JP3167361B2 - Planetary gear transmission - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a planetary gear transmission in which two sets of planetary gear trains are coaxially arranged between an input member and an output member.

[0002]

2. Description of the Related Art Planetary gear transmissions are widely used for automatic transmissions of automobiles and the like. Conventional planetary gear transmissions often include two sets of planetary gears integrally combined, such as a Ravigneaux gear train, a Simpson gear train, and the like, and in this case, generally up to four forward speeds. Met. However, there is a demand for multi-speed gears for the purpose of improving running characteristics and the like. For this reason, transmissions having five or more forward speeds have been proposed and put into practical use.

In order to cope with such multi-stage gears, the number of planetary gear trains may be increased. For example, three or five sets of planetary gear trains are used to obtain the fifth to sixth gears. Various transmissions have been conventionally proposed (for example, see Japanese Unexamined Patent Publication No.
9-222644, JP-A-1-320362 and the like. However, if the number of planetary gear trains is increased, the number of component parts increases accordingly, leading to an increase in manufacturing cost, weight, and size. There is a problem that the number of stages can be increased by using two sets of planetary gear trains. A transmission having such a configuration has also been proposed. For example, JP-A-2-256
Japanese Patent Application Publication No. 944 discloses a planetary gear transmission in which a fifth forward speed is obtained using a Ravigneaux gear train. Japanese Patent Application Laid-Open No. 64-12160 discloses a planetary gear transmission in which six forward speeds are obtained by using two sets of double pinion type planetary gear trains.

[0004]

[0003] Such a transmission is known as 2
Since the transmission is configured using a set of planetary gear trains, the transmission can be made compact and lightweight. However, in the case of a Ravigneaux gear train, there is a problem that the configuration itself is complicated. Further, in the case where the transmission using the Ravigneaux gear train is used to increase the number of gears, in some speed gears (for example, the highest gear, the lowest gear, and the reverse gear), one of the elements is considerably larger than the input rotation. There is a problem of rotating at high speed, that is, a problem of over-rotation of any element.

In the case of the transmission disclosed in Japanese Patent Application Laid-Open No. 64-12160, two sets of double pinion type planetary gear trains are arranged in parallel. It is simple, and it can be said that it is easy to reduce the size and weight of the transmission. However, in this transmission, at the time of shifting between adjacent speed stages, it is necessary to temporarily release all currently engaged engagement means (clutch or brake) and to engage another engagement means. However, there is a problem that a complicated shift cannot be avoided and the shift control becomes complicated. In this transmission, for example, when shifting from the first speed to the second speed, both the clutch C1 and the brake B1 that are engaged in the first speed are released, and the clutch C2 and the brake B2 that are different from these are released.
Are engaged. In this case, there is a problem that the control is complicated because the engagement / disengagement control of a total of four engagement means is required. Further, there is a possibility that a state in which any of the engagement means is not engaged during the shift and becomes neutral and the engine speed is increased, and in order to prevent this, the engagement / disengagement control of each engagement means is performed. There is a problem that timing is difficult.

The present invention has been made in view of the above-described problems, and it is possible to set five or more forward gears by two sets of planetary gear trains.
It is an object of the present invention to provide a planetary gear transmission having a configuration in which the structure of the transmission can be simplified, reduced in size and weight, and the shift control is easy.

[0007]

Means for Solving the Problems To achieve such an object, a planetary gear transmission according to a first aspect of the present invention includes a first and a second planetary gear train in a power transmission path from an input member to an output member. Are arranged coaxially, and a first element constituting a first planetary gear train is removably connected to an input member via a first clutch means, and a third and a fourth elements are formed.
The first planetary gear train constituting the second planetary gear train is
And the second element is removably connected to the first element and the second element.
A second element forming the planetary gear train is removably connected to the input member via the second clutch means, and a third element forming the first planetary gear train forms a second planetary gear train. The first and second elements, which are always connected to the third element and are always connected to the output member, and constitute the second planetary gear train, can be fixedly held via first and second brake means, respectively. Has become. Further, in the planetary gear transmission according to the second aspect of the present invention, the first element forming the first planetary gear train is removably connected to the input member via the first clutch means, and the third element is connected to the third element. And a second element constituting the first planetary gear train is removably connected to the first and second elements constituting the second planetary gear train via the fourth clutch means, respectively. The third member constituting the first planetary gear train is always connected to the input member via the clutch means so as to be freely disengageable, and the third element constituting the second planetary gear train. The first and second elements which are connected and constitute the second planetary gear train can be fixedly held through the first and second brake means, respectively.

[0008]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Preferred embodiments of the present invention will be described below with reference to the drawings. According to the configuration of the velocity diagram including the planetary gear transmission according to the present invention, it is classified into three types of groups, and these groups are classified into Type I and Type I, respectively.
Called I, Type III. Where type I and II
Only I is the planetary gear transmission according to the invention, type II
Belongs to the prior art, but all of them will be described below for each group.

Type I The type I group is a transmission whose speed diagram is configured as shown in FIG. As shown in the diagram, the transmission includes a first planetary gear train G1 including three elements E11, E12, and E13 (each corresponding to a sun gear, a carrier, and a ring gear), and three transmissions. Element E2
1, E22, E23 (each is a sun gear, carrier,
(Corresponding to any of the ring gears). In this diagram, for each planetary gear train, a vertical line indicates the component, the length of the vertical line indicates the number of rotations, and the interval between the vertical lines indicates the number of teeth of the sun gear among the components and the ring gear. Are shown in proportion to the reciprocal of the number of teeth.

The elements E11 and E13 are connected to the input member 1 via the second clutch K2 and the first clutch K1, respectively.
And the elements E12 and E23 are connected to each other and to the output member 5. Further, the elements E11 and E22 are removably connected via a third clutch K3, and the element E22 can be fixedly held by the first brake B1. Elements E11 and E11
21 is connected via a fourth clutch K4 so as to be freely engaged and disengaged, and the element E21 can be fixedly held by a second brake B2. As can be seen from this configuration, in the transmission belonging to the type I group, one element E11 of the first planetary gear train G1 is replaced by two elements E22 and E21 of the second planetary gear train and clutches K3 and K4, respectively. Are connected so as to be freely detachable.

Here, if the two elements of the first planetary gear train G1 and the two elements of the second planetary gear train G2 are connected, the two planetary gear trains G1 and G2 become a planetary gear train that operates in conjunction with each other. The velocity diagram can be combined and shown as shown in FIG. However, in this case, the elements E12 and E23
, The element E11 is connected to the elements E21 and E22 via the fourth and third clutches K4 and K3.
Can be connected to each other, and therefore the velocity diagrams in the united state differ according to the connection.

First, the third clutch K3 controls the element E11.
FIG. 2A shows a velocity diagram in a case where the element E22 and the element E22 are connected. The vertical lines in the velocity diagram are referred to as first to fourth rotating members in order from the left. In this case, as shown in Table 1, the element E21 constitutes a first rotating member, the elements E11 and E22 constitute a second rotating member, the elements E12 and E23 constitute a third rotating member, and E1
3 constitutes a fourth rotating member.

[0013]

[Table 1]

On the other hand, the element E11 is controlled by the fourth clutch K4.
FIG. 2B shows a velocity diagram in the case where the element E21 and the element E21 are connected. The vertical lines in this velocity diagram are also
4th rotating member-. Here, the second planetary gear train G
The interval between the vertical lines indicating the three elements 2 is different from that in FIG. 2A, but as described above, the interval between the vertical lines is proportional to the reciprocal of the number of teeth between the sun gear and the ring gear. The ratio of the vertical line spacing is not changed. That is,
The ratio e1 (= m1 / n1) of the intervals m1 and n1 of the three elements E21, E22 and E23 in FIG. 2A is shown in FIG.
M2, n between three elements E21, E22, E23 in
2 is equal to the ratio e2 (= m2 / n2). In this case, as shown in Table 2, the elements E11 and E21 constitute a first rotating member, the element E22 constitutes a second rotating member, and the elements E12 and E23 constitute a third rotating member. The element E13 forms a fourth rotating member.

[0015]

[Table 2]

Next, a description will be given of a specific structure which is realized as a type I transmission. FIG. 3 shows a first type I transmission.
2 shows a skeleton according to the example of FIG. Note that this skeleton shows only the portion above the rotation center line. This transmission has first and second planetary gear trains G1 and G2 arranged coaxially and in parallel. Each planetary gear train
First and second sun gears S1 and S2 located at the center, and first and second planetary pinions P meshing with the first and second sun gears S1 and S2 and revolving while rotating around them.
, P2, and the first and second carriers C1 and C2 that rotatably hold the pinion and rotate the same as the revolution of the pinion.
And first and second ring gears R1 and R2 having internal teeth that mesh with the pinion. The first planetary gear train G1 is a double pinion type gear train. As shown in the figure, the first pinion P1 has two pinions P11 and P11.
12 are provided.

The first sun gear S1 is detachably connected to the input shaft 1 via a first clutch K1, and is connected to the first carrier C1.
Is removably connected to the input shaft 1 via a second clutch K2. The first carrier C1 further includes a third
The clutch is removably connected to the second carrier C2 and the second sun gear S2 via the clutch K3 and the fourth clutch K4. The first ring gear R1 and the second ring gear R2 are directly connected and are directly connected to the output gear 5. Further, the second carrier C2 and the second sun gear S2 can be fixedly held by the first brake B1 and the second brake B2, respectively.

As described above, each element (sun gears S1, S2
, Carriers C1 and C2, and ring gears R1 and R2),
In a transmission configured by connecting the input shaft 1 and the output gear 5, by engaging and disengaging control of the first to fourth clutches K1 to K4 and the first and second brakes B1 and B2 as shown in Table 3, , 5th forward speed (LOW, 2ND, 3RD, 4T
H, 5TH) and the first reverse speed (REV). As shown in Table 3, each of the five forward speeds is set by engaging a plurality of engagement means (clutches and brakes). When shifting between adjacent speeds, at least one gear is required. The shift is performed with the engagement means engaged. Therefore, there is no possibility that all the engagement means are released at the time of this shift and a neutral state occurs, and the shift control is easy.

[0019]

[Table 3]

The forward five speeds (LOW, 2ND,
3RD, 4TH, 5TH) and the first reverse speed (REV) are set by engaging and disengaging control of the first to fourth clutches K1 to K4 and the first and second brakes B1, B2 as shown in Table 4. Can also be done. Also in this case, the shift between the adjacent speed stages is always performed while at least one engagement means is engaged, and in this shift, all the engagement means are released and a neutral state occurs. There is no danger and the shift control is easy. Table 3 and Table 4 differ only in the engagement clutch and brake for setting the second speed (2ND).

[0021]

[Table 4]

FIG. 4 is a speed diagram showing the speed relationship of each element in the transmission having the above-described structure. Based on the speed diagram, the reduction ratio at each speed stage will be described. In the speed diagram of FIG. 4, a speed diagram of the first planetary gear train G1 including the first sun gear S1, the carrier C, and the first ring gear R1, and the speed diagram including the second sun gear S2, the carrier C, and the second ring gear R2. And the speed diagram of the second planetary gear train G2. Also in this diagram, each vertical line indicates its component, and the length of the vertical line corresponds to the number of rotations. The interval between the vertical lines is proportional to the reciprocal of the number of teeth of the sun gear and the reciprocal of the number of teeth of the ring gear.

In the case of the velocity diagram of the first planetary gear train G1 located on the upper side in the figure, three vertical lines correspond to the first carrier C1, the first ring gear R1, and the first sun gear S1 in order from the left. Correspondingly, the length of each vertical line in the upward direction indicates the rotational speed n in the forward direction. The distance "a1" between the vertical line indicating the first sun gear S1 and the vertical line indicating the first carrier C1 corresponds to the reciprocal (= 1 / Zs1) of the number of teeth Zs1 of the first sun gear S1, and the first carrier Vertical line indicating C1 and first ring gear R1
Corresponds to the reciprocal (= 1 / Zr1) of the number of teeth Zr1 of the first ring gear R1. For this reason,
For example, when the first sun gear S1 is rotated at the rotation speed n and the first carrier C1 is fixed and held, the rotation speed n at the intersection of the line A connecting the points indicating both states and the vertical line indicating the first ring gear R1.
a is the number of revolutions of the first ring gear R1.

On the other hand, the lower second planetary gear train G2
Similarly, the three vertical lines correspond to the second sun gear S2, the second carrier C2, and the second ring gear R2 in order from the left. The distance "a2" between the vertical line indicating the second sun gear S2 and the vertical line indicating the second carrier C2 corresponds to the reciprocal (= 1 / Zs2) of the number of teeth Zs2 of the second sun gear S2,
The distance "b2" between the vertical line indicating the second carrier C2 and the vertical line indicating the second ring gear R2 corresponds to the reciprocal (= 1 / Zr2) of the number of teeth Zr2 of the second ring gear R2. Therefore, for example, the second sun gear S2 is fixedly held, and the second ring gear R
2 is rotated at the rotation speed n, the rotation speed nb at the intersection of the line B connecting the points indicating both states and the vertical line indicating the second carrier C2
Is the rotation speed of the second carrier C2.

It should be noted that the first planetary gear train G1 and the second planetary gear train G2 differ in the position of the vertical line representing the sun gear and the ring gear with respect to the vertical line representing the carrier. This is the first
This is because the planetary gear train G1 is of a double pinion type, whereas the second planetary gear train G2 is of a single pinion type. That is, in the double pinion type, the sun gear and the ring gear rotate in the same direction, but in the single pinion type, the ring gear rotates in the opposite direction to the sun gear.

Next, the speed reduction ratio for each speed stage is determined from the speed diagram. Here, the case where the engagement control of the clutch and the brake is performed as shown in Table 3 will be described. First,
In the case of LOW, the first clutch K1 and the fourth clutch K
4 and the first brake B1 are engaged. Here, the fourth
Since the clutch K4 is engaged, the speed diagram is shown in FIG.
And it becomes as shown in FIG. Table 5 shows the relationship between each element and the rotating member. In this case, the first sun gear S1 is driven to rotate at the same rotational speed n0 as the input shaft 1, and the second carrier C2 is fixedly held. Therefore, the point representing the state of the first sun gear S1 and the second carrier C
The rotation speed n1 at the intersection of the dotted line L1 connecting the point indicating the state 2 and the vertical line indicating the first and second ring gears R1 and R2 is the first and second ring gears R1 and R2, that is, the output gear 5 And the ratio of the input and output rotational speeds (= n0 / n1) is the reduction ratio of the transmission.

[0027]

[Table 5]

In the case of the second speed, while the first clutch K1 and the first brake B1 remain engaged, the fourth clutch K
4 is disengaged, and the third clutch K3 is engaged instead. Thus, instead of the fourth clutch K4, the third clutch
Since the clutch K3 is engaged, the speed diagram is shown in FIG.
And it becomes as shown in FIG. Table 6 shows the relationship between each element and the rotating member. In this case, the first sun gear S1 is rotationally driven at the same rotational speed n0 as the input shaft 1 while the first and second carriers C1 and C2 are fixedly held. In this case, the rotation speed n2 of the intersection of the dotted straight line L2 and the vertical lines indicating the first and second ring gears R1 and R2 is the rotation speed of the output gear 5.

[0029]

[Table 6]

In the case of the third speed, the first brake B1 is released while the first and third clutches K1 and K3 remain engaged, and the second brake B2 is engaged instead. Also in this case, the velocity diagram is as shown in FIG. 6 in the type of FIG. 2A, and the relationship between each element and the rotating member is as shown in Table 6. Thereby, in a state where the second sun gear S2 is fixedly held,
The first sun gear S1 is rotationally driven at the same rotational speed n0 as the input shaft 1. Therefore, the rotation speed n3 of the intersection of the dotted straight line L3 and the vertical lines indicating the first and second ring gears R1 and R2 is the rotation speed of the output gear 5.

In the case of the fourth speed, the second brake B2 is released and the second clutch K2 is engaged while the first and third clutches K1 and K3 are engaged. Also in this case, the velocity diagram is as shown in FIG. 6 in the type of FIG. 2A, and the relationship between each element and the rotating member is as shown in Table 6. At this time, the third clutch K3 may be released. In this case, the entire planetary gear trains G1 and G2 integrally rotate together with the input shaft 1. In the diagram, all the elements rotate the same as the input shaft 1, and the horizontal straight line L4 and the first and second
Number of rotations n4 at the intersection with the vertical lines indicating ring gears R1 and R2
(= N0) is the rotation speed of the transmission output gear 5. In addition,
When the third clutch K3 is released, all the elements of the first planetary gear train G1 and the second ring gear R2 of the second planetary gear train G2 rotate integrally with the input shaft 1, and the second sun gear S2 and the second carrier C2 is in a free state.

In the case of the fifth speed, the first clutch K1 is released while the second and third clutches K2 and K3 remain engaged, and the second brake B2 is engaged instead. Also in this case, the velocity diagram is as shown in FIG. 6 in the type of FIG. 2A, and the relationship between each element and the rotating member is as shown in Table 6. Thereby, in a state where the second sun gear S2 is fixedly held,
The first and second carriers C1 and C2 are rotationally driven at the same rotational speed n0 as the input shaft 1. Therefore, the rotation speed n5 of the intersection of the dotted straight line L5 and the vertical lines indicating the first and second ring gears R1 and R2 is the rotation speed of the output gear 5.

In the case of the reverse gear, the second clutch K
2. The fourth clutch K4 and the first brake B1 are engaged. In this case, since the fourth clutch K4 is engaged, the velocity diagram is of the type shown in FIG. 2B, as shown in FIG. 5, and the relationship between each element and the rotating member is as shown in Table 5. . Here, the first carrier C1 and the second sun gear S2
Are driven by the same rotation as the input shaft 1, and the second carrier C2 is fixedly held. In this case, the rotation speed nR at the intersection of the dotted straight line LR and the vertical lines indicating the first and second ring gears R1 and R2 (negative value, indicating that the rotation is opposite to the input rotation) is obtained. This is the number of revolutions of the output gear 5.

In this transmission, the following reduction ratio can be set as an example of a specific reduction ratio. LOW: 3.720 2ND: 1.720 3RD: 1.191 4TH: 1.00000 5TH: 0.735 REV: -2.778 However, the reciprocal of the number of teeth of the first sun gear S1 in the first planetary gear train G1 and The ratio of the first ring gear R1 to the reciprocal of the number of teeth is (1 / Zs1) :( 1 / Zr1) = 1.0: 0.72, and the second sun gear S2 in the second planetary gear train G2.
The ratio of the reciprocal of the number of teeth to the reciprocal of the number of teeth of the second ring gear R2 is (1 / Zs2) :( 1 / Zr2) = 1.0: 0.36.

Next, a second example of the type I transmission is shown in FIG.
And FIG. This transmission has a double pinion type first planetary gear train G1 and a single pinion type second planetary gear train G1.
And a planetary gear train G2. The first sun gear S1 is removably connected to the input shaft 1 via a second clutch K2, and the first carrier C1 is removably connected to the input shaft via a first clutch K1. The first sun gear S1 further includes a third clutch K3 and a fourth clutch K
4 and is connected to the second carrier C2 and the second sun gear S2 so as to be freely detachable. First ring gear R1 and second ring gear R1
The ring gear R <b> 2 is directly connected to the output gear 5. Further, the second carrier C2 and the second sun gear S2 can be fixedly held by the first brake B1 and the second brake B2, respectively. Thus, in the transmission of the present example, the first sun gear S1 of the first planetary gear train G1 is connected to the second sun gear S1 via the clutches K3 and K4, respectively.
It is removably connected to the second carrier C2 and the second sun gear S2 of the planetary gear train G2.

In this transmission, the engagement and disengagement control of the first to fourth clutches K1 to K4 and the first and second brakes B1 and B2 is performed as shown in Table 3 or Table 4, so that the fifth forward speed (LOW) is established. , 2ND, 3RD, 4TH, 5TH) and the first reverse speed (REV). In the case of the type I transmission, clutch / brake disengagement control is performed as shown in Table 3 or Table 4, and each speed stage is set. The speed diagram of this transmission is as shown in FIG. 8, and three vertical lines indicating each element of the first planetary gear train G1 are the first sun gear S1 and the first sun gear S1 from the left.
Three vertical lines corresponding to the ring gear R1 and the first carrier C1 and indicating each element of the second planetary gear train G2 are the second vertical lines from the left.
Sun gear S2, second carrier C2, second ring gear R2
Corresponding to Note that the reduction ratio for each speed stage can be determined in the same manner as in the transmission according to the first example (similar to FIGS. 5 and 6), and therefore, the description thereof will be omitted below.

A third example of a type I transmission is shown in FIGS. This transmission includes a single pinion type first planetary gear train G1 and a double pinion type second planetary gear train G2. The first sun gear S1 is the second
It is detachably connected to the input shaft 1 via the clutch K2,
The first ring gear R1 is removably connected to the input shaft 1 via a first clutch K1. The first sun gear S1 further includes a third clutch K3 and a fourth clutch K
4, the second ring gear R2 and the second carrier C2
Is removably connected to. First carrier C1 and second carrier
The sun gear S2 is directly connected to the output gear 5 as well. The second ring gear R2 and the second carrier C2 can be fixedly held by the first brake B1 and the second brake B2, respectively. Thus, in the transmission of the present example, the first sun gear S1 of the first planetary gear train G1 is connected to the second sun gear S1 via the clutches K3 and K4, respectively.
The planetary gear train G2 is removably connected to the second ring gear R2 and the second carrier C2. The speed diagram of this transmission is as shown in FIG. 10, and three vertical lines indicating each element of the first planetary gear train G1 are, from the left, a first sun gear S1, a first carrier C1, and a first ring gear R1. Correspondingly, three vertical lines indicating each element of the second planetary gear train G2 are, from the left, a second carrier C2, a second ring gear R2, and a second sun gear S.
Corresponds to 2.

A fourth example of a type I transmission is shown in FIGS. This transmission has a single pinion type first planetary gear train G1 and a single pinion type second planetary gear train G1.
And a planetary gear train G2. The first sun gear S1 is removably connected to the input shaft 1 via a second clutch K2, and the first ring gear R1 is removably connected to the input shaft 1 via a first clutch K1. First sun gear S1
Further includes a second carrier C2 and a second sun gear S via a third clutch K3 and a fourth clutch K4, respectively.
2 is detachably connected. The first carrier C1 and the second ring gear R2 are directly connected and are directly connected to the output gear 5. Further, the second carrier C2 and the second sun gear S2 can be fixedly held by the first brake B1 and the second brake B2, respectively. Thus, in the transmission of the present example, the first planetary gear train G1 has the first
The sun gear S1 is detachably connected to the second carrier C2 and the second sun gear S2 of the second planetary gear train G2 via the clutches K3 and K4, respectively. The speed diagram of this transmission is as shown in FIG. 12, and three vertical lines indicating each element of the first planetary gear train G1 are, from the left, a first sun gear S1, a first carrier C1, and a first ring gear R1. Correspondingly, three vertical lines indicating each element of the second planetary gear train G2 are, from the left, a second sun gear S2, a second carrier C2, and a second ring gear R.
Corresponds to 2.

FIGS. 13 and 14 show a fifth example of the type I transmission. This transmission has a single pinion type first planetary gear train G1 and a single pinion type second planetary gear train G1.
And a planetary gear train G2. The first sun gear S1 is removably connected to the input shaft 1 via a first clutch K1, and the first ring gear R1 is removably connected to the input shaft 1 via a second clutch K2. First ring gear R
1 is further removably connected to the second carrier C2 and the second sun gear S2 via a third clutch K3 and a fourth clutch K4, respectively. The first carrier C1 and the second ring gear R2 are directly connected and the output gear 5
It is directly connected to. Further, the second carrier C2 and the second carrier C2
The sun gear S2 includes a first brake B1 and a second
It can be fixedly held by the brake B2. As described above, in the transmission of this embodiment, the first ring gear R1 of the first planetary gear train G1 is engaged with and disengaged from the second carrier C2 and the second sun gear S2 of the second planetary gear train G2 via the clutches K3 and K4, respectively. They are freely connected. The speed diagram of this transmission is as shown in FIG. 14, and three vertical lines indicating each element of the first planetary gear train G1 are the first ring gear R from the left.
1, three vertical lines corresponding to the first carrier C1 and the first sun gear S1 and indicating each element of the second planetary gear train G2 are, from the left, the second sun gear S2, the second carrier C2, and the second ring gear R2. Corresponding.

FIGS. 15 and 16 show a sixth example of the type I transmission. This transmission has a single pinion type first planetary gear train G1 and a single pinion type second planetary gear train G1.
And a planetary gear train G2. The first sun gear S1 is removably connected to the input shaft 1 via a second clutch K2, and the first ring gear R1 is removably connected to the input shaft 1 via a first clutch K1. First sun gear S1
Is further removably connected to the second carrier C2 and the second ring gear R2 via a third clutch K3 and a fourth clutch K4, respectively. The first carrier C1 and the second sun gear S2 are directly connected and are directly connected to the output gear 5. Further, the second carrier C2 and the second ring gear R2 are connected to the first brake B1 and the second
It can be fixedly held by the brake B2. As described above, in the transmission of this embodiment, the first sun gear S1 of the first planetary gear train G1 is engaged with and disengaged from the second carrier C2 and the second ring gear R2 of the second planetary gear train G2 via the clutches K3 and K4, respectively. They are freely connected. The speed diagram of this transmission is as shown in FIG. 16, and three vertical lines indicating each element of the first planetary gear train G1 are the first sun gear S from the left.
1, corresponding to the first carrier C1, the first ring gear R1,
Three vertical lines representing each element of the second planetary gear train G2 correspond to the second ring gear R2, the second carrier C2, and the second sun gear S2 from the left.

FIGS. 17 and 18 show a seventh example of the type I transmission. This transmission has a single pinion type first planetary gear train G1 and a single pinion type second planetary gear train G1.
And a planetary gear train G2. The first sun gear S1 is removably connected to the input shaft 1 via a first clutch K1, and the first ring gear R1 is removably connected to the input shaft 1 via a second clutch K2. First ring gear R
1 is further removably connected to the second carrier C2 and the second ring gear R2 via a third clutch K3 and a fourth clutch K4, respectively. First carrier C1
And the second sun gear S2 are directly connected and the output gear 5
It is directly connected to. Further, the second carrier C2 and the second carrier C2
The ring gear R2 can be fixedly held by the first brake B1 and the second brake B2, respectively. Thus, in the transmission of the present example, the first ring gear R1 of the first planetary gear train G1 is connected to the second carrier C2 and the second carrier C2 of the second planetary gear train G2 via the clutches K3 and K4, respectively.
The ring gear R2 is detachably connected to the ring gear R2. The speed diagram of this transmission is as shown in FIG. 18, and the first planetary gear train G
3 correspond to the first ring gear R1, the first carrier C1, and the first sun gear S1 from the left, and the three vertical lines representing the respective elements of the second planetary gear train G2 are as follows. ,
From the left side, the second ring gear R2, the second carrier C2, the second
Corresponds to sun gear S2.

An eighth example of the type I transmission is shown in FIGS. This transmission comprises a double pinion type first planetary gear train G1 and a single pinion type second planetary gear train G2. The first sun gear S1 is removably connected to the input shaft 1 via a first clutch K1, and the first carrier C1 is removably connected to the input shaft 1 via a second clutch K2. The first carrier C1 is further connected to a second carrier C2 and a second ring gear R via a third clutch K3 and a fourth clutch K4, respectively.
2 is detachably connected. The first ring gear R1 and the second sun gear S2 are directly connected and are directly connected to the output gear 5. Further, the second carrier C2 and the second ring gear R2 are connected to the first brake B1 and the second
It can be fixedly held by the brake B2. As described above, in the transmission of this embodiment, the first carrier C1 of the first planetary gear train G1 is engaged with and disengaged from the second carrier C2 and the second ring gear R2 of the second planetary gear train G2 via the clutches K3 and K4, respectively. They are freely connected. The speed diagram of this transmission is as shown in FIG. 20, and three vertical lines indicating each element of the first planetary gear train G1 are the first carrier C from the left.
1, corresponding to the first ring gear R1, the first sun gear S1,
Three vertical lines representing each element of the second planetary gear train G2 correspond to the second ring gear R2, the second carrier C2, and the second sun gear S2 from the left.

A ninth example of a type I transmission is shown in FIGS. This transmission includes a single pinion type first planetary gear train G1 and a double pinion type second planetary gear train G2. The first sun gear S1 is removably connected to the input shaft 1 via a first clutch K1, and the first ring gear R1 is removably connected to the input shaft 1 via a second clutch K2. First ring gear R
1 is further removably connected to the second ring gear R2 and the second carrier C2 via a third clutch K3 and a fourth clutch K4, respectively. First carrier C1
And the second sun gear S2 are directly connected and the output gear 5
It is directly connected to. The second ring gear R2 and the second carrier C2 can be fixedly held by the first brake B1 and the second brake B2, respectively. Thus, in the transmission of the present embodiment, the first ring gear R1 of the first planetary gear train G1 is engaged with and disengaged from the second ring gear R2 and the second carrier C2 of the second planetary gear train G2 via the clutches K3 and K4, respectively. They are freely connected. The speed diagram of this transmission is as shown in FIG. 22, and the first planetary gear train G
3 correspond to the first ring gear R1, the first carrier C1, and the first sun gear S1 from the left, and the three vertical lines representing the respective elements of the second planetary gear train G2 are as follows. ,
From the left side, the second carrier C2, the second ring gear R2, the second
Corresponds to sun gear S2.

A tenth example of a type I transmission is shown in FIGS. This transmission includes a double pinion type first planetary gear train G1 and a double pinion type second planetary gear train G2. The first sun gear S1 is removably connected to the input shaft 1 via a first clutch K1, and the first carrier C1 is removably connected to the input shaft 1 via a second clutch K2. The first carrier C1 is further provided with a second ring gear R2 and a second carrier C via a third clutch K3 and a fourth clutch K4, respectively.
2 is detachably connected. The first ring gear R1 and the second sun gear S2 are directly connected and are directly connected to the output gear 5. The second ring gear R2 and the second
The carrier C2 includes a first brake B1 and a second brake B1, respectively.
It can be fixedly held by the brake B2. As described above, in the transmission of the present embodiment, the first carrier C1 of the first planetary gear train G1 is engaged with and disengaged from the second ring gear R2 and the second carrier C2 of the second planetary gear train G2 via the clutches K3 and K4, respectively. They are freely connected. The speed diagram of this transmission is as shown in FIG. 24, and three vertical lines indicating each element of the first planetary gear train G1 are the first carrier C from the left.
1, corresponding to the first ring gear R1, the first sun gear S1,
Three vertical lines representing each element of the second planetary gear train G2 correspond to the second carrier C2, the second ring gear R2, and the second sun gear S2 from the left.

An eleventh example of a type I transmission is shown in FIGS. This transmission has a double pinion type first planetary gear train G1 and a single pinion type second planetary gear train G1.
And a planetary gear train G2. The first sun gear S1 is removably connected to the input shaft 1 via a second clutch K2, and the first carrier C1 is removably connected to the input shaft 1 via a first clutch K1. The first sun gear S1 is further connected to a second carrier C2 and a second ring gear R via a third clutch K3 and a fourth clutch K4, respectively.
2 is detachably connected. The first ring gear R1 and the second sun gear S2 are directly connected and are directly connected to the output gear 5. Further, the second carrier C2 and the second ring gear R2 are connected to the first brake B1 and the second
It can be fixedly held by the brake B2. As described above, in the transmission of this embodiment, the first sun gear S1 of the first planetary gear train G1 is engaged with and disengaged from the second carrier C2 and the second ring gear R2 of the second planetary gear train G2 via the clutches K3 and K4, respectively. They are freely connected. The speed diagram of this transmission is as shown in FIG. 26. Three vertical lines indicating each element of the first planetary gear train G1 are the first sun gear S from the left.
1, corresponding to the first ring gear R1, the first carrier C1,
Three vertical lines representing each element of the second planetary gear train G2 correspond to the second ring gear R2, the second carrier C2, and the second sun gear S2 from the left.

A twelfth example of the type I transmission is shown in FIGS. 27 and 28. This transmission includes a double pinion type first planetary gear train G1 and a double pinion type second planetary gear train G2. The first sun gear S1 is removably connected to the input shaft 1 via a first clutch K1, and the first carrier C1 is removably connected to the input shaft 1 via a second clutch K2. The first carrier C1 further includes a second ring gear R2 and a second sun gear S via a third clutch K3 and a fourth clutch K4, respectively.
2 is detachably connected. The first ring gear R1 and the second carrier C2 are directly connected and are directly connected to the output gear 5. The second ring gear R2 and the second
The sun gear S2 includes a first brake B1 and a second
It can be fixedly held by the brake B2. As described above, in the transmission of this embodiment, the first carrier C1 of the first planetary gear train G1 is engaged with and disengaged from the second ring gear R2 and the second sun gear S2 of the second planetary gear train G2 via the clutches K3 and K4, respectively. They are freely connected. The speed diagram of this transmission is as shown in FIG. 28, and three vertical lines indicating each element of the first planetary gear train G1 are the first carrier C from the left.
1, corresponding to the first ring gear R1, the first sun gear S1,
Three vertical lines indicating each element of the second planetary gear train G2 correspond to the second sun gear S2, the second ring gear R2, and the second carrier C2 from the left.

A thirteenth example of the type I transmission is shown in FIGS. 29 and 30. This transmission includes a double pinion type first planetary gear train G1 and a double pinion type second planetary gear train G2. The first sun gear S1 is removably connected to the input shaft 1 via a second clutch K2, and the first carrier C1 is removably connected to the input shaft 1 via a first clutch K1. The first sun gear S1 is further connected to a second ring gear R2 and a second carrier C via a third clutch K3 and a fourth clutch K4, respectively.
2 is detachably connected. The first ring gear R1 and the second sun gear S2 are directly connected and are directly connected to the output gear 5. The second ring gear R2 and the second
The carrier C2 includes a first brake B1 and a second brake B1, respectively.
It can be fixedly held by the brake B2. As described above, in the transmission of this embodiment, the first sun gear S1 of the first planetary gear train G1 is engaged with and disengaged from the second ring gear R2 and the second carrier C2 of the second planetary gear train G2 via the clutches K3 and K4, respectively. They are freely connected. The speed diagram of this transmission is as shown in FIG. 30, and three vertical lines indicating each element of the first planetary gear train G1 are the first sun gear S from the left.
1, corresponding to the first ring gear R1, the first carrier C1,
Three vertical lines representing each element of the second planetary gear train G2 correspond to the second carrier C2, the second ring gear R2, and the second sun gear S2 from the left.

Type II Next, a transmission belonging to the type II group according to the prior art will be described. The type II group is a transmission having a speed diagram configured as shown in FIG. As shown in this diagram, the transmission comprises three elements E11, E1
2, a first planetary gear train G1 composed of E13 (each corresponding to one of a sun gear, a carrier, and a ring gear)
And three elements E21, E22, E23 (each corresponding to a sun gear, a carrier, or a ring gear)
And a second planetary gear train G2. The element E11 is connected to the input member 1 via the first clutch K1, and the element E13 is always connected to the input member 1. Element E1
2 and E23 are connected via the second clutch K2, and the element E23 is connected to the output member 5. Further, the element E
11 and E22 are removably connected via a third clutch K3, and the element E22 can be fixedly held by the first brake B1. Elements E11 and E2
1 is connected via a fourth clutch K4 so as to be freely engaged and disengaged, and the element E21 can be fixedly held by a second brake B2. As can be seen from this configuration, the type
Also in the transmission belonging to the group II, one element E11 of the first planetary gear train G1 is detachably connected to two elements E22 and E21 of the second planetary gear train via clutches K3 and K4, respectively. Have been.

Next, a description will be given of a specific structure which is realized as a type II transmission. FIG. 32 shows a skeleton according to a first example of a type II transmission. This transmission is
Double pinion type first planetary gear train G1 and single pinion type second planetary gear train G2 coaxially arranged in parallel
It is composed of The first sun gear S1 is a first clutch K
The first carrier C <b> 1 is always connected to the input shaft 1 so as to be detachably connected to the input shaft 1 via the input shaft 1. The first sun gear S1 is further removably connected to the second carrier C2 and the second sun gear S2 via a third clutch K3 and a fourth clutch K4, respectively. First ring gear R
The first and second ring gears R2 are connected via a second clutch K2, and the second ring gear R2 is directly connected to the output gear 5. Further, the second carrier C2 and the second sun gear S
2 are a first brake B1 and a second brake B, respectively.
2, it can be fixedly held. As described above, in the transmission of this embodiment, the first sun gear S1 of the first planetary gear train G1 is engaged with and disengaged from the second carrier C2 and the second sun gear S2 of the second planetary gear train G2 via the clutches K3 and K4, respectively. They are freely connected.

As described above, each element (the sun gears S1, S2
, Carriers C1 and C2, and ring gears R1 and R2),
In a transmission configured by connecting the input shaft 1 and the output gear 5, the engagement and disengagement control of the first to fourth clutches K1 to K4 and the first and second brakes B1 and B2 is performed as shown in Table 7. , 5th forward speed (LOW, 2ND, 3RD, 4T
H, 5TH) and the first reverse speed (REV). As shown in Table 7, each of the five forward speeds is set by engaging a plurality of engagement means (clutches, brakes), and when shifting between adjacent speeds, at least one gear is required. The shift is performed with the engagement means engaged. Therefore, there is no possibility that all the engagement means are released at the time of this shift and a neutral state occurs, and the shift control is easy.

[0051]

[Table 7]

5th forward speed (LOW, 2ND,
3RD, 4TH, 5TH) and the first reverse speed (REV) are set by engaging and disengaging control of the first to fourth clutches K1 to K4 and the first and second brakes B1 and B2 as shown in Table 8. Can also be done. Also in this case, the shift between the adjacent speed stages is always performed while at least one engagement means is engaged, and in this shift, all the engagement means are released and a neutral state occurs. There is no danger and the shift control is easy. Table 7 and Table 8 differ only in the engagement clutch and the brake for setting the second speed (2ND).

[0053]

[Table 8]

The speed diagram of this transmission is as shown in FIG. 33. Three vertical lines indicating each element of the first planetary gear train G1 are as follows.
From the left, the first sun gear S1, the first ring gear R1, the first
Three vertical lines corresponding to the carrier C1 and indicating each element of the second planetary gear train G2 correspond to the second sun gear S2, the second carrier C2, and the second ring gear R2 from the left. Also in this case, the speed reduction ratio for each speed stage can be obtained using this speed diagram.
Since the method is the same as that described above, its description is omitted.

FIGS. 34 and 35 show a second example of the type II transmission. This transmission comprises a double pinion type first planetary gear train G1 and a single pinion type second planetary gear train G2. The first carrier C1 is detachably connected to the input shaft 1 via the first clutch K1, and the first sun gear S1 is always connected to the input shaft 1. The first carrier C1 is further connected to a second carrier C2 via a third clutch K3 and a fourth clutch K4, respectively.
And the second sun gear S2.
The first ring gear R1 is removably connected to the second ring gear R2 via a second clutch K2.
2 is directly connected to the output gear 5. Further, the second carrier C2 and the second sun gear S2 can be fixedly held by the first brake B1 and the second brake B2, respectively. As described above, in the transmission of this example, the first carriers C1 of the first planetary gear train G1 are
3, K4 via the second carrier C of the second planetary gear train G2
2 and the second sun gear S2. The speed diagram of this transmission is as shown in FIG.
The three vertical lines indicating each element of the planetary gear train G1 correspond to the first carrier C1, the first ring gear R1, and the first sun gear S1 from the left, and the three vertical lines indicate each element of the second planetary gear train G2. The vertical line indicates the second sun gear S2 and the second carrier C from the left side.
2, corresponding to the second ring gear R2.

FIGS. 36 and 37 show a third example of the type II transmission. This transmission includes a single pinion type first planetary gear train G1 and a double pinion type second planetary gear train G2. The first sun gear S1 is detachably connected to the input shaft 1 via a first clutch K1, and the first ring gear R1 is always connected to the input shaft 1. The first sun gear S1 is further connected to a second ring gear R via a third clutch K3 and a fourth clutch K4, respectively.
2 and the second carrier C2. The first carrier C1 is connected to the second carrier C2 via the second clutch K2.
The second sun gear S2 is removably connected to the sun gear S2.
Are directly connected to the output gear 5. The second ring gear R2 and the second carrier C2 can be fixedly held by the first brake B1 and the second brake B2, respectively. As described above, in the transmission of the present embodiment, the first sun gear S1 of the first planetary gear train G1 is
3 and K4, it is connected to the second ring gear R2 and the second carrier C2 of the second planetary gear train G2 in a detachable manner. The speed diagram of this transmission is as shown in FIG.
The three vertical lines indicating each element of the planetary gear train G1 correspond to the first sun gear S1, the first carrier C1, and the first ring gear R1 from the left, and the three vertical lines indicate each element of the second planetary gear train G2. The vertical line corresponds to the second carrier C2, the second ring gear R2, and the second sun gear S2 from the left.

A fourth example of a type II transmission is shown in FIGS. This transmission has a single pinion type first planetary gear train G1 and a single pinion type second planetary gear train G1.
And a planetary gear train G2. The first sun gear S1 is detachably connected to the input shaft 1 via a first clutch K1, and the first ring gear R1 is always connected to the input shaft 1. The first sun gear S1 is further connected to a second carrier C2 via a third clutch K3 and a fourth clutch K4, respectively.
And the second sun gear S2.
The first carrier C1 is removably connected to the second ring gear R2 via a second clutch K2, and is connected to the second ring gear R2.
Are directly connected to the output gear 5. Also, the second carrier C
2 and the second sun gear S2 are respectively connected to the first brake B
It can be fixedly held by the first and second brakes B2. As described above, in the transmission of the present embodiment, the first sun gears S1 of the first planetary gear train G1 are connected to the clutches K3 and K3, respectively.
It is detachably connected to the second carrier C2 and the second sun gear S2 of the second planetary gear train G2 via K4. The speed diagram of this transmission is as shown in FIG. 39, and three vertical lines indicating each element of the first planetary gear train G1 correspond to the first sun gear S1, the first carrier C1, and the first ring gear R1 from the left. Correspondingly, three vertical lines indicating each element of the second planetary gear train G2 correspond to the second sun gear S2, the second carrier C2, and the second ring gear R2 from the left.

FIGS. 40 and 41 show a fifth example of the type II transmission. This transmission has a single pinion type first planetary gear train G1 and a single pinion type second planetary gear train G1.
And a planetary gear train G2. The first sun gear S1 is detachably connected to the input shaft 1 via a first clutch K1, and the first ring gear R1 is always connected to the input shaft 1. The first sun gear S1 is further connected to a second carrier C2 via a third clutch K3 and a fourth clutch K4, respectively.
And the second ring gear R2. The first carrier C1 is connected to the second carrier C2 via the second clutch K2.
The second sun gear S2 is removably connected to the sun gear S2.
Are directly connected to the output gear 5. Also, the second carrier C
The second and second ring gears R2 can be fixedly held by a first brake B1 and a second brake B2, respectively. As described above, in the transmission of the present embodiment, the first sun gear S1 of the first planetary gear train G1 is
3, K4 via the second carrier C of the second planetary gear train G2
The second and second ring gears R2 are detachably connected to each other. The speed diagram of this transmission is as shown in FIG.
The three vertical lines indicating each element of the planetary gear train G1 correspond to the first sun gear S1, the first carrier C1, and the first ring gear R1 from the left, and the three vertical lines indicate each element of the second planetary gear train G2. The vertical line corresponds to the second ring gear R2, the second carrier C2, and the second sun gear S2 from the left.

FIGS. 42 and 43 show a sixth example of the type II transmission. This transmission includes a single pinion type first planetary gear train G1 and a double pinion type second planetary gear train G2. The first ring gear R1 is detachably connected to the input shaft 1 via a first clutch K1, and the first sun gear S1 is always connected to the input shaft 1. The first ring gear R1 is further removably connected to the second ring gear R2 and the second carrier C2 via a third clutch K3 and a fourth clutch K4, respectively. The first carrier C1 is connected to the second carrier C2 via the second clutch K2.
The second sun gear S2 is removably connected to the sun gear S2.
Are directly connected to the output gear 5. The second ring gear R2 and the second carrier C2 can be fixedly held by the first brake B1 and the second brake B2, respectively. As described above, in the transmission of this example, the first ring gear R1 of the first planetary gear train G1 is connected to the clutch K
3 and K4, it is connected to the second ring gear R2 and the second carrier C2 of the second planetary gear train G2 in a detachable manner. The speed diagram of this transmission is as shown in FIG.
The three vertical lines indicating each element of the planetary gear train G1 correspond to the first ring gear R1, the first carrier C1, and the first sun gear S1 from the left, and the three vertical lines indicating each element of the second planetary gear train G2. The vertical line corresponds to the second carrier C2, the second ring gear R2, and the second sun gear S2 from the left.

FIGS. 44 and 45 show a seventh example of the type II transmission. This transmission has a single pinion type first planetary gear train G1 and a single pinion type second planetary gear train G1.
And a planetary gear train G2. First ring gear R1
Is connected to the input shaft 1 via a first clutch K1 so as to be freely engaged and disengaged, and the first sun gear S1 is always connected to the input shaft 1. The first ring gear R1 is further connected to the second carrier C via a third clutch K3 and a fourth clutch K4, respectively.
2 and the second sun gear S2. The first carrier C1 is connected to the second carrier C2 via the second clutch K2.
The second ring gear R <b> 2 is directly connected to the output gear 5. Further, the second carrier C2 and the second sun gear S2 can be fixedly held by the first brake B1 and the second brake B2, respectively. As described above, in the transmission of this embodiment, the first ring gear R1 of the first planetary gear train G1 is engaged with and disengaged from the second carrier C2 and the second sun gear S2 of the second planetary gear train G2 via the clutches K3 and K4, respectively. They are freely connected. The speed diagram of this transmission is as shown in FIG.
The three vertical lines indicating each element of the planetary gear train G1 correspond to the first ring gear R1, the first carrier C1, and the first sun gear S1 from the left, and the three vertical lines indicating each element of the second planetary gear train G2. The vertical line indicates the second sun gear S2 and the second carrier C from the left side.
2, corresponding to the second ring gear R2.

FIGS. 46 and 47 show an eighth example of the type II transmission. This transmission has a single pinion type first planetary gear train G1 and a single pinion type second planetary gear train G1.
And a planetary gear train G2. First ring gear R1
Is connected to the input shaft 1 via a first clutch K1 so as to be freely engaged and disengaged, and the first sun gear S1 is always connected to the input shaft 1. The first ring gear R1 is further connected to the second carrier C via a third clutch K3 and a fourth clutch K4, respectively.
2 and the second ring gear R2. The first carrier C1 is connected to the second carrier C2 via the second clutch K2.
The second sun gear S2 is removably connected to the sun gear S2.
Are directly connected to the output gear 5. Also, the second carrier C
The second and second ring gears R2 can be fixedly held by a first brake B1 and a second brake B2, respectively. As described above, in the transmission of this example, the first ring gear R1 of the first planetary gear train G1 is connected to the clutch K
3, K4 via the second carrier C of the second planetary gear train G2
The second and second ring gears R2 are detachably connected to each other. The speed diagram of this transmission is as shown in FIG.
The three vertical lines indicating each element of the planetary gear train G1 correspond to the first ring gear R1, the first carrier C1, and the first sun gear S1 from the left, and the three vertical lines indicating each element of the second planetary gear train G2. The vertical line corresponds to the second ring gear R2, the second carrier C2, and the second sun gear S2 from the left.

A ninth example of a type II transmission is shown in FIGS. This transmission includes a double pinion type first planetary gear train G1 and a double pinion type second planetary gear train G2. The first sun gear S1 is the first
It is detachably connected to the input shaft 1 via the clutch K1,
The first carrier C1 is always connected to the input shaft 1. The first sun gear S1 is further removably connected to the second ring gear R2 and the second carrier C2 via a third clutch K3 and a fourth clutch K4, respectively. First
The ring gear R1 is removably connected to the second sun gear S2 via a second clutch K2, and the second sun gear S2 is directly connected to the output gear 5. The second ring gear R2 and the second carrier C2 can be fixedly held by the first brake B1 and the second brake B2, respectively. As described above, in the transmission of the present embodiment, the first sun gear S1 of the first planetary gear train G1 is connected to the clutches K3 and K3, respectively.
4 and is removably connected to the second ring gear R2 and the second carrier C2 of the second planetary gear train G2. The speed diagram of this transmission is as shown in FIG. 49, and three vertical lines indicating each element of the first planetary gear train G1 correspond to the first sun gear S1, the first ring gear R1, and the first carrier C1 from the left. Correspondingly, three vertical lines indicating each element of the second planetary gear train G2 are, from the left side, a second carrier C2, a second ring gear R2,
This corresponds to the second sun gear S2.

A tenth example of a type II transmission is shown in FIGS. 50 and 51. This transmission has a double pinion type first planetary gear train G1 and a single pinion type second planetary gear train G1.
And a planetary gear train G2. The first sun gear S1 is detachably connected to the input shaft 1 via the first clutch K1, and the first carrier C1 is always connected to the input shaft 1. The first sun gear S1 is further connected to a second carrier C2 via a third clutch K3 and a fourth clutch K4, respectively.
And the second ring gear R2. The first ring gear R1 is removably connected to the second sun gear S2 via a second clutch K2, and is connected to the second sun gear S2.
2 is directly connected to the output gear 5. Further, the second carrier C2 and the second ring gear R2 can be fixedly held by the first brake B1 and the second brake B2, respectively. As described above, in the transmission of the present embodiment, the first sun gear S1 of the first planetary gear train G1 is
3, K4 via the second carrier C of the second planetary gear train G2
The second and second ring gears R2 are detachably connected to each other. The speed diagram of this transmission is as shown in FIG.
The three vertical lines indicating each element of the planetary gear train G1 correspond to the first sun gear S1, the first ring gear R1, and the first carrier C1 from the left, and the three vertical lines indicate each element of the second planetary gear train G2. The vertical line indicates the second sun gear S2 and the second carrier C from the left side.
2, corresponding to the second ring gear R2.

FIGS. 52 and 53 show an eleventh example of the type II transmission. This transmission includes a double pinion type first planetary gear train G1 and a double pinion type second planetary gear train G2. The first carrier C1 is detachably connected to the input shaft 1 via the first clutch K1, and the first sun gear S1 is always connected to the input shaft 1. The first carrier C1 further receives the second ring gear R via a third clutch K3 and a fourth clutch K4, respectively.
2 and the second carrier C2. The first ring gear R1 is removably connected to the second sun gear S2 via a second clutch K2, and is connected to the second sun gear S2.
2 is directly connected to the output gear 5. The second ring gear R2 and the second carrier C2 can be fixedly held by the first brake B1 and the second brake B2, respectively. As described above, in the transmission of this example, the first carriers C1 of the first planetary gear train G1 are
3 and K4, it is connected to the second ring gear R2 and the second carrier C2 of the second planetary gear train G2 in a detachable manner. The speed diagram of this transmission is as shown in FIG.
The three vertical lines indicating each element of the planetary gear train G1 correspond to the first carrier C1, the first ring gear R1, and the first sun gear S1 from the left, and the three vertical lines indicate each element of the second planetary gear train G2. The vertical line corresponds to the second carrier C2, the second ring gear R2, and the second sun gear S2 from the left.

A twelfth example of a type II transmission is shown in FIGS. 54 and 55. This transmission has a double pinion type first planetary gear train G1 and a single pinion type second planetary gear train G1.
And a planetary gear train G2. The first carrier C1 is detachably connected to the input shaft 1 via the first clutch K1, and the first sun gear S1 is always connected to the input shaft 1. The first carrier C1 is further connected to a second carrier C2 via a third clutch K3 and a fourth clutch K4, respectively.
And the second ring gear R2. The first ring gear R1 is removably connected to the second sun gear S2 via a second clutch K2, and is connected to the second sun gear S2.
2 is directly connected to the output gear 5. Further, the second carrier C2 and the second ring gear R2 can be fixedly held by the first brake B1 and the second brake B2, respectively. As described above, in the transmission of this example, the first carriers C1 of the first planetary gear train G1 are
3, K4 via the second carrier C of the second planetary gear train G2
The second and second ring gears R2 are detachably connected to each other. The speed diagram of this transmission is as shown in FIG.
The three vertical lines indicating each element of the planetary gear train G1 correspond to the first carrier C1, the first ring gear R1, and the first sun gear S1 from the left, and the three vertical lines indicate each element of the second planetary gear train G2. The vertical line corresponds to the second ring gear R2, the second carrier C2, and the second sun gear S2 from the left.

Type III Next, transmissions belonging to the type III group will be described. The type III group is a transmission configured with a velocity diagram as shown in FIG. As shown in this diagram, the transmission comprises three elements E11, E12, E13
(Each corresponds to one of a sun gear, a carrier, and a ring gear) from a first planetary gear train G1 and three elements E21, E22, and E23 (each corresponding to one of a sun gear, a carrier, and a ring gear). And a second planetary gear train G2. Elements E11 and E13
Are connected to the input member 1 via the second clutch K2 and the first clutch K1, respectively. Elements E13 and E2
3 are directly connected to each other, and the element E12 is connected to the output member 5. Further, the elements E11 and E22 are removably connected via a third clutch K3, and the element E2
2 can be fixedly held by the first brake B1. The elements E11 and E21 are removably connected via a fourth clutch K4, and the element E21 is connected to the second clutch K4.
It can be fixedly held by the brake B2. As can be seen from this configuration, even in the transmission belonging to the type III group, one element E1 of the first planetary gear train G1 is also provided.
1 is the two elements E22 and E21 of the second planetary gear train
, Respectively, are releasably connected via clutches K3 and K4.

Next, a description will be given of a specific structure which is realized as a type III transmission. FIG. 57 shows a skeleton according to a first example of a type III transmission. This transmission has a double pinion type first transmission coaxially arranged in parallel.
Planetary gear train G1 and double pinion type second planetary gear train G
And 2. The first carrier C1 and the first sun gear S1 are removably connected to the input shaft 1 via a first clutch K1 and a second clutch K2, respectively.
The first sun gear S1 further includes a third clutch K3
And a second clutch G4 via a fourth clutch K4 to be detachably connected to the second ring gear R2 and the second carrier C2. The first carrier C1 and the second sun gear S2 are directly connected to each other,
The ring gear R1 is directly connected to the output gear 5. Also,
The second ring gear R2 and the second carrier C2 can be fixedly held by the first brake B1 and the second brake B2, respectively. As described above, in the transmission of this embodiment, the first sun gear S1 of the first planetary gear train G1 is engaged with and disengaged from the second ring gear R2 and the second carrier C2 of the second planetary gear train G2 via the clutches K3 and K4, respectively. They are freely connected.

As described above, each element (the sun gears S1, S2
, Carriers C1 and C2, and ring gears R1 and R2),
In the transmission configured by connecting the input shaft 1 and the output gear 5, the engagement / disengagement control of the first to fourth clutches K1 to K4 and the first and second brakes B1 and B2 is as shown in Table 3 or Table 4. By doing, the forward 5th speed (LOW, 2ND, 3
(RD, 4TH, 5TH) and the first reverse speed (REV) can be set. The speed diagram of this transmission is as shown in FIG. 58. Three vertical lines indicating each element of the first planetary gear train G1 are, from the left, a first sun gear S1, a first ring gear R1, and a first carrier C1. Correspondingly, three vertical lines indicating each element of the second planetary gear train G2 correspond to the second carrier C2, the second ring gear R2, and the second sun gear S2 from the left. Also in this case, using this velocity diagram,
Although the reduction ratio for each speed stage can be obtained, this method is the same as the method described with reference to FIGS. 5 and 6, and a description thereof will be omitted.

A second example of a type III transmission is shown in FIGS. This transmission has a double pinion type first planetary gear train G1 and a single pinion type second planetary gear train G1.
And a planetary gear train G2. The first carrier C1 and the first sun gear S1 are removably connected to the input shaft 1 via a first clutch K1 and a second clutch K2, respectively. The first sun gear S1 further includes a third
The clutch is removably connected to the second carrier C2 and the second sun gear S2 via the clutch K3 and the fourth clutch K4. The first carrier C1 is directly connected to the second ring gear R2, and the first ring gear R1 is directly connected to the output gear 5. Further, the second carrier C2 and the second sun gear S2
Are the first brake B1 and the second brake B2, respectively.
Can be fixedly held. As described above, in the transmission according to the present embodiment, the first sun gear S of the first planetary gear train G1 is used.
1 is removably connected to the second carrier C2 and the second sun gear S2 of the second planetary gear train G2 via the clutches K3 and K4, respectively. The speed diagram of this transmission is shown in FIG.
0, which indicates each element of the first planetary gear train G1.
The vertical lines correspond to the first sun gear S1, the first ring gear R1, and the first carrier C1 from the left, and the second planetary gear train G
The three vertical lines indicating the elements 2 correspond to the second sun gear S2, the second carrier C2, and the second ring gear R2 from the left.

FIGS. 61 and 62 show a third example of a type III transmission. This transmission has a double pinion type first planetary gear train G1 and a single pinion type second planetary gear train G1.
And a planetary gear train G2. The first sun gear S1 and the first carrier C1 are removably connected to the input shaft 1 via a first clutch K1 and a second clutch K2, respectively. The first carrier C1 further includes a third
The clutch is removably connected to the second carrier C2 and the second sun gear S2 via the clutch K3 and the fourth clutch K4. The first sun gear S1 and the second ring gear R2 are directly connected, and the first ring gear R1 is directly connected to the output gear 5. Further, the second carrier C2 and the second sun gear S2
Are the first brake B1 and the second brake B2, respectively.
Can be fixedly held. As described above, in the transmission of the present embodiment, the first carrier C of the first planetary gear train G1 is used.
1 is removably connected to the second carrier C2 and the second sun gear S2 of the second planetary gear train G2 via the clutches K3 and K4, respectively. The speed diagram of this transmission is shown in FIG.
2, which indicates each element of the first planetary gear train G1.
The vertical lines correspond to the first carrier C1, the first ring gear R1, and the first sun gear S1 from the left, and the second planetary gear train G
The three vertical lines indicating the elements 2 correspond to the second sun gear S2, the second carrier C2, and the second ring gear R2 from the left.

FIGS. 63 and 64 show a fourth example of a type III transmission. This transmission has a double pinion type first planetary gear train G1 and a single pinion type second planetary gear train G1.
And a planetary gear train G2. The first carrier C1 and the first sun gear S1 are removably connected to the input shaft 1 via a first clutch K1 and a second clutch K2, respectively. The first sun gear S1 further includes a third
The clutch is connected to the second carrier C2 and the second ring gear R2 via a clutch K3 and a fourth clutch K4 so as to be freely detachable. The first carrier C1 and the second sun gear S2 are directly connected, and the first ring gear R1 is directly connected to the output gear 5. Further, the second carrier C2 and the second ring gear R
2 are a first brake B1 and a second brake B, respectively.
2, it can be fixedly held. As described above, in the transmission of this embodiment, the first sun gear S1 of the first planetary gear train G1 is connected to the second carrier C2 and the second ring gear R2 of the second planetary gear train G2 via the clutches K3 and K4, respectively.
And is detachably connected. The speed diagram of this transmission is as shown in FIG. 64, and three vertical lines indicating each element of the first planetary gear train G1 are, from the left, a first sun gear S1, a first ring gear R1, and a first carrier C1. Correspondingly, three vertical lines indicating each element of the second planetary gear train G2 correspond to the second ring gear R2, the second carrier C2, and the second sun gear S2 from the left.

FIGS. 65 and 66 show a fifth example of the type III transmission. This transmission has a double pinion type first planetary gear train G1 and a single pinion type second planetary gear train G1.
And a planetary gear train G2. The first sun gear S1 and the first carrier C1 are removably connected to the input shaft 1 via a first clutch K1 and a second clutch K2, respectively. The first carrier C1 further includes a third
The clutch is connected to the second carrier C2 and the second ring gear R2 via a clutch K3 and a fourth clutch K4 so as to be freely detachable. The first sun gear S1 and the second sun gear S2 are directly connected, and the first ring gear R1 is directly connected to the output gear 5. Further, the second carrier C2 and the second ring gear R
2 are a first brake B1 and a second brake B, respectively.
2, it can be fixedly held. As described above, in the transmission of this embodiment, the first carrier C1 of the first planetary gear train G1 is connected to the second carrier C2 and the second ring gear R2 of the second planetary gear train G2 via the clutches K3 and K4, respectively.
And is detachably connected. The speed diagram of this transmission is as shown in FIG. 66, and three vertical lines indicating each element of the first planetary gear train G1 correspond to the first carrier C1, the first ring gear R1, and the first sun gear S1 from the left. Correspondingly, three vertical lines indicating each element of the second planetary gear train G2 correspond to the second ring gear R2, the second carrier C2, and the second sun gear S2 from the left.

FIGS. 67 and 68 show a sixth example of the type III transmission. This transmission includes a double pinion type first planetary gear train G1 and a double pinion type second planetary gear train G2. The first sun gear S1 and the first carrier C1 are removably connected to the input shaft 1 via a first clutch K1 and a second clutch K2, respectively. The first carrier C1 is further removably connected to the second ring gear R2 and the second carrier C2 via a third clutch K3 and a fourth clutch K4, respectively. The first sun gear S1 and the second sun gear S2 are directly connected, and the first ring gear R1 is directly connected to the output gear 5. Further, the second ring gear R2 and the second carrier C2
Are the first brake B1 and the second brake B2, respectively.
Can be fixedly held. As described above, in the transmission of the present embodiment, the first carrier C of the first planetary gear train G1 is used.
1 is removably connected to the second ring gear R2 and the second carrier C2 of the second planetary gear train G2 via the clutches K3 and K4, respectively. The speed diagram of this transmission is as shown in FIG. 68, and three vertical lines indicating each element of the first planetary gear train G1 correspond to the first carrier C1, the first ring gear R1, and the first sun gear S1 from the left. Correspondingly, three vertical lines indicating each element of the second planetary gear train G2 correspond to the second carrier C2, the second ring gear R2, and the second sun gear S2 from the left.

[0074]

As described above, in the planetary gear transmission according to the present invention, the first and second planetary gear trains are coaxially arranged in the power transmission path from the input member to the output member. The first and second elements that constitute one planetary gear train are releasably connected to the input member via first and second clutch means, respectively, and the first element that constitutes the first planetary gear train is the first element. The first and second elements constituting the second planetary gear train are removably connected to the first and second elements constituting the second planetary gear train via third and fourth clutch means. Since it is configured to be able to be fixedly held via the first and second brake means, it is possible to obtain a relatively small and compact planetary gear transmission having a novel structure which has not been provided conventionally. Further, in the case of this transmission, it is possible to set a forward gear 5 or higher speed by appropriately controlling a plurality of clutches and brakes for setting a power transmission path from the input member to the output member. is there. In this case, the speed change between the adjacent speed stages is performed while at least one engagement means (clutch or brake) is engaged, so that the speed change control is easy.

[Brief description of the drawings]

FIG. 1 is a velocity diagram of a planetary gear transmission according to the present invention.

FIG. 2 is a velocity diagram of the planetary gear transmission according to the present invention.

FIG. 3 is a skeleton diagram of the planetary gear transmission according to the present invention.

FIG. 4 is a velocity diagram of the planetary gear transmission according to the present invention.

FIG. 5 is a velocity diagram of the planetary gear transmission according to the present invention.

FIG. 6 is a velocity diagram of the planetary gear transmission according to the present invention.

FIG. 7 is a skeleton diagram of the planetary gear transmission according to the present invention.

FIG. 8 is a velocity diagram of the planetary gear transmission according to the present invention.

FIG. 9 is a skeleton diagram of the planetary gear transmission according to the present invention.

FIG. 10 is a velocity diagram of the planetary gear transmission according to the present invention.

FIG. 11 is a skeleton diagram of the planetary gear transmission according to the present invention.

FIG. 12 is a velocity diagram of the planetary gear transmission according to the present invention.

FIG. 13 is a skeleton diagram of the planetary gear transmission according to the present invention.

FIG. 14 is a velocity diagram of the planetary gear transmission according to the present invention.

FIG. 15 is a skeleton diagram of the planetary gear transmission according to the present invention.

FIG. 16 is a velocity diagram of the planetary gear transmission according to the present invention.

FIG. 17 is a skeleton diagram of the planetary gear transmission according to the present invention.

FIG. 18 is a velocity diagram of the planetary gear transmission according to the present invention.

FIG. 19 is a skeleton diagram of the planetary gear transmission according to the present invention.

FIG. 20 is a velocity diagram of the planetary gear transmission according to the present invention.

FIG. 21 is a skeleton diagram of the planetary gear transmission according to the present invention.

FIG. 22 is a velocity diagram of the planetary gear transmission according to the present invention.

FIG. 23 is a skeleton diagram of the planetary gear transmission according to the present invention.

FIG. 24 is a velocity diagram of the planetary gear transmission according to the present invention.

FIG. 25 is a skeleton diagram of the planetary gear transmission according to the present invention.

FIG. 26 is a velocity diagram of the planetary gear transmission according to the present invention.

FIG. 27 is a skeleton diagram of the planetary gear transmission according to the present invention.

FIG. 28 is a velocity diagram of the planetary gear transmission according to the present invention.

FIG. 29 is a skeleton diagram of the planetary gear transmission according to the present invention.

FIG. 30 is a velocity diagram of the planetary gear transmission according to the present invention.

FIG. 31 is a velocity diagram of a planetary gear transmission according to the related art.

FIG. 32 is a skeleton diagram of a planetary gear transmission according to the related art.

FIG. 33 is a velocity diagram of a planetary gear transmission according to the related art.

FIG. 34 is a skeleton diagram of a planetary gear transmission according to the related art.

FIG. 35 is a velocity diagram of a planetary gear transmission according to the related art.

FIG. 36 is a skeleton diagram of a planetary gear transmission according to the related art.

FIG. 37 is a velocity diagram of a planetary gear transmission according to the related art.

FIG. 38 is a skeleton diagram of a planetary gear transmission according to the related art.

FIG. 39 is a velocity diagram of a planetary gear transmission according to the related art.

FIG. 40 is a skeleton diagram of a planetary gear transmission according to the related art.

FIG. 41 is a velocity diagram of a planetary gear transmission according to the related art.

FIG. 42 is a skeleton diagram of a planetary gear transmission according to the related art.

FIG. 43 is a velocity diagram of a planetary gear transmission according to the related art.

FIG. 44 is a skeleton diagram of a planetary gear transmission according to the related art.

FIG. 45 is a velocity diagram of a planetary gear transmission according to the related art.

FIG. 46 is a skeleton diagram of a planetary gear transmission according to the related art.

FIG. 47 is a velocity diagram of a planetary gear transmission according to the related art.

FIG. 48 is a skeleton diagram of a planetary gear transmission according to the related art.

FIG. 49 is a velocity diagram of a planetary gear transmission according to the related art.

FIG. 50 is a skeleton diagram of a planetary gear transmission according to the related art.

FIG. 51 is a velocity diagram of a planetary gear transmission according to the related art.

FIG. 52 is a skeleton diagram of a planetary gear transmission according to the related art.

FIG. 53 is a velocity diagram of a planetary gear transmission according to the related art.

FIG. 54 is a skeleton diagram of a planetary gear transmission according to the related art.

FIG. 55 is a velocity diagram of a planetary gear transmission according to the related art.

FIG. 56 is a velocity diagram of the planetary gear transmission according to the present invention.

FIG. 57 is a skeleton diagram of the planetary gear transmission according to the present invention.

FIG. 58 is a velocity diagram of the planetary gear transmission according to the present invention.

FIG. 59 is a skeleton diagram of the planetary gear transmission according to the present invention.

FIG. 60 is a velocity diagram of the planetary gear transmission according to the present invention.

FIG. 61 is a skeleton diagram of a planetary gear transmission according to the present invention.

FIG. 62 is a velocity diagram of the planetary gear transmission according to the present invention.

FIG. 63 is a skeleton diagram of the planetary gear transmission according to the present invention.

FIG. 64 is a velocity diagram of the planetary gear transmission according to the present invention.

FIG. 65 is a skeleton diagram of the planetary gear transmission according to the present invention.

FIG. 66 is a velocity diagram of the planetary gear transmission according to the present invention.

FIG. 67 is a skeleton diagram of a planetary gear transmission according to the present invention.

FIG. 68 is a velocity diagram of the planetary gear transmission according to the present invention.

[Explanation of symbols]

 1 Input shaft 5 Output gear B1, B2 Brake K1, K2, K3, K4 Clutch S1, S2 Sun gear C1, C2 Carrier R1, R2 Ring gear

──────────────────────────────────────────────────続 き Continuation of the front page (72) Inventor Takashi Hotta 1-4-1 Chuo, Wako-shi, Saitama Pref. Honda Research Institute (56) References 3-24365 (JP, A) JP-A-60-205050 (JP, A) JP-A-56-94053 (JP, A) (58) Fields investigated (Int. Cl. ⁷ , DB name) F16H 3/44 -3/78

Claims (2)

(57) [Claims] 1. A first and a second planetary gear train having a sun gear element, a carrier element and a ring gear element, respectively, are coaxially disposed in a power transmission path from an input member to an output member. A planetary gear transmission having a plurality of clutches and brakes for setting a power transmission path from the first gear to the output member, wherein a first element forming the first planetary gear train is a first element. The input member is detachably connected to the input member via clutch means, and is detachably connected to first and second elements constituting the second planetary gear train via third and fourth clutch means, respectively. A second element constituting the first planetary gear train is removably connected to the input member via a second clutch means, and a third element constituting the first planetary gear train is Said The first and second elements constituting the second planetary gear train are always connected to the third element constituting the second planetary gear train and always connected to the output member, and the first and second elements constitute the second planetary gear train. A planetary gear transmission characterized by being capable of being fixedly held via brake means. 2. A power transmission path from an input member to an output member, wherein first and second planetary gear trains each having a sun gear element, a carrier element and a ring gear element are coaxially arranged, and A planetary gear transmission having a plurality of clutches and brakes for setting a power transmission path from the first gear to the output member, wherein a first element forming the first planetary gear train is a first element. The input member is removably connected to the input member via clutch means, and is removably connected to first and second elements constituting the second planetary gear train via third and fourth clutch means. A second element forming the first planetary gear train is connected to the input member via a second clutch means so as to be freely detachable, and a third element forming the second planetary gear train. A third element forming the first planetary gear train is always connected to the output member, and the first and second elements forming the second planetary gear train are first and second elements. 2. A planetary gear transmission characterized in that the planetary gear transmission can be fixedly held via brake means (2).