JPS5844900B2 - Hensoku house - 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 vehicles, particularly automobiles.

It is desirable that a gear type auxiliary device 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.

Although a large number of combinations of transmissions are possible, it is desirable that the following conditions be satisfied.

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

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

(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 satisfies the meshing conditions, and the sun gear and planetary gear, which have the smallest diameter, also have the required number of teeth or more.

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

(6) When changing gears while driving, the frictional engagement means is switched to change gears, but this switching is done in order to reduce the switching shock.
What can be done by switching only one piece.

In consideration of these conditions, the present invention basically uses three sets of single pinion simple planetary gear sets, basically uses two clutch devices, and basically three brake devices, and each planetary gear The object of the present invention is to provide a transmission having at least four forward speeds and one reverse speed by appropriately connecting movable members of a set and appropriately connecting and disengaging a clutch device and a brake device.

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

The first embodiment of the device of the present invention will be explained with reference to FIG.
is a commonly known three-element, one-stage, two-phase torque converter, which includes a pump impeller 11 connected to an engine output shaft 20.
．． The stator wheel 14 is supported by a turbine runner 12 connected to an input shaft 21 and a case 100 via a one-way brake 13.

A first planetary gear set 30, a second planetary gear set 40, and a third planetary gear set 50 of single pinion type are present between the input shaft 21 and the output shaft 22.

The first planar gear set 30 includes a first sun gear 31
A first planetary gear 32 that meshes with the first sun gear, a first ring gear 33 that meshes with the first planetary gear, and a first carrier 34 that pivotally supports the first planetary gear 32.

Similarly, the second planetary gear set 40 includes a second sun gear 41 and a second planetary gear 4 that meshes with the second sun gear.
2, a second ring gear 43 that meshes with the second planetary gear 42, and a second carrier 44 that pivotally supports the second planetary gear 42.

The third planetary gear set 50 includes a third sun gear 51, a third planetary gear 52 that meshes with the third sun gear, a third ring gear 53 that meshes with the third planetary gear 52, and a third planetary gear 53 that pivotally supports the third planetary gear 52. carrier 54
and has.

A first clutch 61 is disposed between the input shaft 21 and the third ring gear 53 to integrally connect or disconnect the input shaft 21 and the third ring gear 53.

The first, second, and third sun gears 31.41.51 are drivingly connected to each other, and there are a second clutch 62 that integrally connects and disconnects the input shaft 21 and the first, second, and third sun gears 31, 41, and 51;
is installed.

The first, second, and third sun gears 31.41. A first brake 71 is provided between the case 100 and the first brake 71, and when the brake is operated, the first, second, . The third sun gear 31, 41, 51 can be fixed.

The first carrier 34 and the second carrier 44 are integrally fixed, and a second brake γ2 is provided between the first and second carriers 34, 44 and the case 100,
When the brake is activated, the first and second carriers 3
4.44 can be fixed.

A third brake 73 is provided between the first ring gear 33 and the case 100, and is configured to clamp the first ring gear 33 when the brake is activated.

The second ring gear 43 and the third carrier 54 are drivingly connected and are integrally and dynamically connected to the output shaft 22.

And single pinion simple planetary gear set 3
The following equation holds true at 0.40.50.

N□, -(1,+I,)Nc1+11NS1=ONR
2(1+12)Nc2+l2NS2=ON, -(1,+
l3) No3+l3Ns3=0 However, NR1, NR2, NR3: Number of rotations Ncl of the first, second, third ring gear, NO3, NO3: Number of rotations Nsl, Ns2 of the first, second, third carrier. Ns3: Number of revolutions of the first, second, and third sun gear ■1, ■2, ■3: Radius ratio of each ring gear and each sun gear.

Here, specific numerical values of each gear stage of the transmission according to the present invention are as follows: I, = 0.320, I2 = 0.
600.

I3=0.520, and each clutch 61, 62 and each brake 71 .
The operation of 72.73 and the reduction ratio of each gear stage are summarized in the following table.

The rotation speed and tangential force of each element of each planetary gear set at each gear stage are summarized as shown in FIG. 2.

(The value is expressed as a ratio with the input shaft as 1. However, the tangential force is expressed as a ratio with 1 assuming that the torque of the input shaft acts on the ring gear.

The same shall apply hereinafter. ) However, A is the gear stage, B is the item of the planetary gear set, N is the rotation speed, W is the tangential force, and Fn (n = 1..2, 3...) is the forward gear stage. For example, FIFt is the first speed, F2 is the second speed,
Further, Rn (n=1, 2.3, . . . ) indicates a reverse speed, and for example, R1 indicates a first reverse speed (the same applies hereinafter).

). Furthermore, I4. I2. I3: First, second and third planetary gear sets Sl, S2. S3: 1st, 2nd, 3rd sun gear C1, C
2, C3: first, second, and third carriers RG, , Nc2
．． Nc3: first, second, and third ring gears P1. F2.
F3: 1st, 2nd, and 3rd planetary gears, and F4 (4th speed) has a reduction ratio of 1:1. OO, the rotational speed N of each sun gear, ring gear, and carrier is 1.00, and the rotational speed N of each planetary gear is 0.00, and the tangential force W is It is significantly smaller than the tangential force generated,
That is, in other gears, the torque of the input shaft is transmitted to each element only through the engaged clutch due to collapse of each clutch or engagement of only one clutch, whereas in F4 In (4th speed), the input shaft torque is shared by both clutches by engaging at least two clutches, and the shared input shaft torque is transmitted to each element. It is obvious that the tangential force of each element generated by this is smaller than when the torque of the input shaft is transmitted as is without being shared due to the engagement of only one clutch. The rotational speed N and tangential force W of each element in the gear stage are omitted.

Next, a second embodiment of the device of the present invention will be explained with reference to FIG.
This embodiment has a configuration in which a single pinion type fourth planetary gear set 80 is interposed between the third planetary gear set 50 and the output shaft 22 in the previous embodiment, and the connection relationship with each element is as follows. It is.

The fourth planetary gear set 80 includes a fourth sun gear 81.
A fourth planetary gear 82 that meshes with the fourth sun gear, a fourth ring gear 83 that meshes with the fourth planetary gear, and a fourth carrier 84 that pivotally supports the fourth planetary gear 82.

The fourth ring gear 83 is connected to the first ring gear 33 and 1.
The fourth ring gear 83 is connected in a driving manner, and when the third brake 73 is activated, the fourth ring gear 83 is fixed in the same manner as the first ring gear 33.

A fourth brake 74 is provided between the fourth carrier 84 and the case 100, and is configured to clamp the fourth carrier when the brake is activated.

The fourth sun gear 81 is drivingly connected to the second ring gear 43 and the third carrier 54, and is integrally and dynamically connected to the output shaft 22.

And single pinion simple planetary gear set 3
The following equation is obtained at 0.40.50.80.

NRt (1+II) Nc, +II Nsl
= 0NR2(1+I2) Nc2+I2N
S2 = 0NR3(1+I3) NOa + l
3NS3= 0NR4(1+I4) NO4+l
4NS4=0 However, NR1' NR2t NR3, NR4: 1st, 2nd, 3rd, 4th ring gear Ncl, Nc2. Nc3. Nc4: first, second, third,
Number of revolutions of the fourth carrier NSt l N82 t Ni93 t N34 ' Number of revolutions of the first, second, third, and fourth sun gear ■1. ■2. ■3. ■4: Radius ratio of each ring gear and each sun gear.

Here, specific numerical values of each gear stage of the transmission according to the present invention are exemplified as follows: -o, 32o, l2=0.60
0.

l3=0.520, l4=0.562, and each clutch 61, 62 at each gear stage of the transmission of the present invention
The operation of each brake 71, 72, 73, 74 and the reduction ratio of each gear stage are summarized in the following table.

The rotational speed and tangential force of each element of each planetary gear set at each gear stage are summarized as shown in FIG. 4.

However, Xl, X2. X3. X4: 1st, 2nd, 3rd, 4th planetary gear set Sl, S2. S3. S4: 1st, 2nd, 3rd, 4th sun gear 'C1, C2, C3, C4: 1st, 2nd, 3rd, 4th carrier RGl, RG2. RG3. RG, :1st, 2nd
, third and fourth ring gears Pt, P2 p P3 t P4 : first, second, third and fourth planetary gears.

Next, a third embodiment of the device of the present invention will be explained with reference to FIG.
Similar to the second embodiment, this embodiment has the third planetary gear set 50 and the output shaft 2 in the first embodiment.
2, a single pinion type fourth planetary gear set 80 is interposed between the two, and the connection relationship with each element is as follows.

The fourth ring gear 83 is drivingly connected to the first carrier 34 and the second carrier 44, and when the second brake 72 is operated, the fourth ring gear 83 is connected to the first carrier 34 and the second carrier 44. 83 is fixed.

A fourth brake 74 is provided between the fourth carrier 84 and the case 100, and is configured to clamp the fourth carrier when the brake is activated.

The fourth sun gear 81 is drivingly connected to the second ring gear 43 and the third carrier 54, and is integrally and dynamically connected to the output shaft 22.

Here, specific numerical values of each gear stage of the transmission according to the present invention are exemplified as follows: 11=0.320, l2=0.60
0.

l3=0.520, l4=0.562, and each clutch 61.62 in each gear of the transmission of the present invention
The operation of each brake 71, 72, 73, 74 and the reduction ratio of each gear stage are summarized in the following table.

The rotational speed and tangential force of each element of each planetary gear set at each gear stage are summarized as shown in FIG. 6.

Next, a fourth embodiment of the device of the present invention will be explained with reference to FIG.
Similar to the second embodiment, this embodiment has the third planetary gear set 50 and the output shaft 2 in the first embodiment.
2, a single pinion type fourth planetary gear set 80 is interposed between the two, and the connection relationship with each element is as follows.

The fourth sun gear 81 is connected to the first ring gear 33 in a 7-drive manner, and when the third brake 73 is operated,
Similar to the first ring gear 33, the fourth sun gear 81
is fixed.

A fourth brake 74 is provided between the fourth carrier 84 and the case 100, and is configured to lock the fourth carrier 84 when the brake is activated.

The fourth ring gear 83 drivingly connects the second ring gear 43 to the third carrier 54 and is integrally and dynamically connected to the output shaft 22 .

Here, specific numerical values of each gear stage of the transmission according to the present invention are exemplified as follows: 11=0.320, l2=0.60
0.

I3=0.520, I4=0.562,
Each clutch 61 in each gear of the transmission of the present invention,
The operation of 62 and each brake 71, 72, 73, 74 and the reduction ratio of each gear stage are summarized in the following table.

The rotational speed and tangential force of each element of each planetary gear set at each gear stage are summarized as shown in FIG. 8.

Next, a fifth embodiment of the device of the present invention will be explained with reference to FIG.
Similar to the second embodiment, this embodiment has the third planetary gear set 50 and the output shaft 2 in the first embodiment.
2, a single pinion type fourth planetary gear set 80 is interposed between the two, and the connection relationship with each element is as follows.

The fourth sun gear 81 is connected to the first and second carriers 34 .
44, and is locked in the same manner as the first and second carriers 34, 44 when the second brake 72 is activated.

A fourth brake 74 is provided between the fourth carrier 84 and the case 100, and is configured to lock the fourth carrier 84 when the brake is activated.

The fourth ring gear 83 is drivingly connected to the second ring gear 43 and the third carrier 54, and is also dynamically connected integrally to the output shaft 22.

Here, to give an example of specific numerical values of each gear stage of the transmission according to the present invention, 11=0.320. l2=0.600゜l3=0.520, l4=0.437, and each clutch 61, 62 at each gear stage of the transmission of the present invention
The operation of each brake 71, 72, 73, 74 and the reduction ratio of each gear stage are summarized in the following table.

The rotational speed and tangential force of each element of each planetary gear set at each gear stage are summarized as shown in FIG. 10.

Next, a sixth embodiment of the device of the present invention will be described with reference to FIG. 11. Similar to the second embodiment, this embodiment differs from the third planetary gear set 50 and the output shaft 22 in the first embodiment. It has a configuration in which a single pinion type fourth planetary gear set 80 is interposed between them, and the connection relationship with each element is as follows.

The fourth carrier 84 is drivingly connected to the first ring gear 33, and is locked in the same manner as the first ring gear 33 when the third brake 73 is activated.

A fourth brake 74 is provided between the fourth sun gear 81 and the case 100, so that the fourth sun gear 81 can be fixed when the brake is activated.

The fourth ring gear 83 is drivingly connected to the second ring gear 43 and the third carrier 54, and is also dynamically connected integrally to the output shaft 22.

Here, specific numerical values of each gear stage of the transmission according to the present invention are exemplified as follows: 11=0.320, l2=0.60
0.

l3=0.520, l4=0.562, and each clutch 61.62 in the passenger gear of the transmission of the present invention
The operation of each brake 71, 72, 74, 74 and the reduction ratio of each gear stage are summarized in the following table.

The rotational speed and tangential force of each element of each planetary gear set at each gear stage are summarized as shown in FIG. 12.

Next, a seventh embodiment of the device of the present invention will be explained with reference to FIG. 13. In this embodiment, like the second embodiment, the third planetary gear set 50 and the output shaft 22 are connected to each other in the first embodiment. It has a configuration in which a single pinion type fourth planetary gear set 80 is interposed between them, and the connection relationship with each element is as follows.

The fourth carrier 84 is connected to the first and second carriers 34 .
44, and is locked in the same manner as the first and second carriers 34, 44 when the second brake 72 is activated.

A fourth brake T4 is provided between the fourth sun gear 81 and the case 100, so that the fourth sun gear 81 can be fixed when the brake is activated.

The fourth ring gear 83 is drivingly connected to the second ring gear 43 and the A3 carrier 54, and is also dynamically connected integrally to the output shaft 22.

Here, the specific numerical values of each gear of the transmission according to the present invention are I, -0,320, l2 = 0.600° l3 = 0.520, l4 = 0.280, and the present invention Each clutch 61, 62 at each gear stage of the transmission
The operation of each brake 71, 72, 73, 74 and the reduction ratio of each gear stage are summarized in the following table.

The tangential forces of the rotational speed of each element of each planetary gear set at each gear stage are summarized as shown in FIG. 14.

Next, an eighth embodiment of the device of the present invention will be described with reference to FIG. 15. This embodiment is similar to the second embodiment in that the third planetary gear set 50 and the output shaft 22 are connected to each other in the first embodiment. It has a configuration in which a single pinion type fourth planetary gear set 80 is interposed between them, and the connection relationship with each element is as follows.

The fourth carrier 84 is drivingly connected to the first ring gear 33, and is locked in the same manner as the first ring gear 33 when the third brake 73 is activated.

A fourth brake 74 is provided between the fourth ring gear 83 and the case 100, and is configured to clamp the fourth ring gear 83 when the brake is activated.

The fourth sun gear 81 is drivingly connected to the second ring gear 43 and the third carrier 54, and is integrally and dynamically connected to the output shaft 22.

Here, specific numerical values of each gear stage of the transmission according to the present invention are exemplified as follows: 11=0.320, l2=0.60
0.

I3=0.520, I,=0.562,
Each clutch 61 in each gear of the transmission of the present invention,
The operation of 62 and each brake/1.72, 73, 74 and the reduction ratio of each gear stage are summarized in the following table.

The rotational speed and tangential force of each element of each planetary gear set at each gear stage are summarized as shown in Fig. 16.

Next, a ninth embodiment of the device of the present invention will be explained with reference to FIG. 17. Similar to the second embodiment, this embodiment has the same configuration as that of the third planetary gear set 1 and the output shaft 22. A single-pinion type fourth planetary gear set 80 is interposed between the two elements, and the connection relationship with each element is as follows.

The fourth carrier 84 is connected to the first and second carriers 34 .
44, and is locked in the same manner as the first and second carriers 34, 44 when the second brake 72 is activated.

A fourth brake 74 is provided between the fourth ring gear 83 and the case 100, and is configured to clamp the fourth ring gear 83 when the brake is activated.

The fourth sun gear 81 is drivingly connected to the second ring gear 43 and the third carrier 54, and is integrally and dynamically connected to the output shaft 22.

Here, the specific numerical values of each gear of the transmission according to the present invention are I, -0,320, l2=0.600, l3=0.520, l4=0.562, and the present invention Each clutch 61, 62 at each gear stage of the transmission
The operation of each brake 71, 72, 73, 74 and the reduction ratio of each gear stage are summarized in the following table.

The rotational speed and tangential force of each element of each planetary gear set at each gear stage are summarized as shown in FIG. 18.

Next, a tenth embodiment of the device of the present invention will be explained with reference to FIG. 19. Similar to the second embodiment, this embodiment is similar to the second embodiment in that the third planetary gear set 50 and the output shaft 22 are connected to each other in the first embodiment. It has a configuration in which a single pinion type fourth planetary gear set 80 is interposed between them, and the connection relationship with each element is as follows.

The fourth sun gear 81 is connected to the first ring gear 33 in a one-drive manner, and when the third brake 73 is operated,
It is secured similarly to the first ring gear 33.

A fourth brake 74 is provided between the fourth ring gear 83 and the case 100, and is configured to clamp the fourth ring gear 83 when the brake is activated.

The fourth carrier 84 is drivingly connected to the second ring gear 43 and the third carrier 54, and is also dynamically connected integrally to the output shaft 22.

Here, specific numerical values of each gear stage of the transmission according to the present invention are exemplified as follows: 11=0.320, l2=0.60
0°I3=0.520, I4=0.437, and each clutch 6 in each gear of the transmission of the present invention
1, 62 and each brake 71, 72, 73, 74 and the reduction ratio of each gear stage are summarized in the following table.

The rotational speed and tangential force of each element of each planetary gear set at each gear stage are summarized as shown in FIG. 20.

Next, an eleventh embodiment of the device of the present invention will be explained with reference to FIG. A single-pinion type fourth planetary gear set 80 is interposed between the two elements, and the connection relationship with each element is as follows.

The fourth sun gear 81 is connected to the first and second carriers 34 .
44, and when the second brake 72 is activated, it is fixed in the same way as the first and second carriers 34, 44.

A fourth brake 74 is provided between the fourth ring gear 83 and the case 100, and is configured to clamp the fourth ring gear 83 when the brake is activated.

The fourth carrier 84 is drivingly connected to the second ring gear 43 and the third carrier 54, and is also dynamically connected integrally to the output shaft 22.

Here, specific numerical values of each gear stage of the transmission according to the present invention are exemplified as follows: I = 0.320, l2 = 0.6
00°I3=0.520, I,=0.437, and the operation of each clutch 61, 62 and each brake 71, 72, 73, 74 in each gear of the transmission of the present invention and deceleration of each gear The ratios are summarized in the table below.

The rotation speed and tangential force of each element of each planetary gear set at each gear stage are summarized as shown in FIG. 22.

Next, a twelfth embodiment of the device of the present invention will be described with reference to FIG. 23. Similar to the second embodiment, this embodiment has the same structure as that of the third planetary gear set 50 and the output shaft 22 in the first embodiment. It has a configuration in which a single pinion type fourth planetary gear set 80 is interposed between them, and the connection relationship with each element is as follows.

The fourth ring gear 83 and the first ring gear 33,
The third brake 73 is connected in a driving manner, and is locked in the same way as the first ring gear 33 when the third brake 73 is activated.

A fourth brake 74 is provided between the fourth sun gear 81 and the case 100, and when the brake is operated,
The fourth ring gear 83 can be secured.

The fourth carrier 84 is drivingly connected to the second ring gear 43 and the third carrier 54, and is also dynamically connected integrally to the output shaft 22.

Here, specific numerical values of each gear stage of the transmission according to the present invention are exemplified as follows: 11=0.320, l2=0.60
0゜l3=0.520, l4=0.562,
Each clutch 61 in each gear of the transmission of the present invention.
The operation of 62 and each brake 71, 72, 73, 74 and the reduction ratio of each gear stage are summarized in the following table.

The rotational speed and tangential force of each element of each planetary gear set at each gear stage are summarized as shown in FIG. 24.

Next, a thirteenth embodiment of the device of the present invention will be explained with reference to FIG. 25. In this embodiment, like the second embodiment, the third planetary gear set 50 and the output shaft 22 are connected in the first embodiment. It has a configuration in which a single pinion type fourth planetary gear set 80 is interposed between them, and the connection relationship with each element is as follows.

The fourth ring gear 83 is connected to the first and second carriers 34.
．． 44 in a driving manner, and the second brake 72
When the carrier is activated, it is secured in the same manner as the first and second carriers 34 and 44.

A fourth brake 74 is provided between the fourth sun gear 81 and the case 100, and when the brake is operated,
The fourth sun gear 81 can be secured.

The fourth carrier 84 is drivingly connected to the second ring gear 43 and the third carrier 54, and is also dynamically connected integrally to the output shaft 22.

Here, specific numerical values of each gear stage of the transmission according to the present invention are exemplified as follows: 11=0.320, l2=0.60
0゜l3=0.520, l4=0.320,
Each clutch 61 in each gear of the transmission of the present invention,
The operation of 62 and each brake 71, 72, 73, 74 and the reduction ratio of each gear stage are summarized in the following table.

The rotational speed and tangential force of each element of each planetary gear set at each gear stage are summarized as shown in FIG. 26.

Next, a fourteenth embodiment of the device of the present invention will be explained with reference to FIG. 27. Similar to the second embodiment, this embodiment differs from the third planetary gear set 50 and the output shaft 22 in the first embodiment. It has a configuration in which a single pinion type fourth planetary gear set 80 is interposed between them, and the connection relationship with each element is as follows.

The fourth ring gear 83 is drivingly connected to the third ring gear 53.

A fourth brake 74 is provided between the fourth sun gear 81 and the case 100, and when the brake is operated,
The fourth sun gear 81 can be secured.

The fourth carrier 84 is drivingly connected to the second ring gear 43 and the third carrier 54, and is integrally and dynamically connected to the output shaft 22.

Here, specific numerical values of each gear stage of the transmission according to the present invention are exemplified as follows: 11=0.320, l2=0.60
0.

l3=0.520. l4=0.280, and the operation of each clutch 61, 62 and each brake 71, 72, 73, 74 in each gear of the transmission of the present invention and the reduction ratio of each gear are summarized as shown in the following table. Become.

The rotational speed and tangential force of each element of each planetary gear set at each gear stage are summarized as shown in FIG. 28.

Next, a fifteenth embodiment of the device of the present invention will be explained with reference to FIG. 29. In this embodiment, similar to the second embodiment, in the first embodiment, the third planetary gear set 50 and the output shaft 22 are connected to each other. A single pinion type fourth planetary gear set 80 is interposed between them, and the connection relationship with each element is as follows.

The fourth sun gear 81 is drivingly connected to the third ring gear 53.

A fourth brake 74 is provided between the fourth ring gear 83 and the case 100, and is configured to clamp the fourth ring gear 83 when the brake is activated.

The fourth carrier 84 is drivingly connected to the second ring gear 43 and the third carrier 54, and is also dynamically connected integrally to the output shaft 22.

Here, specific numerical values of each gear stage of the transmission according to the present invention are exemplified as follows: 11=0.320, l2=0.60
0.

l3=0.520, l4=0.280, and each clutch 61, 62 at each gear stage of the transmission of the present invention
The operation of each brake 71, 72, 73, 74 and the reduction ratio of each gear stage are summarized in the following table.

The rotational speed and tangential force of each element of each planetary gear set at each gear stage are summarized as shown in FIG. 30.

As is clear from the above explanation, according to the present invention, there are basically three
By using a silk planetary gear set, the initial purpose can be achieved and at least four forward speeds and one reverse speed can be obtained which are excellent in practical use, and in addition, by simply changing the radius ratio of the first planetary gear set. In the first gear, the reduction ratio for reverse movement can be changed, and the reduction ratio can also be set relatively large, which increases the degree of freedom in design and makes it easy to respond to required specifications, making it suitable for industrial use. It has a great effect.

[Brief explanation of drawings]

FIG. 1 is a schematic central longitudinal cross-sectional view diagrammatically showing the first embodiment of the transmission device of the present invention, and FIG. 2 is the rotational speed and tangential force of each element of the planetary gear set in the first embodiment of the device of the present invention. FIG. 3 is a schematic central longitudinal cross-sectional view diagrammatically showing the second embodiment of the transmission device of the present invention, and FIG. 4 is a diagram showing the planetary gear set in the second embodiment of the device of the present invention. An explanatory diagram showing the relationship between the rotational speed of each element and the tangential force, FIG. 5 is a schematic central longitudinal cross-sectional view diagrammatically showing the third embodiment of the transmission device of the present invention, and FIG. 6 is a diagrammatic view of the transmission device of the present invention. An explanatory diagram showing the relationship between the rotational speed and tangential force of each element of the planetary gear set in the third embodiment, FIG. 7 is a central vertical cross-sectional schematic diagram diagrammatically showing the fourth embodiment of the transmission of the present invention, FIG. 8 is an explanatory diagram showing the relationship between the rotation speed and tangential force of each element of the planetary gear set in the fourth embodiment of the device of the present invention, and FIG. 9 is a diagrammatic representation of the fifth embodiment of the transmission device of the present invention. FIG. 10 is an explanatory view showing the relationship between the rotational speed and tangential force of each element of the planetary gear set in the fifth embodiment of the device of the present invention, and FIG. 11 is a schematic view of the transmission of the present invention. FIG. 12 is an explanatory diagram showing the relationship between the rotation speed and tangential force of each element of the planetary gear set in the sixth embodiment of the device of the present invention; FIG. FIG. 14 is a schematic central longitudinal cross-sectional view diagrammatically showing a seventh embodiment of the transmission device of the present invention, and FIG. An explanatory diagram showing the relationship, FIG. 15 is a schematic central vertical cross-sectional view diagrammatically showing an eighth embodiment of the transmission device of the present invention, and FIG. 16 is a diagram showing each element of a planetary gear set in the eighth embodiment of the device of the present invention. FIG. 17 is a schematic central longitudinal cross-sectional view diagrammatically showing the ninth embodiment of the transmission device of the present invention, and FIG. 18 is a diagram showing the ninth embodiment of the transmission device of the present invention. FIG. 19 is an explanatory diagram showing the relationship between the rotational speed of each element of the planetary gear set and the tangential force in the embodiment, and FIG.
FIG. 20 is an explanatory diagram showing the relationship between the rotational speed and tangential force of each element of the planetary gear set in the tenth embodiment of the device of the present invention;
Fig. 1 is a schematic central longitudinal cross-sectional view diagrammatically showing an eleventh embodiment of the transmission device of the present invention, and Fig. 22 shows the rotational speed and tangential force of each element of the planetary gear set in the eleventh embodiment of the device of the present invention. FIG. 23 is a schematic central longitudinal cross-sectional view diagrammatically showing the twelfth embodiment of the transmission of the present invention, and FIG. An explanatory diagram showing the relationship between the rotational speed of an element and a tangential force, FIG. 25 is a schematic central longitudinal cross-sectional view diagrammatically showing a thirteenth embodiment of the transmission of the present invention, and FIG. FIG. 27 is an explanatory diagram showing the relationship between the rotational speed and tangential force of each element of the planetary gear set in the thirteenth embodiment; FIG. Fig. 28 is an explanatory diagram showing the relationship between the rotational speed and tangential force of each element of the planetary gear set in the 14th embodiment of the device of the present invention, and Fig. 29 is the 15th embodiment of the transmission of the present invention.
FIG. 30 is a central vertical cross-sectional schematic view diagrammatically showing the embodiment, and is an explanatory diagram showing the relationship between the rotation speed and tangential force of each element of the planetary gear set in the 15th embodiment of the device of the present invention. 21...Input shaft, 22...Output shaft, 3
1...First sun gear, 32...First planetary gear, 33...First ring gear, 34
...First carrier, 41...Second sun gear, 42...Second planetary gear, 43...
...Second ring gear, 44...Second carrier, 51...Third sun gear, 52...
Third planetary gear, 53...Third ring gear, 54...Third carrier, 61...First clutch, 62...Second clutch, 71...・
...First brake, 72...Second brake, γ3...Third brake, 81...Fourth sun gear, 82...Fourth Planetary gear, 8
3...4th ring gear, 84...4th
Carrier.

Claims (1)

[Claims] 1. Several planetary gear sets each consisting of a human power shaft, an output shaft, 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 sun gears of the first to third planetary gear sets are drivingly connected, the carriers of the first and second planetary gear sets are drivingly connected, and the ring gear of the second planetary gear set and the carrier of the third planetary gear set are connected in a driving manner. A first clutch is connected to the output shaft in a driving manner to connect or release the ring gear of the third planetary gear set with respect to the input shaft, and a first clutch connects or releases each sun gear of the first to third planetary gear sets with respect to the input shaft. 2nd clutch to be released, 1st to 3rd
A first brake capable of securing each sun gear of the planetary gear set to the case, a second brake capable of securing both carriers of the first and second planetary gear sets to the case, and a ring gear of the first planetary gear set secured to the case. A transmission device comprising a third brake. 2. A human power shaft, an output shaft, each of which has several sets of planetary gears from 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; The sun gears of the third planetary gear set are drivingly connected, the carriers of the first and second planetary gear sets are drivingly connected, and the ring gear of the second planetary gear set and the carrier of the third planetary gear set are output. a first clutch which is drivingly connected to the shaft and connects or releases a ring gear of a third planetary gear set with respect to the input shaft; and a first to third planetary gear set; or a second clutch for releasing, a first brake capable of securing each sun gear of the first to third planetary gear sets to the case, and a second brake capable of securing both carriers of the first and second planetary gear sets to the case. , and a third brake capable of fixing the ring gear of the first planetary gear set to the case, and one or more of the sun gear, ring gear, and carrier of the fourth planetary gear set is tilted or one of the first planetary gear sets is connected to the first planetary gear set. a fourth brake, the other of which is drivingly connected to the ring gear of the fourth planetary gear set, and the other of which is drivingly connected to the output shaft, and which is capable of securing the remaining members of the sun gear, ring gear, and carrier of the fourth planetary gear set to the case. Transmission device. 3 A human power shaft, an output shaft, several sets of planetary gears each consisting of a sun gear, a ring gear, and a carrier that pivotally supports a planetary gear that connects the two gears, and a case that is a fixed member; The sun gears of the third planetary gear set are drivingly connected, and both the carriers of the first and second planetary gear sets are drivingly connected, and the ring gear of the second planetary gear set and the third carrier are drivingly connected.
a first clutch, which is drivingly connected to the carrier of the planetary gear set to the output shaft and connects or releases the ring gear of the third planetary gear set with respect to the input shaft;
A second clutch that connects or releases each sun gear of the first to third planetary gear sets with respect to the input shaft, a first brake that can secure each sun gear of the first to third planetary gear sets to the case, and first and second planetary gear sets. A second brake capable of securing both carriers of the planetary gear set to the case, and a third brake capable of securing the ring gear of the first planetary gear set to the case. any two of them are drivingly connected to both the carriers of the first and second planetary gear sets, and the other is drivingly connected to the output shaft, and the sun gear of the fourth planetary gear set; A transmission device comprising a fourth brake capable of fixing the ring gear and the remaining members of the carrier to the case. 4. A human power shaft, an output shaft, each of which has several sets of planetary gear sets consisting of a sun gear, a ring gear, and a carrier that pivots a planetary gear that forms a meshing interlock between the two gears, a case that is a fixed member, and a case that is a fixed member. The sun gears of the first to third planetary gear sets are drivingly connected, the carriers of the first and second planetary gear sets are drivingly connected, and the ring gear of the second planetary gear set and the third planetary gear set are connected in a driving manner. A carrier is drivingly connected to the output shaft, and the first clutch connects or releases the ring gear of the third planetary gear set with respect to the input shaft, and each sun gear of the first to third planetary gear sets is connected to the input shaft. A second clutch that connects or releases the first brake, which can lock each sun gear of the first to third planetary gear sets to the case, and which can lock both carriers of the first and second planetary gear sets to the case. A second brake and a third brake capable of fixing the ring gear of the first planetary gear set to the case are provided, and the ring gear of the fourth planetary gear set is drivingly connected to the ring gear of the third planetary gear set, and the fourth A transmission comprising a fourth brake in which a carrier of a planetary gear set is drivingly connected to the output shaft, and a sun gear of a fourth planetary gear set can be fixed to the case. 5 several sets of planetary gear sets, each consisting of a human power shaft, an output shaft, and a carrier force that supports a sun gear, a ring gear, and a planetary gear that continues the meshing interlock between the two gears;
It has a case which is a fixed member, the sun gears of the first to third planetary gear sets are connected in a driving manner, both the carriers of the first and second planetary gear sets are connected in a driving manner, and the carriers of the second planetary gear set are connected in a driving manner. The ring gear and the carrier of the third planetary gear set are drivingly connected to the output shaft, and each of the first clutch and the first to third planetary gear sets connects or releases the ring gear of the third planetary gear set with respect to the input shaft. A second clutch that connects or releases the sun gear from the input shaft, a first brake that can secure each of the sun gears of the first to third planetary gear sets to the case, and a first brake that can secure both carriers of the first and second planetary gear sets to the case. A second brake that can
and a third brake capable of fixing the ring gear of the first planetary gear set to the case, the sun gear of the fourth planetary gear set is drivingly connected to the ring gear of the third planetary gear set, and the carrier of the fourth planetary gear is connected to the ring gear of the third planetary gear set. A transmission comprising a fourth brake drivingly connected to the output shaft and capable of fixing a ring gear of a fourth planetary gear set to the case.