JPS5814575B2 - Hensokuuchi - Google Patents

Description

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

It is desirable that a gear-type auxiliary transmission for an automatic transmission for a large vehicle such as a truck or bus has at least four or more gear stages.

For this reason, it is conceivable to realize four or more gear stages by combining three, four, or more single-pinion or double-pinion simple planetary gear sets and appropriately connecting 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) When shifting gears during forward travel, the frictional engagement means are switched to change gears, but this switching can be done by only one switch in order to reduce the switching shock.

(3) The rotational speed is low in order to reduce the circumferential speed of the bearings of each element of the planetary gear set.

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

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

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

Taking these conditions into consideration, the present invention basically uses two single pinion planetary gear sets and one double pinion planetary gear set, basically two clutch devices, and basically two brake devices. A planetary gear type transmission having at least four forward speeds and one reverse speed by appropriately connecting the movable members of each planetary gear set and disconnecting the clutch device and the brake device as appropriate. It is.

The present invention has 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 two gears, and a case that is a fixed member. Both carriers of the pinion type first and second planetary gear sets and the sun gear of the double pinion type third planetary gear set are drivingly connected, and the sun gear of the first planetary gear set and the ring gear of the second planetary gear set are drivingly connected. The sun gear of the second planetary gear set is drivingly connected to the carrier of the third planetary gear set, the ring gear of the third planetary gear set is drivingly connected to the output shaft, and the sun gear of the second planetary gear set is drivingly connected to the carrier of the third planetary gear set. and the carrier of the third planetary gear set are coupled to or released from the input shaft, and the sun gear of the first planetary gear set and the ring gear of the second planetary gear set are coupled to the input shaft. a second clutch to be connected to or released from the shaft; and a sun gear and a second clutch of the first planetary gear set.
The ring gear of the planetary gear set is connected to the ring gear, the carrier of the first and second planetary gear set is connected to the sun gear of the third planetary gear set, and the sun gear of the second planetary gear set and the third planetary gear set are connected. one brake capable of fixing any one of the four ring gears of the first planetary gear set to the case, and the other one fixed to the case. This transmission is equipped with another brake that can be tightened, and another brake that can be secured to the case.

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

First, a first embodiment of the present invention will be described with reference to FIG.

Between the input shaft and the output shaft are a single pinion type first planetary gear set X1 and second planetary gear set X2.
and a double pinion type third planetary gear set X3 are sequentially arranged from the input shaft to the output shaft.

The first planetary gear set X1 includes a first sun gear S1,
a first planetary gear P1 meshing with the first sun gear S1;
First ring gear RG1 meshing with first planetary gear P1
and a first carrier C that pivotally supports the first planetary gear P1.
It is composed of 1.

The second planetary gear set X2 has a second sun gear S2,
a second planetary gear P2 that meshes with a second sun gear S2;
It meshes with the second planetary gear P2 and the first sun gear S
1, and a second carrier C2 that pivotally supports the second planetary gear P2 and is connected to the first carrier C1.

The third planetary gear set X3 includes a third sangya S3 connected to the first carrier C1 and the second carrier C2, and a third planetary gear set X3.
a third planetary gear P3 meshing with sun gear S3;
A fourth planetary gear P4 that meshes with the planetary gear P3, a third ring gear RG3 that meshes with the fourth planetary gear P4 and is connected to the output shaft, and a third planetary gear P
and a third carrier C3 that pivotally supports the third and fourth planetary gears P4 and is connected to the second sun gear S2.

CL1 is the first clutch, which connects the input shaft to the second sun gear S2.
and the third carrier C3 can be released or coupled at the same time.

CL2 is the second clutch, which connects the input shaft to the first sun gear S1.
and second ring gear RG2 can be released or coupled at the same time.

B1 is a first brake, which is arranged so as to be able to simultaneously fasten the first sun gear S1 and second ring gear RG2 to the case.

Reference numeral B2 denotes a second brake, which is arranged so as to be able to simultaneously secure the first carrier C1, second carrier C2, and third sun gear S3 to the case.

B3 is a third brake, which is arranged so as to be able to fix the first ring gear RG1 to the case.

B4 is a fourth brake, which is arranged so as to be able to simultaneously secure the second sun gear S2 and the third carrier C3 to the case.

The following equations hold true for each of the planetary gear sets X1, X2, and X3.

The same applies to all embodiments described below.

NRG1-(1+I1)NC1+I1NS1=0NRG
2-(1+I2)NC2+I2NS2=ONRG3-(
1-I3) NC3-I3NS3=0 However, NRG1, N
RG2 and NRG3 are the rotational speeds of the first, second and third ring gears, NC1, NC2 and NC3 are the rotational speeds of the first and second and third carriers, respectively, and NS1, NS2 and NS3 are the rotational speeds of the first and second carriers, respectively.
, I1, I2, and I3 are the radius ratios of the ring gear and the sun gear, respectively.

Here, to illustrate the specific numerical values of each gear stage in the first embodiment of the present invention, each radius ratio is I1=0.500, I2=0
．． 548, I3=0.500, 5 forward speeds, 2 reverse speeds
gears can be obtained.

Table 1A summarizes the relationships between the operations of the clutches CL1 and CL2 and the brakes B1, B2, B3, and B4 and the reduction ratios of each gear in each gear.

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 ratio obtained by operating CL1 and B3 is 3.21, and the reduction ratio is obtained by operating CL1 and B2. Gears F4, CL1 and C with a reduction ratio of 1.48 obtained by operating gears F3, CL1 and B1 with a ratio of 2.00
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 gear of either gear R1 of 67 or gear R2 with a reduction ratio of 1.10 obtained by operating CL2 and B2.

(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 combining gear F1, CL2, and B4. Gear F2 with a reduction ratio of 3.10, F4 with a reduction ratio of 1.48 obtained by operating CL1 and B1, and F5 with a reduction ratio of 1.00 obtained by operating CL1 and CL2.
4 forward speeds and reduction ratio 3 obtained by operating CL2 and B3.
．． One reverse gear of 64 gears R1 can be obtained.

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) When 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 (1) in which the brake B4 is not used is preferable in practice.

However, Fn (n=1,...n) indicates the forward gear stage,
For example, F1 is the first forward stage, and Rn (n=1,...
n) indicates a reverse gear stage; for example, R1 is the first reverse gear stage.

(The same applies to subsequent examples.

) Table 1B summarizes the relationship between the speed and the rotational speed and tangential force of each gear set.

Regarding the symbols in Table 1B, A indicates the gear stage, B indicates the planetary gear set, N indicates the rotation speed, W indicates the tangential force, and φ
each indicates zero.

Note that the same reference numerals as in Table 1A above mean the same objects.

(The same applies to all embodiments described below) The numerical values in Table 1B are expressed as a ratio with the input shaft being 1, and each tangential force assumes that the torque of the input shaft acts on the ring gear.

Note that since the reduction ratio of the fifth stage, which is the highest forward speed stage, is 1.00, the rotation speed of each sun gear, ring gear, and carrier is 1.00, and the rotation speed of each planetary gear is 0.0.

Moreover, the tangential force is significantly smaller than that for other gears.

That is, in other gears, the torque of the input shaft is transmitted to each element by the engagement of one of the clutches, whereas in the case of the fourth forward gear, at least two clutches are engaged. Because the torque of the input shaft is shared and transmitted to each element by the engagement of the two elements, the tangential force of each element is small.

Therefore, the fifth gear is the highest forward speed with a reduction ratio of 1.00.
Regarding the stage, I deliberately omitted the number of revolutions and tangential force.

In all subsequent embodiments, the meanings of the symbols and the omission of the reduction ratio 1.00 are the same as in the first embodiment.

Next, a second embodiment of the present invention will be described based on FIG. 2, or since it is roughly the same as the first embodiment described above, an additional configuration will be explained.

A single pinion type fourth planetary gear set X4 disposed behind the third planetary gear set X3 includes a fourth sun gear S4 connected to the output shaft, and a fourth sun gear S4.
a fifth planetary gear P5 meshing with the fifth planetary gear P5, a fourth ring gear RG4 meshing with the fifth planetary gear P5 and connected to the first ring gear RG1, and a fifth planetary gear P
5 and a fourth carrier C4 which pivotally supports the carrier.

Note that when the third brake B3 is operated, the fourth ring gear RG4 is fixed to the case.

The difference from the first embodiment described above is that the fourth brake B4 is
The carrier C4 is arranged so as to be secured to the case.

That is, the fourth brake B4 is not arranged to secure the second sun gear S2 and the third carrier C3 to the case.

The following equation holds true for the fourth planetary gear set X4.

The same applies to all the embodiments described below.

NRG4-(1+I4)NC4+I4NS4=0However,
NRG4 is the rotational speed of the fourth ring gear NC4 is the rotational speed of the fourth carrier, NS4 is the rotational speed of the fourth sun gear, and ■4 is the radius ratio of the fourth ring gear and the fourth sun gear.

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 the second embodiment, the respective radius ratios are I1 = 6.500, I2 = 0.548, ■3=0.
500, ■4=0.562, and each clutch CL1, CL2 and each brake B1,
Table 2A summarizes the relationship between the operations of B2, B3, and B4 and the reduction ratio of each gear, and Table 2B summarizes the relationship between the rotational speed and tangential force between each gear and each gear set. It becomes like this.

Next, a third embodiment of the present invention will be described based on FIG. 3, but since it is roughly the same as the first embodiment described above, the added configuration will be explained.

A single-pinion fourth planetary gear set X4 disposed behind the third planetary gear set X3 includes a fourth sun gear S4 connected to the output shaft, a fifth planetary gear P5 meshing with the fourth sun gear S4, and a fifth planetary gear set X4. It is composed of a fourth ring gear RG4 that meshes with the planetary gear P5 and is connected to the first carrier C1, the second carrier C2, and the third sun gear S3, and a fourth carrier C4 that pivotally supports the fifth planetary gear P5. .

The difference from the first embodiment described above is that the fourth brake B4 is
The carrier C4 is arranged so as to be secured to the case.

That is, the fourth brake B4 does not fix the second sun gear S2 and the third carrier C3 to the case.

Here, by using the calculation formula explained in the first embodiment, and illustrating the specific numerical values of each gear in the third embodiment, the radius ratios are: ■1 = 0.500, I2 = 0.548 , I3=0.
500, I4=0.562, each clutch CL1, CL2 and each brake B1, in 5 forward speeds and 3 reverse speeds.
Table 3A summarizes the relationship between the operations of B2, B3, and B4 and the reduction ratio of each gear, and Table 3B summarizes the relationship between the rotation speed and tangential force between each gear and each gear set. It becomes like this.

Next, a fourth embodiment of the present invention will be described based on FIG. 4, but since it is roughly the same as the first embodiment described above, only the added configuration will be explained.

A single-pinion fourth planetary gear set X4 disposed behind the third planetary gear set X3 includes a fourth sun gear S4 connected to the first ring gear RG1, a fifth planetary gear P5 meshing with the fourth sun gear S4, and a fifth planetary gear P5 meshing with the fourth sun gear S4. The fourth ring gear RG4 meshes with the fifth planetary gear P5 and is connected to the output shaft, and the fourth carrier C4 pivotally supports the fifth planetary gear P5.

Note that when the third brake B3 is operated, the fourth sun gear S4 is fixed to the case.

The difference from the first embodiment described above is that the fourth brake B4 is
The carrier C4 is arranged so as to be secured to the case.

That is, the fourth brake B4 is not arranged to secure the second sun gear S2 and the third carrier C3 to the case.

Here, if we use the calculation formula explained in the above-mentioned first embodiment to give an example of specific numerical values for each gear stage in the fourth embodiment, each radius ratio is I1 = 0.500, I2 = 0.548, I3=0.
500, I4=0.562, each clutch CL1, CL2 and each brake B1, in 5 forward speeds and 3 reverse speeds.
Table 4A summarizes the relationship between the operations of B2, B3, and B4 and the reduction ratio of each gear, and Table 4B summarizes the relationship between the rotation speed and tangential force between each gear and each gear set. It will be like that.

Next, a fifth embodiment of the present invention will be described based on FIG. 5, but since it is roughly the same as the first embodiment described above, only the added configuration will be explained.

A single-pinion fourth planetary gear set X4 disposed behind the third planetary gear set X3 includes a fourth sun gear S4 connected to the first carrier C1, the second carrier C2, and the third sun gear S3; a fifth planetary gear P5 meshing with S4; and a fourth planetary gear P5 meshing with the fifth planetary gear P5 and connected to the output shaft.
It is composed of a ring gear RG4 and a fourth carrier C4 that pivotally supports a fifth planetary gear P5.

The difference from the first embodiment described above is that the fourth brake B4 is
The carrier C4 is arranged so as to be secured to the case.

That is, the fourth brake B4 is not arranged to secure the second sun gear S2 and the third carrier C3 to the case.

Here, by using the calculation formula explained in the first embodiment, and illustrating the specific numerical values of each gear stage in the fifth embodiment, each radius ratio is I1 = 0.500, I2 = 0.548, I3=0.
500, I4=0.437, and each clutch CL1, CL2 and each brake B1, in 5 forward speeds and 3 reverse speeds.
Table 5A summarizes the relationship between the operations of B2, B3, and B4 and the reduction ratio of each gear, and Table 5B summarizes the relationship between the rotational speed and tangential force between each gear and each gear set. It becomes like this.

Next, a sixth embodiment of the present invention will be described based on FIG. 6, but since it is roughly the same as the first embodiment described above, only the added configuration will be explained.

A single-pinion fourth planetary gear set X4 disposed behind the third planetary gear set X3 has a fourth sun gear S4, a fifth planetary gear P5 that meshes with the fourth sun gear S4, and a fifth planetary gear P5 that meshes with the fifth planetary gear P5 and the It is composed of a third ring gear RG3, a fourth ring gear connected to the output shaft, and a fourth carrier C4 pivotally supporting the fifth planetary gear P5 and connected to the first ring gear RGI.

Note that when the third brake B3 is operated, the fourth carrier CC4 is fixed to the case.

The difference from the first embodiment described above is that the fourth brake B4 is
The sun gear S4 is arranged so as to be secured to the case.

That is, the fourth brake B4 does not fix the second sun gear S2 and the third carrier C3 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 the sixth embodiment, the respective radius ratios are I1 = 0.500, I2 = 0.548, I3=0.
500, I4=0.562, each clutch CL1, CL2 and each brake B1, in 5 forward speeds and 3 reverse speeds.
Table 6A summarizes the relationship between the operations of B2, B3, and B4 and the reduction ratio of each gear, and table 6B summarizes the relationship between the rotational speed and tangential force between each gear and each gear set.
It will look like a table.

The following seventh embodiment of the present invention will be described based on FIG. 7, but since it is roughly the same as the first embodiment described above, only the added configuration will be described.

A single pinion fourth planetary gear set X4 disposed behind the third planetary gear set X3 includes a fourth sun gear S4 connected to the output shaft, a fifth planetary gear P5 meshing with the fourth sun gear S4, and a fifth planetary gear. It is composed of a fourth ring gear RG4 that meshes with P5 and is connected to the first carrier C1, second carrier C2, and third sun gear S3, and a fourth carrier C4 that pivotally supports the fifth planetary gear P5.

The difference from the first embodiment described above is that the fourth brake B4 is
The carrier C4 is arranged so as to be secured to the case.

That is, the fourth brake B4 is not arranged to secure the second sun gear S2 and the third carrier C3 to the case.

Here, if we exemplify the specific numerical values of each gear stage in the seventh embodiment using the calculation formula explained in the first embodiment, each radius ratio is I1 = 0.500, I2 = 0.548 , I3=0
．． 500, I4=0.280, 5 forward speeds, 2 reverse speeds
Each clutch CL1, CL2 and each brake B1 in the stage
, B2, B3, B4 and the reduction ratio of each gear stage are summarized as shown in Table 7A, and the relationship between the rotational speed and tangential force of each gear stage and each gear set is summarized in Table 7B.
It will look like a table.

Next, an eighth embodiment of the present invention will be described based on FIG. 8, but since it is roughly the same as the first embodiment described above, only the added configuration will be explained.

A single-pinion fourth planetary gear set X4 disposed behind the third planetary gear set X3 includes a fourth sun gear S4 connected to the output shaft, a fifth planetary gear P5 meshing with the fourth sun gear S4, and a fifth planetary gear P5. It is composed of a fourth ring gear RG4 that meshes with P5, and a fourth carrier C4 that pivotally supports the fifth planetary gear P5 and is connected to the first ring gear RG1.

Note that when the third brake B3 is operated, the fourth carrier C4 is fixed to the case.

The difference from the first embodiment described above is that the fourth brake B4 is
The ring gear RG4 is arranged so as to be secured to the case.

That is, the fourth brake B4 is not arranged to secure the second sun gear S2 and the third carrier C3 to the case.

Here, if we exemplify the numerical values of the specific gears of the eighth embodiment using the calculation formula explained in the first embodiment, the respective radius ratios are I1 = 0.500, I2 = 0.548, I3=0.
500, I4=0.562, each clutch CL1, CL2 and each brake B1, in 5 forward speeds and 3 reverse speeds.
Table 8A summarizes the relationship between the operation of B2, B3, and B4 and the reduction ratio of each gear, and Table 8B summarizes the relationship between the rotation speed and tangential force between each gear and each gear set. It becomes like this.

Next, a ninth embodiment of the present invention will be described based on FIG. 9, but since it is roughly the same as the first embodiment described above, only the added configuration will be explained.

A single-punion fourth planetary gear set X4 disposed behind the third planetary gear set X3 includes a fourth sun gear S4 connected to the output shaft, a fifth planetary gear P5 meshing with the fourth sun gear S4, and a fifth planetary gear set X4. A fourth ring gear RG4 that meshes with the planetary gear P5, and a fourth ring gear RG4 that pivotally supports the fifth planetary gear P5 and the first carrier C.
1 and a fourth carrier C4 connected to the second carrier C2 and the third sun gear S3.

The difference from the first embodiment described above is that the fourth brake B4 is
The ring gear RG4 is arranged so as to be secured to the case.

That is, the fourth brake B4 is not arranged to secure the second sun gear S2 and the third carrier C3 to the case.

Here, if we exemplify the specific numerical values of each gear stage in the ninth embodiment using the calculation formula explained in the first embodiment, each radius ratio is ■1 = 0.50, I2 = 0.548 , I3=0.5
00, I4=0.562, and each clutch CL1, CL2 and each brake B1, B in 5 forward speeds and 2 reverse speeds
Table 9A summarizes the relationship between the operations of 2, B3, and B4 and the reduction ratio of the gears, and Table 9B summarizes the relationship between the rotational speed and tangential force between each gear and each gear set. become.

Next, a tenth embodiment of the present invention will be described based on FIG. 10. Since it is roughly the same as the first embodiment described above, only the added structure will be described. The single pinion type fourth planetary gear set X4 provided is the first ring gear RG.
1, a fifth planetary gear P5 that meshes with the fourth sun gear S4, a fourth ring gear FtG4 that meshes with the fifth planetary gear P5, and a fourth ring gear FtG4 that pivotally supports the fifth planetary gear P5 and is connected to the output shaft. and a fourth carrier C4.

Note that when the third brake B3 is operated, the fourth sun gear S4 is fixed to the case.

The difference from the first embodiment described above is that the fourth brake B4 is
The ring gear RG4 is arranged so as to be secured to the case.

That is, the fourth brake B4 is not arranged to secure the second sun gear S2 and the third carrier C3 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 the 10th embodiment, each radius ratio is I1 = 0.500, I2 = 0.548, ■3=0
．． 500,■4=0.437, 5 forward speeds, 3 reverse speeds
Each clutch CL1, CL2 and each brake B1 in the stage
, B2, B3, B4 and the reduction ratio of each gear stage are summarized as shown in Table 10A, and the relationship between the rotational speed and tangential force of each gear stage and each gear set is summarized as Table 1.
It will look like the 0B table.

Next, an eleventh embodiment of the present invention will be described based on FIG. 11, but since it is roughly the same as the first embodiment described above, only the added configuration will be explained.

A single-pinion fourth planetary gear set X4 disposed behind the third planetary gear set X3 includes a fourth sun gear S4 connected to the first carrier C1, the second carrier C2, and the third sun gear S3; It is composed of a fifth planetary gear P5 that meshes with the sun gear S4, a fourth ring gear RG4 that meshes with the fifth planetary gear P5, and a fourth carrier C4 that pivotally supports the fifth planetary gear P5 and is connected to the output shaft.

The difference from the first embodiment described above is that the fourth brake B4 is
The ring gear RG4 is arranged so as to be secured to the case.

That is, the fourth brake B4 is not arranged to secure the second sun gear S2 and the third carrier C3 to the case.

Here, if we use the calculation formula explained in the first embodiment and give an example of the specific numerical values of each gear stage in the 11th embodiment, each radius ratio is I1 = 0.500, I2 = 0.548, I3=0
．． 500, I4=0.437, 5 forward speeds, 2 reverse speeds
Each clutch CL1, CL2 and each brake B1 in the stage
, B2, B3, B4 and the reduction ratio of each gear stage are summarized as shown in Table 11A, and the relationship between the rotational speed and tangential force of each gear stage and each gear set is summarized as Table 1.
It will look like table 1B.

Next, a twelfth embodiment of the present invention will be described based on FIG. 12, but since it is roughly the same as the first embodiment described above, only the added configuration will be explained.

A single-pinion fourth planetary gear set X4 disposed behind the third planetary gear set X3 has a fourth sun gear S4, a fifth planetary gear P5 that meshes with the fourth sun gear S4, and a fifth planetary gear P5 that meshes with the fifth planetary gear P5. It is composed of a fourth ring gear RG4 connected to the first ring gear RG1, and a fourth carrier C4 pivotally supporting the fifth planetary gear P5 and connected to the third ring gear RG3 and the output shaft.

Note that when the third brake B3 is operated, the fourth ring gear RG4 is fixed to the case.

The difference from the first embodiment described above is that the fourth brake B4 is
The sun gear S4 is arranged so as to be secured to the case.

That is, the fourth brake B4 is not arranged to secure the second sun gear S2 and the third carrier C3 to the case.

Here, by using the calculation formula explained in the first embodiment, and illustrating the specific numerical values of each gear stage in the 12th embodiment, the radius ratios are I1 = 0.500, I2 = 0.548, I3=0
．． 500, I4=0.562, 5 forward speeds, 2 reverse speeds
Each clutch C in the stage = L1, CL2 and each brake B
Table 12A summarizes the relationship between the operations of 1, B2, B3, and B4 and the reduction ratio of each gear, and table 12B summarizes the relationship between the rotational speed and tangential force between each gear and each gear set. It will look like the table.

Next, a thirteenth embodiment of the present invention will be described based on FIG. 13, but since it is roughly the same as the first embodiment described above, only the added configuration will be explained.

A single-pinion fourth planetary gear set X4 disposed behind the third planetary gear set X3 has a fourth sun gear S4, a fifth planetary gear P5 that meshes with the fourth sun gear S4, and a fifth planetary gear P5 that meshes with the fifth planetary gear P5. A fourth ring gear RG connected to the first carrier C1, the second carrier C2, and the third sun gear S3.
4, and a fourth carrier C4 that pivotally supports the fifth planetary gear P5 and is connected to the third ring gear RG3 and the output shaft.

The difference from the first embodiment described above is that the fourth brake B4 is
The sun gear S4 is arranged so as to be secured to the case.

That is, the fourth brake B4 is not arranged to secure the second sun gear S2 and the third carrier C3 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 the 13th embodiment, the respective radius ratios are I1 = 0.500, I2 = 0.548, I3=0
．． 500, I4=0.320, 6 forward speeds, 2 reverse speeds
Each clutch CL1, CL2 and each brake B1 in the stage
, B2, B3, B4 and the reduction ratio of each gear stage are summarized as shown in Table 13A, and the relationship between the rotational speed and tangential force of each gear stage and each gear set is summarized as Table 13A.
It will look like table 3B.

Next, a fourteenth embodiment of the present invention will be described based on FIG. 14, but since it is roughly the same as the first embodiment described above, only the added configuration will be explained.

A single-pinion fourth planetary gear set X4 disposed behind the third planetary gear set X3 has a fourth sun gear S4, a fifth planetary gear P5 that meshes with the fourth sun gear S4, and a fifth planetary gear P5 that meshes with the fifth planetary gear P5. Second sun gear S2 and the third carrier C3
and a fourth carrier C4 that pivotally supports the fifth planetary gear P5 and is connected to the third ring gear RG3 and the output shaft.

The difference from the first embodiment described above is that the fourth brake B4 is
The sun gear S4 is arranged so as to be secured to the case.

That is, the fourth brake B4 is not arranged to secure the second sun gear S2 and the third carrier C3 to the case.

Here, if we exemplify the specific numerical values of each gear stage in the 14th embodiment using the calculation formula explained in the above-mentioned first embodiment, each radius ratio is ■1 = 0.500, I2 = 0.548 , I3=0
．． 500, I4=0.280, 6 forward speeds, 2 reverse speeds
Each clutch CL1, CL2 and each brake B1 in the stage
, B2, B3, B4 and the reduction ratio of each gear stage are summarized as shown in Table 14A, and the relationship between the rotation speed and tangential force of each gear stage and each gear set is summarized as Table 14A.
It will look like table 4B.

Next, a fifteenth embodiment of the present invention will be described based on FIG. 15, but since it is roughly the same as the first embodiment described above, only the added configuration will be explained.

A single-pinion fourth planetary gear set X4 disposed behind the third planetary gear set X3 includes a fourth sun gear S4 connected to the second sun gear S2 and the third carrier C3, and a fourth sun gear S4 that meshes with the fourth sun gear S4. 5
Planetary gear P5, fourth ring gear RG4 meshing with the 15th planetary gear P5, and fifth planetary gear P
5, and a fourth carrier C4 that is connected to the third ring gear RG3 and the output shaft.

The difference from the first embodiment described above is that the fourth brake B4 is
The ring gear RG4 is arranged so as to be secured to the case.

That is, the fourth brake B4 is not arranged to secure the second sun gear S2 and the third carrier C3 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 the 15th embodiment, each radius ratio is I1 = 0.500, I2 = 0.548 ,I3=
0.500, I4=0.280, and each clutch CL1, CL2 and each brake B in 5 forward speeds and 3 reverse speeds
Table 15A summarizes the relationship between the operations of 1, B2, B3, and B4 and the reduction ratio of each gear, and table 15B summarizes the relationship between the rotational speed and tangential force between each gear and each gear set. It will look like the table.

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

(1) A first sun gear, a first planetary gear that meshes with the first sun gear, a first ring gear that meshes with the first planetary gear, a first carrier that pivotally supports the first planetary gear, a second sun gear, and a second planetary gear that meshes with the second sun gear. A planetary gear, a second ring gear that meshes with the second planetary gear and is connected to the first sun gear, a second carrier that pivotally supports the second planetary gear and is connected to the first carrier, and a third sun gear that is connected to the first carrier and the second carrier. , a third planetary gear that meshes with the third sun gear, a fourth planetary gear that meshes with the third planetary gear, a third ring gear that meshes with the fourth planetary gear and is connected to the output shaft, a third planetary gear that pivotally supports the third planetary gear, and a fourth planetary gear. The third carrier is connected to the second sun gear, and the second
A first clutch that simultaneously releases or connects the sun gear and the third carrier; a second clutch that simultaneously releases or connects the first sun gear and the second ring gear from the input shaft; and a second clutch that simultaneously releases or connects the first sun gear and the second ring gear to the case. A first brake, a second brake capable of simultaneously securing the first carrier, second carrier, and third sun gear to the case; a third brake capable of securing the first ring gear to the case; a third brake capable of simultaneously securing the second sun gear and third carrier to the case; A transmission consisting of 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 connected to the output shaft, a fifth planetary gear meshing with the fourth sun gear, a fourth ring gear meshing with the fifth planetary gear and connected to the first ring gear, and a fourth carrier pivotally supporting the fifth planetary gear are added. and a transmission configured such that the fourth brake can secure the fourth carrier to the case.

(3) In the transmission having the configuration described in item (1) above,
a fourth sun gear connected to the output shaft; a fifth planetary gear meshing with the fourth sun gear; a fourth ring gear meshing with the fifth planetary gear and connected to the first carrier, the second carrier, and the third sun gear; A transmission device further includes a fourth carrier that pivotally supports a planetary gear, and is arranged such that the fourth brake can fix the fourth carrier to a case.

(4) In the transmission having the configuration described in item (1) above,
A fourth sun gear connected to the first ring gear, a fifth planetary gear meshing with the fourth sun gear, a fourth ring gear meshing with the fifth planetary gear and connected to the output shaft, and a fourth carrier pivotally supporting the fifth planetary gear are added. and a transmission arranged such that the fourth brake can secure the fourth carrier to the case.

(5) In the transmission having the configuration described around (1) above,
a fourth sun gear connected to the first carrier, the second carrier and the third sun gear; a fifth planetary gear meshing with the fourth sun gear; a fourth ring gear meshing with the fifth planetary gear and connected to the output shaft; A transmission that includes a fourth carrier that pivotally supports a planetary gear, and is arranged such that the fourth brake can tighten the fourth carrier.

(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 connected to the third ring gear and the output shaft, a fourth ring gear that pivotally supports the fifth planetary gear and is connected to the first ring gear. A transmission device further comprising: a fourth carrier which is arranged so that the fourth brake can securely fasten the fourth sun gear to the case;

(7) In the transmission having the configuration described in item (1) above,
a fourth sun gear connected to the output shaft; a fifth planetary gear meshing with the fourth sun gear; a fourth ring gear meshing with the fifth planetary gear and connected to the first carrier, the second carrier, and the third sun gear; A transmission device further includes a fourth carrier that pivotally supports a planetary gear, and is arranged such that the fourth brake can push the fourth carrier into a case.

(8) In the transmission having the configuration described in item (1) above,
A fourth sun gear coupled to the output shaft, a fifth planetary gear meshing with the fourth sun gear, a fourth ring gear meshing with the fifth planetary gear, and a fourth carrier pivotally supporting the fifth planetary gear and coupled to the first ring gear are added. The transmission is arranged such that the fourth brake can securely fasten the fourth ring gear to the case.

(9) In the transmission having the configuration described in item (1) above,
a fourth sun gear connected to the output shaft; a fifth planetary gear meshing with the fourth sun gear; a fourth ring gear meshing with the fifth planetary gear; A fourth carrier connected to the third sun gear is added, and the fourth carrier is connected to the third sun gear.
A transmission device arranged such that a brake can secure the fourth ring gear to a case.

(10) In the transmission having the configuration described in item (1) above, a fourth sun gear connected to the first ring gear, a fifth planetary gear meshing with the fourth sun gear, a fourth ring gear meshing with the fifth planetary gear, A transmission that includes a fourth carrier that pivotally supports a fifth planetary gear and is connected to the output shaft, and is arranged so that the fourth brake can secure the fourth ring gear to the case.

(11) In the transmission having the configuration described in item (1) above, a fourth sun gear connected to the first carrier, the second carrier, and the third sun gear, a fifth planetary gear meshing with the fourth sun gear, The fourth planetary gear meshes with the fifth planetary gear.
A transmission device further includes a fourth carrier that pivotally supports a ring gear and a fifth planetary gear and is connected to the output shaft, and is arranged such that the fourth brake can fix the fourth ring gear to a 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 fourth ring gear that meshes with the fifth planetary gear and is connected to the first ring gear. , a transmission which is provided with a fourth carrier that pivotally supports a fifth planetary gear and is connected to the third ring gear and the output shaft, and is arranged so as to be able to secure the fourth sun gear to the case.

(13) In the transmission having the configuration described in item (1) above, a fourth sun gear, a fifth planetary gear meshing with the fourth sun gear, a fifth planetary gear meshing with the fifth planetary gear, and the first carrier, the second carrier, A fourth ring gear coupled to the third sun gear pivotally supports a fifth planetary gear, and a fourth carrier coupled to the third ring gear and the output shaft is added, and the fourth brake fixes the fourth sun gear to the case. The transmission is arranged so as to obtain the desired results.

(14) 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 also connects the second sun gear and the third carrier. The fourth ring gear to be connected,
A transmission including a fourth carrier that pivotally supports a fifth planetary gear and is connected to the third ring gear and the output shaft, and is arranged so that the fourth brake can secure the fourth sun gear to the case.

(15) In the transmission having the configuration described in item (1) above, a fourth sun gear that is connected to the second sun gear and the third carrier, a fifth planetary gear that meshes with the fourth sun gear, and a fifth planetary gear that meshes with the fifth planetary gear. A fourth carrier is added that pivotally supports a matching fourth ring gear and a fifth planetary gear and is connected to the third ring gear and the output shaft, and
A transmission device arranged so that the brake can secure the fourth ring gear to the case.

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

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

(18) A transmission having the configuration described in item (3) above, in which the fourth brake 6 is 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 third brake is removed.

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

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

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

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

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

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

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

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

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

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

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

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

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

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

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

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

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

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

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

As is clear from the above description, according to the present invention, it is possible to provide a transmission device capable of shifting at least four forward speeds and one reverse speed, which achieves the initial objective, and makes a great contribution to industry.

[Brief explanation of the drawing]

1 to 15 are center vertical cross-sectional views diagrammatically showing the first to fifteenth embodiments of the present invention, respectively. X1, X2, X3, X4... Planetary gear set, S1, S2, 83, 84... Sun gear,
P1, P2, P3, P4, P5...Planetary gear, RG1, RG2, RG3, RG4...Ring gear, C1, C2, C3, C4...Carrier, CL1, CL2・・・・・・Clutch, B1, B2
, B3, B4... 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 king gear, a ring gear, and a planetary gear that connects the meshing linkage between the two gears, and a case that is a fixed member. Single pinion type 1st
Both carriers of the second planetary gear set and the sun gear of the double-pinion third planetary gear set are drivingly connected, the sun gear of the first planetary gear set and the ring gear of the second planetary gear set are drivingly connected, 2 planetary gear set sun gear and 3rd
The carrier of the planetary gear set is drivingly connected, the ring gear of the third planetary gear set is drivingly connected to the output shaft, and the sun gear of the second planetary gear set and the carrier of the third planetary gear set are connected. the first to couple or release the input shaft with respect to the input shaft;
clutch, the sun gear of the first planetary gear set and the second
a second clutch that connects or releases the ring gear of the planetary gear set with respect to the input shaft;
and one in which the sun gear of the first planetary gear set and the ring gear of the second planetary gear set are connected, one in which both the carriers of the first and second planetary gear sets and the sun gear of the third planetary gear set are connected, A brake capable of fixing any one of the four ring gears of the first planetary gear set to the case, the sun gear of the second planetary gear set and the carrier of the third planetary gear set being connected; A transmission device comprising: another brake that can be secured to the case; and another brake that can be secured to the case. 2. 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 first 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. 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 connected to both the carriers of the first and second planetary gear sets and the carrier of the fourth planetary gear set. The sun gear of the third planetary gear set is drivingly connected to the connected one and the other is drivingly connected to the output shaft, and the sun gear, the ring gear of the fourth planetary gear set,
A transmission comprising a further braking device capable of securing the remaining parts of the carrier to the case. 4. In the first invention described in the claims, any two of the sun gear, ring gear, and carrier of the fourth planetary gear set may be replaced with the sun gear of the second planetary gear set and the sun gear of the third planetary gear set. The carrier is drivingly connected to the connected one 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 can be fixed to the case. A transmission device that is equipped with a separate braking device.