JPH0536660B2 - - Google Patents

Description

[Detailed description of the invention]

(Industrial Application Field) The present invention relates to a planetary gear train that is often used as an auxiliary transmission in automatic transmissions installed in vehicles such as automobiles, and in particular, a planetary gear train that enables multi-stage formation including an overdrive gear stage. It's about columns. (Prior Art) Conventionally, as a planetary gear train for an automatic transmission, a Simpson gear train consisting of two simple planetary gear sets is used to constitute an auxiliary transmission with four forward speeds.
There is one manufactured by GM in the US shown in the figure. This planetary gear train consists of two planetary gear sets _G1 and _G2.
S ₁ and S ₂ , internal gears R ₁ and R ₂ and pinion carriers PC ₁ and PC ₂ , input shaft I, output shaft O, four clutches Cl ₁ , Cl ₂ , Cl ₃ and Cl ₄ ,
Two brakes Br ₁ and Br ₂ and two one-way clutches OWC ₁ and OWC ₂ are connected as shown in the figure. Therefore, clutch Cl ₁ ,
By selectively operating Cl ₂ , Cl ₃ and Cl ₄ , brakes Br ₁ and Br ₂ , and one-way clutches OWC ₁ and OWC ₂ as shown in the table below (○ marks operate),
It is possible to obtain a shift action of 4 forward speeds and 1 reverse speed.

[Table] (Problems to be Solved by the Invention) However, in the case of the planetary gear train of the conventional automatic transmission described above, power is not transferred between the planetary gear sets G ₁ and G ₂ in the second gear, which is often used during normal driving. Because of this, the power transmission efficiency decreases, and sun gear S ₁ rotates at high speed in 4th gear (planetary gear assembly).
When the reduction ratio of G ₁ and G ₂ are both 0.5, the rotation speed of input shaft I is 2.5 times), so the strength of the member connected to sun gear S ₁ and the strength of the bearing that directs this must be determined with durability in mind. The problem was that it needed to be made larger. On the other hand, due to the demand for energy conservation in automobiles, the auxiliary gear shifting devices of automatic transmissions are becoming more multi-staged, including overdrive gears, in order to make more use of the efficient engine speed range and increase transmission efficiency through lock-up. However, it has been impossible to further increase the number of stages in the conventional planetary gear train described above due to its structure. (Means for Solving the Problems) The present invention proposes a planetary gear train that is developed from the Simpson gear train to meet the above-mentioned multi-stage requirements and does not cause the above-mentioned problems. Specifically, a first planetary gear set includes a first sun gear, a first internal gear, and a first pinion carrier, and a second planetary gear set includes a second sun gear, a second internal gear, and a second pinion carrier.
The third planetary gear set includes a third sun gear, a third internal gear, and a third pinion carrier, and the first internal gear is integrated with the input shaft and the third pinion carrier is integrated with the output shaft. At the same time, the first planetary gear set can be appropriately interlocked by the first clutch, the second sun gear can be appropriately fixed by the first brake, and the second sun gear can be appropriately coupled to the first sun gear by the second clutch, and the first pinion The carrier can be coupled to the second pinion carrier as appropriate by the third clutch, and to the second internal gear as appropriate by the fourth clutch, and the second internal gear is integrally coupled to the third internal gear, and the second internal gear is integrally coupled to the third internal gear. The sun gear can be fixed as appropriate by the second brake, and can be coupled to the second pinion carrier as appropriate by the fifth clutch. (Function) In the planetary gear train of the present invention configured as described above,
The operation of the fourth clutch causes the first forward speed; the actuation of the fourth clutch and the first brake causes the second forward speed; the actuation of the first and fourth clutches and the first brake causes the third forward speed; The fourth forward speed is obtained by actuation of the third and fifth clutches, the fifth forward speed is obtained by actuation of the first, third, and fifth clutches and the first brake; Reverse movement can be achieved by applying the second brake. Furthermore, the fourth and fifth
The above-mentioned forward movement is achieved by the operation of the clutch and the first brake.
The 2' speed is obtained between the 3rd forward speed and the 3rd forward speed, and the 3'th speed is obtained between the 3rd forward speed and the 4th forward speed by the operation of the 3rd and 5th clutches and the first brake. . The reduction ratio of the fifth forward speed is determined by the tooth ratio of the second planetary gear train and the tooth ratio of the third planetary gear train, and the speed is always an overdrive speed. Therefore, the auxiliary transmission device of the automatic transmission can be made to have more stages including an overdrive gear stage. Furthermore, since no power is circulated between the planetary gear sets at any of the speeds, the power transmission efficiency during running can be improved. Furthermore, since there are no gears or members that rotate particularly high compared to the rotational speed of the input shaft and output shaft, the durability of the rotating members can be improved without particularly considering strength. (Example) Hereinafter, an example 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, in which 1 is the first planetary gear set, 2 is the second planetary gear set, and 3 is the second planetary gear set.
1 and 2 respectively show third planetary gear sets, and these planetary gear sets 1 to 3 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 includes a first internal gear 1
_R , a first sun gear _1S , a first pinion _1P meshing with these, and a first pinion carrier _1C rotatably supporting this pinion, and a second planetary gear set 2 and a second planetary gear set. Similarly, 3 also
second and third internal gears _2R , _3R ;
3rd sun gear _2S , _3S , 2nd and 3rd pinion 2
_P , 3 _P and second and third pinion carriers 2 _C , 3 _C
It consists of The first internal gears _1R of the planetary gear sets 1 to 3 as described above are integrally connected to the input shaft 4, and the third pinion carrier _3C is integrally connected to the output shaft 5, respectively, and the first planetary gear sets 1 The first clutch _C1 allows appropriate interlocking. In this embodiment, the first internal gear 1 _R and the first sun gear 1 _S are connected by the first clutch C ₁ to connect the first internal gear 1 R and the first sun gear 1 S.
The planetary gear set 1 is interlocked, that is, the elements are connected so that all the elements rotate together.
Alternatively, as shown in FIG. 3, the first internal gear and the first pinion carrier may be connected by a first clutch, or as shown in FIG. The first planetary gear set 1 may be interlocked by being coupled by a clutch. The first sun gear _1S and the second sun gear _2S can be appropriately coupled by the second clutch C2, and the first sun gear _{1S is} connected to the second sun gear _2S via the one-way clutch O/C1 _. Input shaft 4
The second sun gear _2S can also be fixed as appropriate by the first brake _B1 . The first pinion carrier 1 _C is the third clutch C ₃
The fourth clutch _C4 can be connected to the second _internal gear _2R , and the second internal gear _2R can be connected to the third internal gear _3R. Join together. Further, the second pinion carrier _2C and the third sun gear _3S can be connected appropriately by the fifth clutch _C5 , and the second pinion carrier _2C can be connected to the third sun gear _3S via the one-way clutch O/C2. _S
The third sun gear _3S can also be fixed as appropriate by a second brake, and can be connected to the input shaft 4 by a one-way clutch O/C _3. It is possible to rotate only in the same direction. The operation of the above embodiment will be explained next. The planetary gear train shown in FIG. 1 includes first to fifth clutches _C1 to _C5.
By selectively operating the first and second brakes B ₁ and B ₂ in combinations as shown in the table below, it is possible to provide five forward speeds and one reverse speed as shown in the table. can. In addition, the ○ mark in the same table indicates operation.
(○) indicates something that operates but does not participate in power transmission. Further, α ₁ is the ratio of the number of teeth of the first sun gear 1 _S to the first internal gear 1 _R , α ₂ is the ratio of the number of teeth of the second sun gear 2 S to the second internal gear 2 _R , and α ₃ is the ratio of the number of teeth of the second sun gear 2 _S to the first internal gear 1 R, Null Gear 3 3rd for _R
The tooth number ratio of the sun gear _3S is shown, and examples of the reduction ratio are numerical values when α ₁ =0.45, α ₂ =0.4, and α ₃ =0.4.

【table】

[Table] When selecting 1st speed in forward automatic shift driving D range, operate the 4th clutch _C4 . At this time, the power transmitted from the input shaft 4 to the first internal gear _1R rotates the first pinion carrier _1C ,
This rotation is transmitted to the second internal gear _2R and the third internal gear _3R via the fourth clutch _C4 , and the rotation of the third internal gear _3R is transmitted to the third internal gear 3R.
Since the sun gear _3S is prevented from rotating by the one-way clutch O/ _C3 , it is taken out from the output shaft 5 via the third pinion carrier _3C . On the other hand, the second
The rotation of the internal gear _2R is prevented from rotating by the second pinion carrier _2C via the one-way clutches O/C ₂ and O/C ₃ .
_S , is transmitted to the first sun gear _1S via the one-way clutch O/ _C1 to reverse the rotation. Therefore, a first forward speed with a reduction ratio of (1+α ₁ +α ₁ /α ₂ )(1+α ₃ ) is obtained. When selecting the second forward speed, the first brake _B1 is operated in addition to the case of the first speed. At this time, the first brake _B1 fixes the second sun gear _2S , and the first brake _B1 fixes the second sun gear 2S, and the first brake
Since the sun gear 1 _S is prevented from reversing, the rotation input to the first internal gear 1 _R is applied to the first pinion carrier 1 _C while the first sun gear 1 _S is fixed.
is transmitted to. This rotation is transmitted to the third internal gear _3R via the fourth clutch _C4 , and since the third sun gear _3S is prevented from rotating by the one-way clutch O/ _C3 , the rotation is transmitted to the third internal gear 3R via the fourth clutch C4. The rotation of _R is taken out from the output shaft 5 via the third pinion carrier _3C . Therefore, the reduction ratio (1+
A second forward speed of α ₁ )(1+α ₃ ) can be obtained. When selecting the third forward speed, the first clutch _C1 is actuated in addition to the case of the second speed. At this time, the first clutch _C1 interlocks the first planetary gear set 1, so the rotation of the input shaft 4 continues as it is.
The rotation of the third internal gear _3R is transmitted through the clutch _C4 to the third internal gear _3R .
Since the sun gear _3S is prevented from rotating by the one-way clutch O/ _C3 , the signal is read out from the output shaft 5 via the third pinion carrier _3C . Therefore, the third forward speed with a reduction ratio of 1+α ₃ is obtained. In addition, the first
Brake B ₁ is not involved in power transmission, but
If the second pinion carrier _2C , which is also not involved in power transmission, stops, the second sun gear _2S will reverse at high speed, so it is better to keep it operating. When selecting the fourth forward speed, the fourth clutch _C4 is deactivated from the third speed state, and the third clutch _C3 and fifth clutch _C5 are activated instead. At this time, the first planetary gear set 1 is interlocked by the first clutch _C1 , and the rotation of the input shaft 4 is directly transmitted to the second pinion carrier _2C via the third clutch _C3 . This rotation is transmitted through the second internal gear _2R to the third internal gear _3R.
Also, the third sun gear _3S is connected via the fifth clutch _C5 .
and is taken out from the output shaft 5 via the third pinion carrier _3C . At this time, the torque reaction force applied to the output shaft 5 is applied to the second pinion carrier _2C and the second
It works to speed up the rotation of the second sun gear _2S via the internal gear _2R , but the second sun gear _2S rotates faster than each element of the first planetary gear set 1 due to the one-way clutch O/C ₁ . Since this is prevented, the rotation is the same as that of the first sun gear _1S . Therefore, the second sun gear _2S and the second pinion carrier _2C
The third sun gear _3S and the third internal gear _3R also rotate in the same manner to interlock the second planetary gear set 2, thereby interlocking the third planetary gear set 3. Therefore, the reduction ratio 1
4th forward speed can be obtained. When selecting the fifth forward speed, the first brake _B1 is operated in addition to the case of the fourth speed. At this time, the first planetary gear set 1 is interlocked by the first clutch _C1 , and the rotation of the input shaft 4 is directly transmitted to the second pinion carrier via the third clutch _C3 . This rotation is caused by the second internal gear 2.
It is transmitted to the third internal gear _3R via _R , but the speed is increased because the second sun gear _2S is fixed by the first brake _B1 . The rotation of the second pinion carrier _2C is also directly transmitted to the third sun gear _3S via the fourth clutch _C4 . Therefore, the speed of the third pinion carrier _3C is increased to rotate the output shaft 5. Therefore, reduction ratio (1+α ₃ )/
(1 + α ₂ + α ₃ ) overdrive (reduction ratio is 1
A fifth forward speed is obtained with a transmission of less than When selecting reverse gear, the 1st, 2nd, and 5th
Activate clutches C ₁ , C ₂ , C ₅ and second brake B ₂ . At this time, the first planetary gear set ₁ is interlocked by the first clutch C1, and the rotation of the input shaft 4 is directly transmitted to the second sun gear _2S . Since the second pinion carrier _2C is fixed by the second brake _B2 via the fifth clutch _C5 , this rotation is reversely transmitted to the second internal gear _2R . The second internal gear _2R rotates the output shaft 5 via the third internal gear _3R and third pinion carrier _3C . Therefore, the reduction ratio -
A reverse gear position of (1+α ₃ )/α ₂ can be obtained. When selecting 1st to 4th speeds in the forward engine brake running L range, the first and second clutches
C ₁ , C ₂ , fourth and fifth clutches C ₄ , C ₅ and first,
By selectively operating the second brakes B ₁ and B ₂ in combinations as shown in the table above, each gear stage can be obtained. In this case, the one-way clutch that was involved in transmitting power from the input shaft 4 to the output shaft 5 in the forward automatic transmission range is replaced by the operation of a clutch installed parallel to the one-way clutch, so that the force in the opposite direction is transmission is becoming possible. Thereby, when reverse driving force is applied to the drive wheels of the vehicle, this force is transmitted from the output shaft 5 to the input shaft 4, making it possible to apply engine braking. By selectively operating the clutches and brakes in the combinations shown in the table above, the second forward speed and the third forward speed can be achieved.
2' speed between the 3rd and 4th forward speeds.
It is also possible to obtain a 3' speed between the two speeds. As described above, in this embodiment, a gear ratio extremely close to that of a manual five-speed transmission for an automobile can be obtained. Furthermore, when used in combination with an engine with a narrow power band, the 2' speed and the 3' speed can be added to form a 7-speed transmission. Next, FIG. 2 shows the relationship of rotational speeds among the respective elements 1 _R to 3 _R , 1 _S to 3 _S , and 1 _C to 3 _C of the planetary gear sets 1 to 3 in the above embodiment. In the figure, the vertical axis represents the rotation speed as 0 in the center, normal rotation at the top, and reverse rotation at the bottom, and the distance ratio between each element is expressed as the tooth number ratio α ₁ ~
The horizontal axis corresponds to α ₃ , and when the distance between the sun gear and the pinion carrier is set to 1, the distance between the pinion carrier and the internal gear becomes α. The rotational speeds of the elements coupled to each other are then shown on a common vertical line. In the figure, the output rotation speed at each gear stage is determined as follows. That is, in the first forward speed and the 2' forward speed, the rotation speed of the first internal gear _1R , which is the input element, is a, and in the first speed, the rotation speed of the second pinion carrier _2C and the third sun gear _3S is Since the rotational speed of the first and second sun gears is 0 at 0 and 2' speeds,
The intersection points F ₁ and F ₂ ′ of the straight line connecting these corresponding points and the vertical line representing the rotation speed of the third pinion carrier 3 _C , which is the output element, are the output at 1st speed and 2′ speed, respectively. It will show the number of rotations. In addition, in 2nd speed, the 3rd internal gear _3R is
The rotation speed is the same as pinion carrier 1 _C , but the 3rd
Since the rotation speed of sun gear _3S is 0, the intersection point _F2 between the straight line connecting these points and the vertical line representing the rotation speed of the third pinion carrier _3C indicates the output rotation speed in 2nd gear. become. In the third speed, the rotation speed of the third internal gear _3R is a, which is equal to the first internal gear _1R , but the rotation speed of the third sun gear _3S is 0, so
The intersection point _F3 between the straight line connecting these points and the vertical line representing the rotation speed of the third pinion carrier _3C indicates the output rotation speed in the third speed. In addition, in the 3' speed, the second pinion carrier _2C rotates at the same speed as the first pinion carrier _1C in the 2' speed, and the second sun gear _2S has a rotation speed of 0.
A point indicating the rotation speed of the third internal gears 2 _R and 3 _R is determined. Since the third sun gear _3S rotates at the same time as the second pinion carrier, the intersection point _F3 ' between the straight line connecting these points and the vertical line representing the rotation speed of the third pinion carrier _3C is the third sun gear 3S. It shows the output rotation speed at 'speed. In 4th gear, all elements rotate together, so a straight line extended horizontally from the point indicating the rotation speed a of the first internal gear 1 _R and the third pinion carrier 3 _C
The intersection point _F4 with the vertical line representing the rotational speed indicates the output rotational speed in the fourth gear. In addition, in the fifth speed, the rotation speed of the second pinion carrier _2C is a, which is equal to that of the first internal gear, and the rotation speed of the second sun gear _2S is 0, so that the second and third internal gears _2R , 3 The point indicating the rotation speed of _R is determined. Since the third sun gear _3S rotates at the same time as the second pinion carrier, the intersection point _F5 between the straight line connecting these points and the vertical line representing the rotation speed of the third pinion carrier _3C is the fifth gear. This indicates the output rotation speed. In the reverse gear, the rotation speed of the second sun gear _2S is equal to that of the first internal gear, and the rotation speed of the second pinion carrier _2C is 0, so that the second and third internal gears _2R , 3 The point indicating the reversed rotation speed of _R is determined. And third sun gear 3
Since the rotation speed _S is 0, the intersection point R between the straight line connecting these points and the vertical line representing the rotation speed of the third pinion carrier _3C indicates the reverse gear. As is well known, the coupling pattern between two planetary gear sets is such that when the sun gears are coupled together and the internal gears are coupled together, when the sun gears are coupled together and the pinion carriers are coupled together, the coupling pattern between the internal gears and the pinion carriers is different. In the case of a predetermined pattern such as when two planetary gear sets are combined, power circulation occurs between the planetary gear sets, but in the planetary gear train of this embodiment, each element shown in the alignment chart and table of As is clear from the coupling relationship, no coupling pattern occurs in which power circulation occurs between the two planetary gear sets at any of the speeds. Therefore, according to the planetary gear train of this embodiment, power transmission efficiency can be improved. (Effects of the Invention) Thus, the planetary gear train of the present invention is an advanced version of the Simpson gear train with one simple planetary gear set added, so it has a reasonable configuration and an overdrive that improves fuel efficiency during high-speed running. By increasing the number of gears including gears, it is possible to configure an auxiliary transmission for an automatic transmission having a gear ratio extremely close to that of a manual five-speed automobile transmission. Furthermore, when used in combination with an engine with a narrow power band or a low output engine, it can also be used as a 7-speed transmission. Therefore, the efficient engine rotation range can be used extensively, and the power transmission efficiency can be increased by locking up, so that the effect of improving energy efficiency can be obtained. Furthermore, the fact that power circulation between the planetary gear sets does not occur at all gears also contributes to increasing power transmission efficiency. Furthermore, the durability of the rotating parts has been improved by eliminating gears and other parts that rotate at a particularly high speed compared to the rotational speed of the input and output shafts, which has the effect of increasing reliability as an automatic transmission. It also has.

[Brief explanation of the drawing]

FIG. 1 is a half-skeleton diagram showing an embodiment of the planetary gear train of the automatic transmission of the present invention, and FIG. 2 is a rotational speed diagram of the planetary gear components in the planetary gear train.
FIGS. 3 and 4 are main part skeleton diagrams showing other examples of the present invention, and FIG. 5 is a half skeleton diagram showing a conventional planetary gear train. 1...First planetary gear set, 1 _R ...First internal gear, 1 _C ...First pinion carrier, 1 _S ...
...First sun gear, 2...Second planetary gear set, 2 _R ...
...Second internal gear, 2 _C ...Second pinion carrier, 2 _S ...Second sun gear, 3...Third planetary gear set, 3 _R ...Third internal gear, 3 _C ...
…3rd pinion carrier, 3 _S …Sun gear, 4
... Input shaft, 5 ... Output shaft, C ₁ ... First clutch, C ₂ ... Second clutch, C ₃ ... Third clutch,
C ₄ ... 4th clutch, C ₅ ... 5th clutch, B ₁
...First brake, B ₂ ...Second brake, O/
C ₁ , O/C ₂ , O/C ₃ ...One-way clutch.

Claims (1)

[Claims] 1 A first planetary gear set consisting of a first sun gear, a first internal gear, and a first pinion carrier;
a second planetary gear set consisting of a second sun gear, a second internal gear and a second pinion carrier;
a third planetary gear set including a sun gear, a third internal gear, and a third pinion carrier; 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
The planetary gear set can be appropriately interlocked by the first clutch, the second sun gear can be properly fixed by the first brake, and can be connected to the first sun gear by the second clutch, and the first pinion carrier can be connected by the third clutch. The second internal gear can be coupled to the second pinion carrier as appropriate and the second internal gear as appropriate by the fourth clutch, and the second internal gear can be integrally coupled to the third internal gear, and the third sun gear can be coupled as appropriate to the second internal gear by the second brake. A planetary gear train for an automatic transmission, characterized in that it can be fixed and can be connected to a second pinion carrier as appropriate by a fifth clutch.