the first internal gear IR is
The pinion carrier IC is rotated, and this rotation is transmitted to the third sun gear 8S via the fourth clutch C2.Then, this rotation is transmitted to the third sun gear 8S through the fourth clutch C2. The rotation is taken out from the output shaft 5 via the 3-pinion carrier 8C. On the other hand, the rotation reaching the 4th clutch O6 is also transmitted to the 2nd internal gear 2R, and the one-way clutch 0102゜01
Since the second pinion carrier 20 is prevented from rotating through the pinion 08, the rotation of the second internal gear 2R is caused by the second pinion 2P and the second sun gear 2S.

It is transmitted to the first sun gear IS via the one-way clutch O101 and reverses it.
Speed is obtained n0 When selecting the second forward speed, the first brake B is also operated in addition to the case of the first speed described above. At this time, the first brake B1 fixes the second sun gear 2S and prevents the first sun gear IS from reversing via the one-way clutch O10, so that the rotation input to the first internal gear IR is transferred to the first pinion. IP is transferred to the first pinion carrier 10 while being transferred around the non-rotating first sun gear IS. This rotation is transferred to the third sun gear 8 via the fourth clutch O4.
Since the third internal gear 8R is prevented from rotating due to the one-way clutch O/G, the third sun gear 8S rotates the output shaft 5 via the third pinion carrier 8C. Therefore, when selecting the third forward speed, the first clutch C1 is activated in addition to the case of the second speed described above.
0 interlocks the first planetary gear set 1, and the input shaft 4
The rotation of is transmitted as it is to the third sun gear 8S via the fourth clutch C4, and since the rotation of the third internal gear 8R is prevented by the one-way clutch O10, this sun gear is transmitted to the output shaft via the third pinion carrier 8C. 5
can be rotated. Note that the first brake B1 is activated, but since this brake is not involved in power transmission, it can remain inactive. 1 brake B
0 is conveniently operated in this gear position.

When selecting 4th forward speed, change from the above 3rd speed to 1st speed.
Clutch C is deactivated and fifth clutch C5 is activated instead. At this time, first, second, and sun gears Is, 2
3 is made non-rotating as in the case of the second speed, so the same rotation as in this case is transmitted to the fourth clutch C.
Rotation is transmitted from the clutch C1 to the third sun gear 8S on one hand, and the second internal gear 2R and second pinion 2P on the other hand.

2nd pinion carrier 20. The signal is transmitted to the third internal gear 8R through the fifth clutch C5. Therefore, the third
The output shaft 5 is rotated via the third pinion gear rear 8C due to the rotation difference between the sun gear 8S and the third internal gear 3R, so that the reduction ratio can be changed.

When selecting the 5th forward speed, the 4th speed is changed from the above 4th speed state.
Clutch C6 is deactivated and third clutch C is used instead.
Activate 8. At this time, as in the case of the fourth speed, the rotation output from the first pinion carrier 10° is transferred to the third clutch C8, the second pinion carrier 20. This signal is transmitted to the third internal gear 8R via the fifth clutch C6, and also to the third sun gear 8S via the third clutch C8, second pinion 2P, and second internal gear 2R. In this case, the rotation difference between the third internal gear 8R and the third sun gear 8S causes the third pinion carrier 8C to
A fifth forward speed in which the output shaft 5 is rotated can be obtained through the rotation of the output shaft 5.

When it is desired to select the 6th forward speed, the first brake B is deactivated from the state of the 5th speed, and the first clutch C0 is activated instead. At this time, the first planetary gear set 1 is interlocked and all elements are IR.

Is, 10 rotated at the same speed as the human powered shaft 4, and
The rotation of the first pinion carrier 10 is the third clutch OB,
2nd pinion carrier 20. The transmission is directly transmitted to the third internal gear 8R via the fifth clutch C5, and the first
The rotation of sun gear IS is transmitted to third sun gear 8S via one-way clutch 010□, second sun gear 2B, second pinion 2P, and second internal gear 2R, and is transmitted to third sun gear 8S at the same speed and in the same direction as third internal gear 3R. Therefore, the sixth forward speed with a reduction ratio of 1 can be obtained.

When selecting the seventh forward speed, the first brake B1 is operated in addition to the case of the sixth speed. At this time, the first planetary gear set 1 is interlocked, and the rotation of the input shaft 4 is continued as it is with the third clutch 08%, second pinion carrier 20. It is transmitted to the third internal gear 8R via the fifth clutch O5. During this time, the second pinion 2P rolls around the fixed second sun gear 2S, and rotates the third sun gear 8S in the opposite direction to the third internal gear 8R via the second internal gear 2R. Therefore, the output shaft 5 can obtain the seventh forward speed with an increased speed ratio).

When selecting the reverse gear, the first, second, and fifth clutches are operated, and the second brake B2 is operated. At this time, the third internal gear 8R is fixed by the second brake B, and the third internal gear 8R is fixed by the second brake B. Since the second pinion carrier 20 is fixed via the clutch C5, the rotation that reaches the first internal gear IR from the input shaft 4 is transferred to the first clutch O, the second clutch J, and the second sun gear 28. 2nd pinion 2P.

2nd internal gear 2R, 3rd sun gear 8S.

The rotation is reversed via the third pinion ap and the first pinion carrier 8c and transmitted to the output shaft 5 to obtain a reverse gear position of 1+α0, with a reduction ratio of 1112.

α2・α8 When selecting 1st to 6th speeds in the forward engine brake running (L) range, the first to fifth clutches C to 0.
The selection can be made by selectively operating the first and second brakes B, B, in combination as shown above, but in these cases, the one-way clutch O10, 0102
,0108 are not activated, and the drive wheel of the vehicle
In other words, when the output shaft 5 reversely drives the input shaft 4, that is, the engine, the reverse driving force can be transmitted to the engine and the engine brake can be applied. In the above embodiment, the planetary gear set 1 ~Each element IR of 8~
The relationship of rotational speeds among 8R, Is to ss, and la to 80 is as shown in FIG. In Fig. 2, the rotational speeds of mutually connected elements are expressed by a common vertical axis (high rotation in the upper part of the figure), and the ratio of the distance between these vertical axes corresponds to the tooth number ratio α□ to α8. , the relationship between the rotational speeds of each element when the rotational speed of the input shaft 4 is a is shown. In the figure, 1 to 5 represent the output rotational speeds at the first to seventh forward speeds, respectively, and R is the output rotational speed at the reverse gear.

The output rotation speed at each of these gears is determined as follows.

That is, in the first forward speed and the fourth forward speed, the first internal gear I
The rotation speed of R is the same as the input rotation speed a, and the rotation speed of the third internal gear 80 is O1 in the first gear, and the second rotation speed in the fourth gear.
The rotation speed of sun gear 2S is 0. A line connecting these corresponding points and the third pinion carrier 3o which is the output element
The intersection point 1.4 with the vertical axis indicating the rotational speed indicates the output rotational speed at the first and fourth speeds. In the second speed, the first pinion carrier IC rotates at the same speed as the second internal gear 2R in the fourth speed, and the third internal gear 8
Although R is prevented from rotating, the intersection point 2 between the line connecting these points and the vertical axis indicating the rotation speed of the third pinion carrier 8C indicates the output rotation speed in the second speed.

In the third speed, the rotational speed of the first pinion carrier 1o is the same as the input rotational speed a, and the third internal gear 8R is prevented from rotating, so the line connecting these points and the The intersection point 8 with the vertical axis indicating the rotation speed of the 3-pinion carrier 80 indicates the output rotation speed at the third speed. In the fifth speed, the second pinion carrier 2C rotates at the same speed as the first pinion carrier IC in the fourth speed, and the second sun gear 2S is prevented from rotating, so the line connecting these points , the intersection point 6 with the vertical axis indicating the rotation speed of the third pinion carrier 8G indicates the output rotation speed at the fifth speed. In the 6th speed, all the elements rotate integrally with the input shaft 4, so a line indicating this and the 3rd. pinion carrier 80
The intersection point 6 with the vertical axis indicating the rotation speed is the output rotation speed in the 6th speed.0 In the 7th speed, the rotation speed of the second pinion carrier 2C and the third internal gear 8R is the same as the input rotation speed a. Since the first and second sun gears are prevented from rotating,
A line connecting these points and the second pinion carrier 8
The intersection point 7 with the vertical axis indicating the rotation speed of C becomes the output rotation speed in the seventh speed.

In the reverse gear stage, the second pinion carrier 2Cj and the third
Since the internal gear 8R is fixed and the rotational speeds of the first and second sun gears Is and 28 are the same as the input rotational speed a, the line connecting these points and the rotational speed of the third pinion carrier 80 are The intersection point R with the vertical axis indicates the output rotation speed in the reverse gear position.

(Effects of the Invention) In this way, the planetary gear train of the present invention has a configuration that is developed from the Simpson gear train by adding one set of cruising gear sets 1 as described above, so that only one set of planetary gear sets is added. Although it has a compact configuration, it can be multi-staged up to forward speed.
s, 2S, and 38, and the allowable input torque can be increased. In addition, other than the output shaft 6 and the third pinion carrier aC that rotates together with it, the second pinion carrier rotates at a higher speed than the input shaft 4. As is clear from the figure, there is no need to pay special consideration to the strength of the rotating member and the durability of its bearing. Furthermore, it is clear from the above that no circulation of power occurs between the 11th second and third planetary gear sets 1 to 8, which increases the power transmission efficiency and improves the durability of each planetary gear set. can be done.

Incidentally, as is clear from the above table, the reduction ratio of the first forward speed can be made sufficiently large, and since this cannot be increased, conventional torque converters for increasing torque are used for power transmission of automatic transmissions. Although it was essential to the system, the planetary gear train of the present invention makes it possible to even omit the torque converter for the above-mentioned reasons, and in this respect as well, the automatic transmission can be made compact and inexpensive.

[Brief explanation of the drawing]

Fig. 1 is a half-skeleton diagram showing an embodiment of the planetary gear train of the present invention, Fig. 2 is a rotational speed diagram of the planetary gear components in the planetary gear train, and Figs. 3 and 4 are respectively the invention of the invention. Fig. 5 is a half-part skeleton diagram showing a conventional planetary gear train. 1...First planetary gear set IR...First internal gear IS...First sun gear IC...First pinion carrier 2...Second planetary gear set 2R...Second internal Gear 2S...Second sun gear 2C.
...Second pinion carrier 8...Third planetary gear set
8R...Third internal gear 8S...Ha sun gear 3C...Third binion carrier! ,. 4...Input shaft 5...Output shaft 0□...
・1st clutch C3...2nd clutch C...3rd clutch C6...4th clutch C...5th clutch B work...1st brake B,...2nd brake

Claims (1)

[Claims] 1. A first planetary gear set including a first sun gear, a first internal gear, and a first pinion carrier; a second planetary gear set including a second sun gear, a second internal gear, and a second pinion carrier; and a third planetary gear set. A sun gear, a third internal gear, and a third planetary gear set consisting of a third pinion carrier are coaxially provided, and the first internal gear is an input shaft,
The third pinion carrier is integrally connected to the output shaft, the first planetary gear set can be interlocked as appropriate by the first clutch, the second sun gear can be appropriately fixed by the first brake, and the second sun gear can be appropriately interlocked by the second clutch. 1 sun gear, the 1st pinion carrier can be connected to the 2nd pinion carrier by the 3rd clutch, and the 2nd internal gear by the 4th clutch, and the 2nd internal gear can be connected to the 3rd sun gear. An automatic transmission characterized in that the second pinion carrier can be appropriately connected to the third internal gear by a fifth clutch, and the third internal gear can be appropriately fixed by a second brake. planetary gear train.