JPS5814576B2 - Hensokuuchi - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a transmission for a vehicle, and particularly to a transmission suitable for use in combination with a fluid coupling of an automobile.

Generally, it is desirable for a transmission device for a large vehicle such as a truck or a bus to have at least four or more gear stages.

For this reason, it is conceivable to combine three or four or more sets of single pinion or double pinion type simple planar gear sets and to realize at least four or more gear stages by appropriately linking each element therein. .

A large number of combinations of transmissions can be considered, but it is desirable that the following conditions be satisfied.

(1) The output shaft must be connected to the same element for each gear stage.

(2) Each element of each planetary gear set has a low rotational speed to reduce the circumferential speed of its bearings.

(3) Due to problems with the strength of the teeth of each gear, the tooth load or tangential force of each element is small.

(4) The number of teeth of each gear in each planetary gear set must satisfy the meshing conditions, and the sun gear and planetary gear with the minimum diameter must also have the required number of teeth or more.

(5) The connection of each element of each planetary gear set can be easily achieved with a length as short as possible.

(6) When shifting gears when traveling forward, the friction means are switched to shift the gears, but this switching is done in order to reduce the switching shock.
What can be done by switching only one piece.

Considering these conditions mentioned above, the present invention uses two basic single-pinion simple planetary gear sets and one double-pinion simple planetary gear set, basically two clutch devices and two brake devices. Basically, three gears are used, and the movable members of each planetary gear set are appropriately coupled, and the clutch device and brake device are appropriately disengaged, thereby providing a transmission with at least four forward gears and one reverse gear. It provides:

The present invention has several sets of planetary gear sets, each consisting of an input shaft, an output shaft, a carrier supporting a sun gear, a ring gear, and a planetary gear metal that connects the gears, and a case that is a fixed member. The carrier of the pinion type first planetary gear set and the sun gear of the single pinion type second planetary gear set are drivingly connected, and the carrier of the single pinion type third planetary gear set and the ring gear of the second planetary gear set are driven by one drive. The ring gear of the first planetary gear set, the carrier of the second planetary gear set, and the sun gear of the third planetary gear set are drivingly connected to the output shaft, and the carrier of the first planetary gear set and the second planetary gear set A first device that connects or releases the input shaft with the sun gear connected to the input shaft.
A clutch, a second clutch that connects or disengages the sun gear of the first planetary gear set with respect to the input shaft, the sun gear of the first planetary gear set, the carrier of the first planetary gear set, and the sun gear of the second planetary gear set are connected. , the ring gear of the second planetary gear set and the carrier of the third planetary gear set are connected, and any one of the four ring gears of the third planetary gear set is secured to the case. This transmission is equipped with one brake that can be fixed to the case, another brake that can be fixed to the case, and another brake that can be fixed to the case.

Embodiments of the present invention will be described below with reference to the drawings.

In FIG. 1, a double pinion type first planetary gear set X1, a single pinion type second planetary gear set X2, and a third planetary gear set X3 are appropriately arranged between the input shaft and the output shaft.

The first planetary gear set X1 includes a first sun gear S1, a first planetary gear P1 that meshes with the first sun gear S1, a second planetary gear P2 that meshes with the first planetary gear P1, and a first ring gear RG1 that meshes with the second planetary gear P2. and a first carrier C1 that pivotally supports the first planar gear P1 and the second planar gear P2.

The second planetary gear set X2 includes a second sun gear S2, a third planetary gear P3 that meshes with the second sun gear S2, and a second ring gear RG that meshes with the third planetary gear P3.
2, and a second carrier C2 that pivotally supports a third plane gear P3.

The third planetary gear set X3 includes a third sun gear S3, a fourth planetary gear P4 that meshes with the third sun gear S3, and a third ring gear RG that meshes with the fourth planetary gear P4.
3, and a third carrier C3 that pivotally supports a fourth planetary gear P4.

The connection relationship between the first planetary gear set X1, the second planetary gear set X2, and the third planetary gear set X3 includes the first carrier C1 and the second sun gear S2, the first ring gear RG1, the second carrier C2, the third sun gear S3, and the third planetary gear set X2. The output shaft, second ring gear RG2, and third carrier C3 are each drivingly connected.

The first clutch CL1 is arranged to connect or disconnect the input shaft, the first carrier C1, and the second sun gear S2.

The second clutch CL2 is arranged to connect or disconnect the input shaft and the first sun gear S1.

The first brake B1 is arranged so as to be fixed to the first sun gear S1k case.

The second brake B2 is arranged to secure the first carrier C1 and the second sun gear S2 to the case.

The third brake B3 is arranged to secure the second ring gear RG2 and the third carrier C3 to the case.

The fourth brake B4 is arranged to secure the third ring gear RG3 to the case.

From the above explanation, the following equation holds true for each planetary gear set of the transmission of the present invention.

NRG1-(1-I1)NC,-I1NS1=ONRG
2-(1+I2)NC2+12NS2=0NRG3-(
1+I3)NC3+13NS3=0*NRG4-(1+
I4) NC4+I4NS4=0 (However, this *formula applies to all embodiments after the second embodiment.

) Here, NRG1, NRG2, NRG3, NRG4: 1st, 2nd
・Rotation speed of 3rd and 4th ring gear NC1・NC2・NC
3・NC4: Number of rotations of the first, second, third, and fourth carriers NS1・NS
2・NS3・NS4: Number of revolutions of the 1st, 2nd, 3rd, and 4th sun gear ■1・■2・
■3・■4: 1st and 2nd for 1st, 2nd, 3rd and 4th ring gear
- Radius ratio of the third and fourth sun gears.

Here, to illustrate the specific numerical values of each gear in the first embodiment of the present invention, each radius ratio is ■1=0.320, I2
=0.452, I3=0.452, and five forward speeds and two reverse speeds can be obtained.

To summarize the relationship between the operation of the clutches CL1, CL2 and the brakes B1, B2, B3, B4 and the reduction ratio of each gear in each gear, we can see that the 1A display (here, the reduction ratio of 1.00 is obtained) For this purpose, clutch CL1, CL2
This can be achieved by combining any two of them, and the same applies to the following embodiments.

).

Therefore, in order to obtain at least four forward speeds and one reverse speed, two clutch devices and three brake devices are basically used, and these are engaged and disengaged as appropriate. It goes without saying that this can be achieved by doing so.

That is, referring to Fig. 1 and Table 1A, when any three of brakes B1, B2, B3, and B4 are used, the following four forward speeds and one reverse speed are possible. You can get the gears.

(1) For example, if three brakes B1, B2, and B3 are used, the reduction is obtained by operating gear F1, CL2, and B2, which has a reduction ratio of 3.21 obtained by combining CL1 and B3. Gears F2 with a ratio of 3.13, gears F4 with a reduction ratio of 1.47 obtained by operating CL1 and B1, CL1 and C
Four forward speeds of gear F5 with a reduction ratio of 1.00 obtained by operating L2 and a reduction ratio of 3.0 obtained by operating CL2 and B3.
It is possible to obtain one reverse speed of gear R1 of 70.

(2) Also, if three brakes, B1, B3, and B4 are used, the reduction ratio of 3.21 obtained by operating CL1 and B3 is obtained by operating gear F1, CL1, and B4. Gear stage F3 with a reduction ratio of 2.52, gear stage F4 with a reduction ratio of 1.47 obtained by operating CL1 and B1, and gear stage F5 with a reduction ratio of 1.00 obtained by operating CL1 and CL2.
4 forward speeds and 1 reverse speed of either R1 with a reduction ratio of 3.70 obtained by operating CL2 and B3 or R2 with a reduction ratio of 2.24 obtained by operating CL2 and B4. I can do it.

Similarly, (3) If three brakes, B1, B2, and B4 are used, the gears F2, F3, F4,
You can get 4 forward speeds of F5 and 1 reverse speed of R2, (
4) If three brakes, B2, B3, and B4 are used, four forward speeds of F1, F2, F3, and F5 and one reverse speed of either R1 or R2 can be obtained.

Now, if we look at the friction means that are switched when changing gears during forward running, as is clear from Table 1A, the gear position F
If only No. 2 does not use CL1 and shifts from another gear (for example, F1 or F3), the brake must be switched at the same time as the clutch, making shift control difficult.

Therefore, it goes without saying that among the four methods (1) to (4) described above, the method described as (2) in which the brake B2 is not used is preferable in practice.

Also, the relationship between the rotational speed and tangential force between each gear stage and each gear set is summarized as shown in display 1B.

However, Table 1B shows the ratio of the rotation speed when the input shaft rotation speed is assumed to be 1, and the tangential force ratio when the torque when the torque of the input shaft acts on the ring gear is assumed to be 1.
The same applies to all Examples hereinafter.

Also, to summarize the symbols in the table for all examples, A: Gear stage B: Planetary gear set N: Rotational speed W: Tangential force F1, F2, F3, F4, F5, F6, F7 Forward 1st.
2nd, 3rd, 4th, 5th, 6th, and 7th speeds R1, R2, and R3 are reverse 1st, 2nd, and 3rd speeds.

Furthermore, F5 (F5 gear which is the highest forward speed gear) has a reduction ratio of 1.
．． 00, its rotational speed N and its tangential force W are omitted.

That is, in a gear position where the reduction ratio is 1.00, the rotation speed N of each sun gear, ring gear, and carrier is 1.00, and the rotation speed N of each planetary gear is 0.00.
In addition, the tangential force W is significantly smaller than the tangential force W generated in other gears, that is, in other gears, the engagement of only one clutch among the clutches is not enough. In contrast, the torque of the input shaft is transmitted to each element only through the clutch that is
5th stage), when at least two clutches are engaged, the input shaft torque is shared between both clutches, and the shared input shaft torque is transmitted to each element. It is obvious that the tangential force of each element is smaller than when the torque of the input shaft is not shared but is directly transmitted as in other gears due to the engagement of one clutch.

In the following, the rotational speed N and tangential force W of the gear position at which the reduction ratio is 1.00 will be omitted for all examples.

Next, as a description of the second embodiment of the present invention, the structure and operation of parts different from the above-described first embodiment, that is, parts added to the first embodiment, will be explained.

In Fig. 2, the fourth planetary gear set
A sun gear S4, a fifth planetary gear P5 meshing with the fourth sun gear S4, and a fourth planetary gear P5 meshing with the fifth planetary gear P5.
It is composed of a ring gear RG4 and a fourth carrier C4 that pivotally supports a fifth planetary gear P5.

Also, the fourth sun gear S4, the output shaft, and the fourth ring gear RG
4 and the third carrier C3 are drivingly connected to each other.

Further, the fourth ring gear RG4 is arranged so as to be fixed to the case by the third brake B3.

The fifth brake B5 is arranged to secure the carrier C4 to the case.

Here, by using the calculation formula explained in the above-mentioned first embodiment, and illustrating the specific numerical values of each gear stage in the present second embodiment,
I1=0.320, I2=0.452, I3=0.45
2, I4 = 0.562, and each clutch CL1, CL2 and each brake B1 in 6 forward speeds and 3 reverse speeds
, B2, B3, B4, and B5 and the reduction ratio of each gear stage are summarized as shown in display 2A, and the relationship between the rotation speed and tangential force between each gear stage and each gear set is summarized as shown in display 2A. It will look like 2B display.

Next, a description of the third embodiment of the present invention will be given, focusing on the parts that are different from the first and second embodiments described above, that is, the parts added to the first embodiment, and the connection relationship that is different from the second embodiment.

In FIG. 3, the fourth sun gear S4 and the output shaft, and the fourth ring gear RG4 and the third ring gear RG3 are drivingly connected, respectively.

Further, the fourth ring gear RG4 is arranged so as to be fixed to the case by the fourth brake B4.

The fifth brake B5 is arranged to secure the fourth carrier C4 to the case.

Here, by using the calculation formula explained in the above-mentioned first embodiment, and illustrating the specific numerical values of each gear stage in the present third embodiment, it is as follows:
I1=0.320, I2=0.452, I3=0.45
2, I4 = 0.562, and each clutch CL1, CL2 and each brake B1 in 6 forward speeds and 3 reverse speeds
, B2, B3, B4, and B5 and the reduction ratio of each gear stage are summarized as shown in display 3A, and the relationship between the rotation speed and tangential force between each gear stage and each gear set is summarized as shown in display 3A. It will look like 3B display.

Next, the fourth embodiment of the present invention will be explained, focusing on the parts different from the first and second embodiments described above, that is, the parts added to the first embodiment, and the connection relationship different from the second embodiment.

In FIG. 4, the fourth sun gear S4 and the third carrier C
3. The fourth ring gear RG4 and the output shaft are each drivingly connected.

Further, the fourth sun gear S4 is arranged so as to be fixed to the case by the third brake B3.

The fifth brake B5 is arranged to secure the fourth carrier C4 to the case.

Here, by using the calculation formula explained in the above-mentioned first embodiment, and illustrating the specific numerical values of each gear stage in the fourth embodiment,
I1=0.320, I2=0.452, I3=0.45
2, I4 = 0.562, and each clutch CL1, CL2 and each brake B1 in 6 forward speeds and 3 reverse speeds
, B2, B3, B4, and B5 and the reduction ratio of each gear stage are summarized as shown in No. 4A, and the relationship between the rotation speed and tangential force of each gear set and each gear set is summarized as shown in No. 4A. It will look like 4B display.

Next, the fifth embodiment of the present invention will be explained, focusing on the parts different from the first and second embodiments described above, that is, the parts added to the first embodiment, and the connection relationship different from the second embodiment.

In FIG. 5, the fourth sun gear S4 and the third ring gear RG3, and the fourth ring gear RG4 and the output shaft are drivingly connected, respectively.

Further, the fourth sun gear S4 is arranged so as to be fixed to the case by the fourth brake B4.

The fifth brake B5 is arranged to secure the fourth carrier C4 to the case.

Here, if we use the calculation formula explained in the above-mentioned first embodiment to give an example of the numerical values of each gear stage in the present fifth embodiment,
I1=0.320, I2=0.452, I3=0.45
2, I4=0.437, and each clutch CL1, CL2 and each brake B1 in 6 forward speeds and 3 reverse speeds
, B2, B3, B4, and B5 and the relationship between the reduction ratio of each gear stage is summarized as shown in display 5A, and the relationship between the rotation speed and tangential force between each gear stage and each gear set is summarized as shown in display 5A. It will look like 5B display.

Next, as a description of the sixth embodiment of the present invention, a description will be given focusing on the parts different from the first and second embodiments described above, that is, the parts added to the first embodiment, and the connection relationship different from the second embodiment.

In FIG. 6, the fourth carrier C4 and the third carrier C
3. The fourth ring gear RG4 and the output shaft are each drivingly connected.

Further, the fourth carrier C4 is arranged so as to be fixed to the case by the third brake B3.

The fifth brake B5 is arranged so as to fix the fourth sun gear S4 to the case.

Here, if we use the calculation formula explained in the above-mentioned first embodiment to give an example of the numerical values of each gear stage in the present sixth embodiment,
I1=0.320, I2=0.452, I3=0.45
2, I4 = 0.562, and each clutch CL1, CL2 and each brake B1 in 6 forward speeds and 3 reverse speeds
, B2, B3, B4, and B5 and the relationship between the reduction ratio of each gear stage is summarized as shown in No. 6A, and the relationship between the rotation speed and tangential force between each gear stage and each gear set is summarized as No. 6A. It will look like 6B display.

Next, the seventh embodiment of the present invention will be explained, focusing on the parts that are different from the first and second embodiments described above, that is, the parts added to the first embodiment, and the connection relationship that is different from the second embodiment.

In FIG. 7, the fourth carrier C4 and the third ring gear RG3, and the fourth ring gear RG4 and the output shaft are drivingly connected, respectively.

Further, the fourth carrier C4 is arranged so as to be fixed to the case by the fourth brake B4.

The fifth brake B5 is arranged so as to fix the fourth sun gear S4 to the case.

Here, using the calculation formula explained in the first embodiment, the specific numerical values of each gear in the seventh embodiment are exemplified as I1=0.320, I2=0.452, I3=0.4
52, I4=0.280, and each clutch CL1, CL2 and each brake B in 6 forward speeds and 2 reverse speeds
The relationship between the operations of 1, B2, B3, B4, and B5 and the reduction ratio of each gear is summarized as shown in No. 7A, and the relationship between the rotation speed and tangential force between each gear and each gear set is summarized. It will look like display 7B.

Next, an explanation of the eighth embodiment of the present invention will be given, focusing on the parts that are different from the first and second embodiments described above, that is, the parts added to the first embodiment, and the connection relationships that are different from the second embodiment.

In FIG. 8, a fourth carrier C4 and the third carrier C
3. The fourth sun gear S4 and the output shaft are coupled in a husband-and-wife driving manner.

Further, the fourth carrier C4 is arranged so as to be fixed to the case by the third brake B3.

The fifth brake B5 is arranged so as to be able to securely fasten the fourth ring gear RG4 to the case.

Here, by using the calculation formula explained in the above-mentioned first embodiment, the specific numerical values of each gear stage of the present eighth embodiment are illustrated as follows.
I1=0.320, I2=0.452, I3=0.45
2, I4 = 0.562, and each clutch CL1, CL2 and each brake B1 in 6 forward speeds and 3 reverse speeds
, B2, B3, B4, and B5 and the relationship between the reduction ratio of each gear stage is summarized as shown in No. 8A, and the relationship between the rotation speed and tangential force between each gear stage and each gear set is summarized as shown in No. 8A. It will look like 8B display.

Next, the ninth embodiment of the present invention will be explained, focusing on the parts that are different from the first and second embodiments described above, that is, the parts added to the first embodiment, and the connection relationships that are different from the second embodiment.

In FIG. 9, the fourth sun gear S4 and the output shaft, and the fourth carrier C4 and the third ring gear RG3 are drivingly connected, respectively.

Further, the fourth carrier C4 is arranged so as to be fixed to the case by the fourth brake B4.

The fifth brake B5 is arranged to secure the fourth ring gear RG4 to the case.

Here, by using the calculation formula explained in the above-mentioned first embodiment, and illustrating the specific numerical values of each gear stage of the present ninth embodiment,
I1=0.320, I2=0.452, I3=0.45
2, I4 = 0.562, and each clutch CL1, CL2 and each brake B1 in 6 forward speeds and 3 reverse speeds
, B2, B3, B4, and B5 and the reduction ratio of each gear stage are summarized as shown in No. 9A, and the relationship between the rotational speed and tangential force between each gear stage and each gear set is summarized as No. 9A. It will look like 9B display.

Next, a description of the tenth embodiment of the present invention will be given, focusing on the parts that are different from the first and second embodiments described above, that is, the parts added to the first embodiment, and the connection relationships that are different from the second embodiment.

In FIG. 10, the fourth carrier C4, the output shaft, and the fourth
The sun gear S4 and the third carrier C3 are each drivingly connected.

Further, the fourth sun gear S4 is arranged so as to be fixed to the case by the third brake B3.

The fifth brake B5 is arranged so as to be able to securely fasten the fourth ring gear RG4 to the case.

Here, if we use the calculation formula explained in the above-mentioned first embodiment to give an example of the specific numerical values of each gear in the tenth embodiment, I1=0.320, I2=0.452, I3 =0.4
52, I4=0.437, and each clutch CL1, CL2 and each brake B in 6 forward speeds and 3 reverse speeds
The relationship between the operations of 1, B2, B3, B4, and B5 and the reduction ratio of each gear is summarized as shown in No. 10A, and the relationship between the rotation speed and tangential force between each gear and each gear set is summarized. It will look like display 10B.

Next, an explanation of the eleventh embodiment of the present invention will be given, focusing on the parts that are different from the first and second embodiments described above, that is, the parts added to the first embodiment, and the connection relationships that are different from the second embodiment.

In FIG. 11, the fourth sun gear S4 and the third ring gear RG3, and the fourth carrier C4 and the output shaft are drivingly connected, respectively.

Further, the fourth sun gear S4 is arranged so as to be fixed to the case by the fourth brake B4.

The fifth brake B5 is arranged so as to be able to securely fasten the fourth ring gear RG4 to the case.

Here, if we use the calculation formula explained in the above-mentioned first embodiment to give an example of the specific numerical values of each gear stage in this 11th embodiment, I1=0.320, I2=0.452, I3 =0.4
52, I4=0.437, and each clutch CL1, CL2 and each brake B in 6 forward speeds and 3 reverse speeds
The relationship between the operations of 1, B2, B3, B4, and B5 and the reduction ratio of each gear is summarized as shown in display 11A, and the relationship between the rotation speed and tangential force between each gear and each gear set is summarized. It will look like display 11B.

Next, a description of the twelfth embodiment of the present invention will be given, focusing on the parts that are different from the first and second embodiments described above, that is, the parts added to the first embodiment, and the connection relationships that are different from the second embodiment.

In FIG. 12, the fourth carrier C4, the output shaft, and the fourth
The ring gear RG4 and the third carrier C3 are each drivingly connected.

Further, the fourth ring gear RG4 is arranged so as to be fixed to the case by the third brake B3.

The fifth brake B5 is arranged so as to fix the fourth sun gear S4 to the case.

Here, if we use the calculation formula explained in the above-mentioned first example to give an example of the specific numerical values of each gear in the 12th actual case, ■1=0.320, I2=0.452, I3=0.4
52, I4=0.562, and each clutch CL1, CL2 and each brake B in 6 forward speeds and 2 reverse speeds
The relationship between the operations of 1, B2, B3, B4, and B5 and the reduction ratio of each gear is summarized as shown in display 12A, and the relationship between the rotation speed and tangential force between each gear and each gear set is summarized. It will look like display 12B.

Next, as a description of the thirteenth embodiment of the present invention, a description will be given focusing on the parts different from the first and second embodiments described above, that is, the parts added to the first embodiment, and the connection relationship different from the second embodiment.

In FIG. 13, the fourth carrier C4, the output shaft, and the fourth
Ring gear RG4 and second sun gear S2 are each drivingly connected.

Further, the fourth ring gear RG4 is arranged so as to be fixed to the case by the second brake B2.

The fifth brake B5 is arranged so as to fix the fourth sun gear S4 to the case.

Here, by using the calculation formula explained in the above-mentioned first embodiment, the specific numerical values of each gear stage of the present thirteenth embodiment are exemplified as I1=0.320, I2=0.452, ■3=0.
452, I4 = 0.280, and the relationship between the operation of each clutch CL1, CL2 and each brake B1, B2, B3, B4, B5 and the reduction ratio of each gear in 7 forward speeds and 2 reverse speeds is summarized. The relationship between the rotational speed and the tangential force of each gear and each gear set is summarized as shown in 13B.

Next, as a description of the fourteenth embodiment of the present invention, a description will be given focusing on the parts different from the first and second embodiments described above, that is, the parts added to the first embodiment, and the connection relationship different from the second embodiment.

In FIG. 14, the fourth carrier C4, the output shaft, and the fourth
The sun gear S4 and the second sun gear S2 are each drivingly connected.

Further, the fourth sun gear S4 is arranged so as to be fixed to the case by the second brake B2.

The fifth brake B5 is arranged so as to be able to securely fasten the fourth ring gear RG4 to the case.

Here, if we use the calculation formula explained in the above-mentioned first embodiment to give an example of the specific numerical values of each gear stage in this 14th embodiment, I1=0.320, I2=0.452, 3=0.4
52, I4=0.280, and each clutch CL1, CL2 and each brake B in 6 forward speeds and 3 reverse speeds
The relationship between the operations of 1, B2, B3, B4, and B5 and the reduction ratio of each gear is summarized as shown in display 14A, and the relationship between the rotation speed and tangential force between each gear and each gear set is summarized. It will look like the 14th B display.

The preferred embodiments of the transmission according to the present invention are as follows.

(1) an input shaft, an output shaft, a first sun gear, a first planetary gear that meshes with the first sun gear, a second planetary gear that meshes with the first planetary gear, and a first ring gear that meshes with the second planetary gear;
a first planetary gear set including a first carrier pivotally supporting the first and second planetary gears; a second sun gear drivingly connected to the first carrier;
A second planetary gear set including a third planetary gear that meshes with the sun gear, a second ring gear that meshes with the third planetary gear, and a second carrier that pivotally supports the third planetary gear, a first ring gear, a second carrier, an output shaft, and one a third sun gear that is drivingly connected to the third sun gear; a fourth planetary gear that meshes with the third sun gear; a third ring gear that meshes with the fourth planetary gear; and a third ring gear that pivotally supports the fourth planetary gear and is drivingly connected to the second ring gear. a third planetary gear set including a third carrier; a first clutch that connects or releases the input shaft with the first carrier and the second sun gear; a second clutch that connects or releases the input shaft with the first sun gear; A first brake capable of being secured to the case, a second brake capable of securing the first carrier and the second sun gear to the case, a third brake capable of securing the second ring gear and the third carrier to the case, and a third ring gear. A transmission device comprising: a fourth brake that can be secured to the case;

(2) In the transmission having the configuration described in item (1) above,
A fourth sun gear that is drivingly connected to the output shaft, a fifth planetary gear that meshes with the fourth sun gear, a fourth ring gear that meshes with the fifth planetary gear and is drivingly connected to the third carrier, and a fifth planetary gear. A transmission device further comprising: a fourth planetary gear set including a supporting fourth carrier; and a fifth brake capable of securing the fourth carrier to the case.

(3) In the transmission having the configuration described in item (1) above,
a fourth sun gear that is drivingly connected to the output shaft; a fifth planetary gear that meshes with the fourth sun gear; a fourth ring gear that meshes with the fifth planetary gear and that is drivingly connected to the third ring gear; and a fifth planetary gear. a fourth planetary gear set including a fourth carrier pivotally supporting the fourth carrier; and a transmission further comprising a fifth brake capable of fixing the fourth carrier to the case.

(4) In the transmission having the configuration described in item (1) above,
a fourth sun gear drivingly connected to the third carrier;
a fourth planetary gear set including a fifth planetary gear that meshes with a fourth sun gear; a fourth ring gear that meshes with the fifth planetary gear and is drivingly connected to the output shaft; and a fourth carrier that pivotally supports the fifth planetary gear; A transmission device further comprising a fifth brake capable of fixing a fourth carrier to the case.

(5) In the transmission having the configuration described in item (1) above,
a fourth sun gear that is drivingly connected to the third ring gear; a fifth planetary gear that meshes with the fourth sun gear; a fourth ring gear that meshes with the fifth planetary gear and that is drivingly connected to the output shaft; and a fifth planetary gear. a fourth planetary gear set including a fourth carrier pivotally supporting the fourth carrier; and a transmission further comprising a fifth brake capable of fixing the fourth carrier to the case.

(6) In the transmission having the configuration described in item (1) above,
a fourth sun gear, a fifth planetary gear that meshes with the fourth sun gear, a fourth ring gear that meshes with the fifth planetary gear and is drivingly connected to the output shaft, and a fourth ring gear that pivotally supports the fifth planetary gear and drives the third carrier. a fourth planetary gear set including a fourth carrier that is coupled to the fourth carrier;

(7) In the transmission having the configuration described in item (1) above,
a fourth sun gear, a fifth planetary gear that meshes with the fourth sun gear, a fourth ring gear that meshes with the fifth planetary gear and is drivingly connected to the output shaft, and a fourth ring gear that pivotally supports the fifth planetary gear and is connected to the third ring gear. A transmission device further comprising a fourth planetary gear set including a fourth carrier drivingly coupled to the fourth carrier, and a fifth brake capable of fixing the fourth sun gear to the case.

(8) In the transmission having the configuration described in item (1) above,
A fourth sun gear that is drivingly connected to the output shaft, a fifth planetary gear that meshes with the fourth sun gear, a fourth ring gear that meshes with the fifth planetary gear, and a fourth ring gear that pivotally supports the fifth planetary gear and is drivingly connected to the third carrier. a fourth planetary gear set including a fourth carrier connected to the case; and a transmission further comprising a fifth brake capable of fixing the fourth ring gear to the case.

(9) In the transmission having the configuration described in item (1) above,
a fourth sun gear that is drivingly connected to the output shaft; a fifth planetary gear that meshes with the fourth sun gear; a fourth ring gear that meshes with the fifth planetary gear; and a fourth ring gear that pivotally supports the fifth planetary gear and is drivingly connected to the third ring gear. The fourth connected to
A transmission device further comprising: a fourth planetary gear set including a carrier; and a fifth brake capable of fixing a fourth ring gear to the case.

(10) In the transmission having the configuration described in item (1) above, a fourth sun gear drivingly connected to the third carrier, a fifth planetary gear meshing with the fourth sun gear, and a fifth planetary gear meshing with the fifth planetary gear. A fourth planetary gear set including a fourth ring gear that fits, and a fourth carrier that pivotally supports a fifth planetary gear and is drivingly connected to the output shaft, and a fifth brake that can secure the fourth ring gear to the case is added. transmission.

(11) In the transmission having the configuration described in item (1) above, a fourth sun gear drivingly connected to the third ring gear;
a fourth planetary gear set including a fifth planetary gear that meshes with a fourth sun gear, a fourth ring gear that meshes with the fifth planetary gear, and a fourth carrier that pivotally supports the fifth planetary gear and is drivingly connected to the output shaft; A transmission that includes a fifth brake capable of securing a fourth ring gear to the case.

(12) In the transmission having the configuration described in item (1) above, a fourth sun gear, a fifth planetary gear that meshes with the fourth sun gear, and a fifth planetary gear that meshes with the fifth planetary gear and the third
A fourth planetary gear set including a fourth ring gear drivingly connected to a carrier, a fourth carrier pivotally supporting a fifth planetary gear and drivingly connected to the output shaft, and a fourth sun gear fixed to the case. A transmission with an additional fifth brake.

(13) In the transmission having the configuration described in item (1) above, a fourth sun gear, a fifth planetary gear that meshes with the fourth sun gear, and a fifth planetary gear that meshes with the fifth planetary gear and the second
a fourth planetary gear set including a fourth ring gear drivingly connected to the sun gear; and a fourth carrier pivotally supporting a fifth planetary gear and drivingly connected to the output shaft, the fourth sun gear being fixed to the case; A transmission with the addition of a fifth brake.

(14) In the transmission having the configuration described in item (1) above, a fourth sun gear drivingly connected to the second sun gear, a fifth planetary gear meshing with the fourth sun gear, and a fifth planetary gear meshing with the fifth planetary gear. A fourth planetary gear set including a fourth ring gear that fits, and a fourth carrier that pivotally supports a fifth planetary gear and is drivingly connected to the output shaft, and a fifth brake that can secure the fourth ring gear to the case is added. transmission.

(15) A transmission having the configuration described in item (1) above, in which the second brake is removed.

(16) A transmission having the configuration described in item (2) above, in which the third brake is removed.

(17) A transmission having the configuration described in item (2) above, in which the second brake is removed.

(18) A transmission having the configuration described in item (2) above, in which the second and third brakes are removed.

(19) A transmission having the configuration described in item (3) above, in which the third brake is removed.

(20) A transmission having the configuration described in item (3) above, in which the second brake is removed.

(21) A transmission having the configuration described in item (3) above, in which the second and third brakes are removed.

(22) A transmission having the configuration described in item (4) above, in which the second brake is removed.

(23) A transmission having the configuration described in item (5) above, in which the second brake is removed.

(24) A transmission having the configuration described in item (6) above, in which the fourth brake is removed.

(5) In the transmission having the configuration described in item (6) above,
A transmission device in which the third brake is removed.

(26) A transmission having the configuration described in item (6) above, in which the second brake is removed.

(27) A transmission having the configuration described in item (6) above, in which the second and fourth brakes are removed.

(28) A transmission having the configuration described in item (6) above, in which the second and third brakes are removed.

(29) A transmission having the configuration described in item (6) above, in which the first brake is removed.

(30) A transmission having the configuration described in item (6) above, in which the first and second brakes are removed.

(31) A transmission having the configuration described in item (7) above, in which the third brake is removed.

(32) A transmission having the configuration described in item (7) above, in which the second brake is removed.

(33) A transmission having the configuration described in item (7) above, in which the second and third brakes are removed.

(34) A transmission having the configuration described in item (7) above, in which the first brake is removed.

(35) A transmission having the configuration described in item (7) above, in which the first and second brakes are removed.

(36) A transmission having the configuration described in item (8) above, in which the fourth brake is removed.

(37) A transmission having the configuration described in item (8) above, in which the third brake is removed.

(38) A transmission having the configuration described in item (8) above, in which the second brake is removed.

(39) A transmission having the configuration described in item (8) above, in which the second and fourth brakes are removed.

(40) A transmission having the configuration described in item (8) above, in which the second and third brakes are removed.

(41) A transmission having the configuration described in item (9) above, in which the fourth brake is removed.

(42) A transmission having the configuration described in item (9) above, in which the third brake is removed.

(43) A transmission having the configuration described in item (9) above, in which the second brake is removed.

(44) A transmission having the configuration described in item (9) above, in which the second and fourth brakes are removed.

(45) A transmission having the configuration described in item (9) above, in which the second and third brakes are removed.

(46) A transmission having the configuration described in item (9) above, in which the first brake is removed.

(47) A transmission having the configuration described in item (9) above, in which the first and second brakes are removed.

(48) A transmission having the configuration described in item (10) above, in which the second brake is removed.

(49) A transmission having the configuration described in item (11) above, in which the third brake is removed.

(50) A transmission having the configuration described in item (11) above, in which the second brake is removed.

(51) A transmission having the configuration described in item (1.1) above, in which the second and third brakes are removed.

(52) A transmission having the configuration described in item (12) above, in which the second brake is removed.

(53) A transmission having the configuration described in item (13) above, in which the fourth brake is removed.

(54) A transmission having the configuration described in item (13) above, in which the third brake is removed.

(55) A transmission having the configuration described in item (13) above, in which the second brake is removed.

(56) A transmission having the configuration described in item (13) above, in which the second and fourth brakes are removed.

(57) A transmission having the configuration described in item (13) above, in which the second and third brakes are removed.

(58) A transmission having the configuration described in item (13) above, in which the first brake is removed.

(59) A transmission having the configuration described in item (13) above, in which the first and third brakes are removed.

(69) A transmission having the configuration described in item (13) above, in which the first and second brakes are removed.

(61) A transmission having the configuration described in item (13) above, in which the first, second, and third brakes are removed.

(62) A transmission having the configuration described in item (14) above, in which the third brake is removed.

(63) A transmission having the configuration described in item (14) above, in which the second brake is removed.

(64) A transmission having the configuration described in item (14) above, in which the second and third brakes are removed.

As is clear from the above description of the structure and operation, the transmission device of the present invention achieves the initial objective and provides a practical transmission having at least four forward speeds and one reverse speed. This has great industrial effects.

[Brief explanation of the drawing]

1 to 14 are schematic central vertical cross-sectional views diagrammatically showing first to fourteenth embodiments of the transmission of the present invention, respectively. X1, X2, X3, X4...1st, 2nd, 3rd, 4th
Planetary gear set, S1, S2, S3, S4...
...1st, 2nd, 3rd, and 4th sun gear, P1, P2, P3
, P4, P5... 1st, 2nd, 3rd, 4th, 5th planetary gear, RG1, RG2, RG3, RG4...
・1st, 2nd, 3rd, 4th ring gear, C1, C2, C3, C
4...1st, 2nd, 3rd, 4th carrier, CL1, C
L2...1st and 2nd clutch, B1, B2, B3
, B4, B5... 1st, 2nd, 3rd, 4th, 5th brake.

Claims (1)

[Claims] 1. Several sets of planetary gears, each consisting of an input shaft, an output shaft, and a carrier that pivotally supports a sun gear, a ring gear, and a planetary gear that connects the gears, and a case that is a fixed member. The carrier of the double pinion type first planetary gear set and the sun gear of the single pinion type second planetary gear set are pivotally connected, and the carrier of the single pinion type third planetary gear set and the ring carrier of the second single pinion type planetary gear set are pivotally connected. The ring gear of the first planetary gear set, the carrier of the second planetary gear set, and the sun gear of the third planetary gear set are drivingly connected to the output shaft. a first clutch that connects or releases the sun gear of the first planetary gear set with respect to the input shaft; a second clutch that connects or releases the sun gear of the first planetary gear set with the input shaft; and a second clutch that connects or releases the sun gear of the first planetary gear set with the input shaft; A sun gear, a carrier of a first planetary gear set and a sun gear of a second planetary gear set are connected, a ring gear of a second planetary gear set and a carrier of a third planetary gear set are connected, and a third planetary gear. One brake that can secure any three of the four ring gears in the set to the case, another brake that can secure the other one to the case, and the remaining one to the case. A transmission device comprising another brake that can be locked. 2. In the first invention set forth in the claims, any two of the sun gear, ring gear, and carrier of the fourth planetary gear set may be replaced with the ring gear of the second planetary gear set and the ring gear of the third planetary gear set. and the other is drivingly connected to the output shaft, and the remaining members of the sun gear, ring gear, and carrier of the fourth planetary gear set are fixed to the case. A transmission device that is provided with a separate braking device. 3. In the first invention described in the claims, any one of the sun gear, ring gear, and carrier of the fourth planetary gear set is drivingly connected to the ring gear of the third planetary gear set. A transmission device comprising another brake device drivingly connected to the output shaft, and capable of fixing the remaining members of the sun gear, ring gear, and carrier of the fourth planetary gear set to the case. 4. In the first invention set forth in the claims, any two of the sun gear, ring gear, and carrier of the fourth planetary gear set are connected to the carrier of the first planetary gear set and the carrier of the second planetary gear set. The fourth gear is drivingly connected to the sun gear and the other is drivingly connected to the output shaft.
A transmission comprising a separate brake device capable of securing the remaining members of the sun gear, ring gear, and carrier of the planetary gear set to the case.