JPS5845610B2 - 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 vehicles, particularly automobiles.

It is desirable that a transmission for a passenger car 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 type or double-pinion type 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 stage speed.

(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 minimum diameter, 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 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.

Taking these conditions into account, the present invention basically uses three sets of single pinion simple planetary gear sets, basically uses three sets as clutch devices, and basically uses two sets as brake devices. It is an object of the present invention to provide a transmission having at least four forward gears and one reverse gear by appropriately coupling movable members of a planetary gear set and appropriately disengaging clutch devices and brake devices.

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

A first embodiment of the device of the present invention will be described with reference to FIG. 1. A single pinion type first planetary gear set X1. There are a second planetary gear set X2 and a third planetary gear set I3.

The first planetary gear set X1 includes a first sun gear S
1, a first planetary gear P1 that meshes with the first sun gear, and a first ring gear RG that meshes with the first planetary gear P1.
1 and a first carrier C1 that pivotally supports the first planetary gear P1.

Further, the second planetary gear set X2 includes a second sun gear P2 that meshes with the second sun gear S2.
and a second ring gear RG2 that meshes with the second planetary gear.
and a second carrier C2 that pivotally supports the second planetary gear P2.

Similarly, the third planetary gear set X3 includes a third sun gear S3 and a third planetary gear P that meshes with the third sun gear.
3 and a third ring gear RG that meshes with the third planetary gear.
3 and a third carrier C3 that pivotally supports the third granary gear P3.

The first sun gear S1 and the third sun gear S3 are drivingly connected.

The first carrier C1 and the second ring gear RG2 are drivingly connected.

The first ring gear RG1, the second sun gear S2, and the third carrier C3 are drivingly connected to each other, and both are drivingly connected integrally to the output shaft.

The input shaft and the first sun gear S1. The input shaft and the first sun gear S1. The first gear that integrally connects and disconnects from the third sun gear S3.
A clutch CL1 is provided.

A second clutch CL2 is provided between the input shaft, the first carrier CI, and the second ring gear RG2 to integrally connect or disconnect the input shaft, the first carrier CI, and the second ring gear RG2. is installed.

A third clutch CL3 is disposed between the input shaft and the second carrier C2 to integrally connect or disconnect the input shaft and the second carrier C2.

A first brake B1 is provided between the second carrier C2 and the case, and when the brake is operated, the second brake
It is designed so that the carrier C2 can be secured.

A second ring gear is provided between the third ring gear RG3 and the case.
A brake B2 is provided so that the third ring gear RG3 can be fixed when the brake is activated.

Then, in each planetary gear cell) Xl, I2°I3, the following formula (the same applies to all embodiments to be described later).

) holds true. However, NRGl, NBG2, NRG3: Number of rotations of the first, second, third ring gear, NC1, NC2, NC3: Number of rotations of the first, second, third carrier, NS1, NS2, NS3: Number of rotations of the first, third ring gear. 2. Number of rotations of the third sun gear, ■□, I2, ■3; Radius ratio of each ring gear and each sun gear.

Here, to illustrate the specific numerical values of each gear stage of the transmission according to the present invention, 11=0.548, ■2-O,548
, 13=0.500 (the same applies to all embodiments described below), and each clutch CLI, CL2°CL3 and each brake B1 . B2
The relationship between the operation and the reduction ratio of each gear stage is summarized as shown in Table 1A.

However, Fn (n=1.2.3... 1.2・・・・・・・・・
) indicates the reverse gear, and R1 is the first reverse gear.

Table 1B summarizes the rotational speed and tangential force of each element of each planetary gear set at each gear stage.

However, the value is expressed as a ratio with the input shaft as 1. However, the tangential force is expressed as a ratio with the input shaft torque acting on the ring gear as 1, and the tangential force of the planetary gear is the ratio of the sun gear and It is equivalent to a ring gear.

Note that the same symbols as in the above-mentioned Fig. 1B refer to the same objects, and furthermore, A indicates the gear stage, B indicates the planetary gear set, N indicates the rotation speed, and W indicates the connecting force. .

Furthermore, F4. (4th forward speed) has a reduction ratio of 1:1. OO
Therefore, 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 the tangential force generated at other gears. In other words, in other gears, when only one of the clutches is engaged, the input shaft can only be operated via the engaged clutch. While torque is transmitted to each element, in F4 (fourth gear), at least two clutches are engaged, so that the input shaft torque is shared between both clutches. Since the input shaft torque is transmitted to each element, the resulting tangential force on each element is smaller than when the input shaft torque is not shared and transmitted as is due to the engagement of only one clutch. It is self-explanatory, and hereinafter the rotational speeds N and W of each element in a gear stage where the reduction ratio is 1:1.00 will be omitted.

Next, a second embodiment of the device of the present invention will be explained with reference to FIG. 2. In the embodiment shown in FIG. The structure is formed by interposing a netari gear set (X4), and the connection relationship with each element is as follows.

The fourth gear set (X4) is the fourth sun gear S
4 and a fourth planetary gear RG4 that meshes with the fourth sun gear.
and a fourth carrier C4 that pivotally supports the fourth planetary gear.
and has.

The fourth ring gear RG4 is the third ring gear RG3.
When the second flake B2 operates, the fourth ring gear R
G4 is fixed.

A third brake B3 is provided between the fourth carrier C4 and the case, and when the third brake B3 is operated, the fourth
It is designed so that the carrier C4 can be secured.

The fourth sun gear S4 is drivingly connected to the third carrier C3 and is integrally and dynamically connected to the output shaft.

Then, the following equation holds true in the fourth planetary gear set X4.

However, 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 I4 is the radius ratio of the 41st ring gear and the fourth sun gear.

Here, to give an example of specific numerical values for each gear stage of the transmission device according to the present invention, 14=0.562, and each clutch CLI, CL2 at each gear stage of the transmission device according to the present invention
, CL3 and each brake B1°B2. The relationship between the operation of B3 and the reduction ratio of each gear stage is summarized as shown in Table 2A.

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

Next, a third embodiment of the device of the present invention will be explained with reference to FIG. 3. This embodiment is similar to the second embodiment shown in FIG. It has a configuration in which a single pinion type fourth planetary gear set X4 is interposed between the planetary gear set X3 and the output shaft, and the connection relationship with each element is as follows.

The fourth sun gear S4 is drivingly connected to the third ring gear RG3, and when the second brake B2 is operated,
Similarly to the third ring gear RG3, the fourth sun gear S4 is fixed.

A third brake B3 is provided between the fourth carrier C4 and the case, and is configured to clamp the fourth carrier C4 when the brake is activated.

The fourth ring gear RG4 is drivingly connected to the third carrier C3 and is integrally and dynamically connected to the output shaft.

Here, to give an example of the specific numerical value of each gear stage of the transmission device according to the present invention, it is 14=0.437, and the operation of each clutch and each brake at each gear stage of the transmission device of the present invention and each gear shift. The relationship between the speed reduction ratios of the stages is summarized as shown in Table 3A.

The rotational speed and tangential force of each element of each planetary gear set at each gear stage are summarized as shown in Table 3B.

Next, a fourth embodiment of the device of the present invention will be explained with reference to FIG. 4. Similar to the second embodiment, this embodiment differs from the third planetary gear set Single pinion type 4th planetary gear X4 between
The connection relationship with each element is as follows.

The fourth carrier C4 is drivingly connected to the third ring gear RG3, and when the second brake B2 is operated,
Similarly to the third ring gear RG3, the fourth carrier C4 is fixed.

A third brake B3 is provided between the fourth sun gear S4 and the case, and is configured to lock the fourth sun gear S4 when the brake is activated.

The fourth ring gear RG4 is drivingly connected to the third carrier C3, and is also dynamically connected integrally to the output shaft.

Here, to give an example of a specific gear position value of the transmission according to the present invention, 14=0.562, and the operation of each clutch and each brake at each gear position of the transmission according to the present invention, The relationship between the speed reduction ratios is summarized in Table 4A.

Table 4B summarizes the rotational speed and tangential force of each element of each planetary gear set at each gear stage.

Next, a fifth embodiment of the device of the present invention will be explained with reference to FIG. 5. Similar to the second embodiment, this embodiment differs from the third planetary gear set A single pinion type fourth planetary gear set

The fourth carrier C4 is drivingly connected to the third ring gear RG3, and when the second brake B2 is operated,
Similarly to the third ring gear RG3, the fourth carrier C4 is fixed.

A third ring gear is provided between the fourth ring gear RG4 and the case.
A brake B3 is provided so that when the brake is activated, the fourth ring gear RG4 can be secured.

The fourth sun gear S4 is drivingly connected to the third carrier C3, and is also dynamically connected integrally with the output shaft.

Here, to give an example of a specific gear position value of the transmission according to the present invention, it is 14=0.562, and each clutch and each brake operation at each gear position of the transmission according to the present invention and each gear position are The relationship between the reduction ratios is summarized as shown in Table 5A.

Table 5B summarizes the rotational speed and connection force of each element of each planetary gear set at each gear stage.

Next, a sixth embodiment of the device of the present invention will be explained with reference to FIG. 6. Similar to the second embodiment, this embodiment differs from the third planetary gear set (X3) and the output shaft in the first embodiment. A single pinion type fourth planetary gear set

The fourth sun gear S4 is drivingly connected to the third ring gear RG3, and when the second brake B2 is operated,
Similarly to the third ring gear RG3, the fourth sun gear S4 is fixed.

A third ring gear is provided between the fourth ring gear RG4 and the case.
A flake B3 is provided so that the fourth ring gear RG4 can be secured when the brake is activated.

The fourth carrier C4 is drivingly connected to the third carrier C3, and is also dynamically connected integrally with the output shaft.

Here, to give an example of the numerical value of a specific gear stage of the transmission device according to the present invention, I, = 0.437, and the operation of each clutch and each brake at each gear stage of the transmission device of the present invention and each gear shift. The relationship between the speed reduction ratios of the stages is summarized as shown in Table 6A.

Table 6B summarizes the rotational speed and tangential force of each element of each planetary gear set at each gear stage.

Next, a seventh embodiment of the device of the present invention will be described with reference to FIG. 7. Similar to the second embodiment, in the first embodiment, the third planetary gear set X3 and the output shaft A single pinion type fourth planetary gear set X4 is interposed between the two, and the connection relationship with each element is as follows.

The fourth ring gear RG4 is the third ring gear RG3.
When the second brake B2 is actuated, the fourth ring gear R
G4 is fixed.

A third brake B3 is provided between the fourth sun gear S4 and the case, and is configured to lock the fourth sun gear S4 when the brake is activated.

The fourth carrier C4 is drivingly connected to the third carrier C3, and is also dynamically connected integrally with the output shaft.

Here, to give an example of a specific numerical value of each gear stage of the transmission device according to the present invention, 14=0.320, and the operation of each clutch and each brake at each gear stage of the transmission device of the present invention and each gear shift. The relationship between the speed reduction ratios of the stages is summarized as shown in Table 7A.

Table 7B summarizes the rotational speed and tangential force of each element of each planetary gear set at each gear stage.

Next, an eighth embodiment of the device of the present invention will be described with reference to FIG. 8. Similar to the second embodiment, this embodiment has the third planetary gear set X3 and the output shaft in the first embodiment. between the single pinion type fourth planetary gear
4, and the connection relationship with each element is as follows.

The fourth ring gear RG4 is drivingly connected to the third sun gear S3.

A third brake B3 is provided between the fourth sun gear S4 and the case, and when the brake is operated, the fourth
Sun gear S4 can be secured.

The fourth carrier C4 is drivingly connected to the third carrier C3 and is integrally and dynamically connected to the output shaft.

Here, to give an example of a specific gear position value of the transmission according to the present invention, 14=0.375. Table 8A summarizes the relationship between the reduction ratios.

Table 8B summarizes the rotational speed and tangential force of each element of each planetary gear set at each gear stage.

Next, a ninth embodiment of the device of the present invention will be explained with reference to FIG. 9. Similar to the second embodiment, this embodiment differs from the third planetary gear set (X3) and the output shaft in the first embodiment. A single pinion type fourth planetary gear set (X4) is interposed between the two, and the connection relationship with each element is as follows.

The fourth sun gear S4 is drivingly connected to the third sun gear S3.

A third ring gear is provided between the fourth ring gear RG4 and the case.
A flake B3 is provided so that the fourth ring gear RG4 can be secured when the brake is activated.

The fourth carrier C4 is drivingly connected to the third carrier C3, and is also dynamically connected integrally with the output shaft.

Here, specific numerical values of the gears of the transmission device according to the present invention are exemplified as follows.

=0.280, and the relationship between the operation of each clutch and each brake at each gear stage of the transmission of the present invention and the reduction ratio of each gear stage is summarized as shown in Table 9A.

Table 9B summarizes the rotational speed and tangential force of each element of each planetary gear set at each gear stage.

As is clear from the above description, according to the present invention, the initial objective can be basically achieved using three planetary gear sets, and a practically excellent gear stage of at least 4 forward speeds and 1 reverse speed can be obtained. It has great industrial effects.

[Brief explanation of the drawing]

FIG. 1 is a schematic central longitudinal cross-sectional view diagrammatically showing a first embodiment of the transmission of the present invention, and FIG. 2 is a schematic central longitudinal cross-sectional diagram diagrammatically showing a second embodiment of the transmission of the present invention. FIG. 3 is a central vertical cross-sectional schematic diagram diagrammatically showing a third embodiment of the transmission of the present invention, and FIG. 4 is a central longitudinal cross-sectional diagram diagrammatically showing a fourth embodiment of the transmission of the present invention. FIG. 5 is a diagrammatic view of a central vertical section showing a fifth embodiment of the transmission of the present invention; FIG. 6 is a diagrammatic view of a sixth embodiment of the transmission of the present invention. FIG. 7 is a diagrammatic diagram of a central vertical section showing a seventh embodiment of the transmission of the present invention; FIG. 8 is a diagrammatic diagram of an eighth embodiment of the transmission of the present invention. FIG. 9 is a schematic central longitudinal cross-sectional view diagrammatically showing a ninth embodiment of the transmission of the present invention. Xl...1st planetary gear set, X2...
...Second planetary gear set, X3...
3rd planetary gear set, X4...4th planetary gear set, Sl...1st sun gear, B
2...Second sun gear, B3...Third sun gear, B4...Fourth sun gear, Pl...
...First planetary gear, P2...Second planetary gear, P3...Third planetary gear, P4
...4th planetary gear, RGI...
1st ring gear, RG2... 2nd ring gear,
RG3...Third ring gear, RG4...
・4th ring gear, C1...1st carrier, C
2...Second carrier, C3...Third carrier, C4...Fourth carrier, CLl...
...First clutch, Cu2...Second clutch, Cu3...Third clutch, B1...
1st brake, B2... 2nd brake, B3.
...Third brake.

Claims (1)

[Claims] 1. A human power shaft, an output shaft, several planetary gear sets each consisting of a sun gear, a ring gear, and a carrier that pivotally supports a planetary gear that carries out meshing motion between the two gears, and a case that is a fixed member. However, the carrier of the first planetary gear set and the ring gear of the second planetary gear set are drivingly connected, both the sun gears of the first and third planetary gear sets are drivingly connected, and the ring gear of the first planetary gear set and the second planetary gear The sun gear of the third planetary gear set and the carrier of the third planetary gear set are drivingly connected to the output shaft, and a first A clutch, which connects or releases the carrier of the first planetary gear set and the ring gear of the second planetary gear set to the input shaft.A second clutch, which connects or releases the carrier of the second planetary gear set to the input shaft. A first brake capable of securing the carrier of the second planetary gear set to the case; and a second brake capable of securing the ring gear of the third planetary gear set to the case. 2. In the first invention described in the claims, one of the sun gear, ring gear, and carrier of the fourth planetary gear set is drivingly connected to the output shaft, and the other is connected to the output shaft. The sun gear of the fourth planetary gear set is drivingly connected to one of the two sun gears of the first and third planetary gear sets connected together, and the ring gear of the third planetary gear set; A transmission comprising a ring gear and a third brake capable of fixing the remaining members in the carrier to the case.