JPS5845611B2 - 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 can be considered, it is desirable that the following conditions be satisfied.

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

(2) Each element of 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 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 a movable member of a planetary gear set and appropriately 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. 1. Between the input shaft and the output shaft, there are a single pinion type first planetary gear set X1, second planetary gear set X2, and third planetary gear set X3. do.

The first planetary gear set (Xl) is the 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 (also the second planetary gear set) X2
is a second sun gear S2, a second planetary gear P2 meshing with the second sun gear, and a second planetary gear P2 meshing with the second planetary gear S2.
It has a second carrier C2 that pivotally supports the ring gear RG2 and 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 planetary gear P3.

The first sun gear S1 and the third ring gear RG3 are drivingly connected.

The first carrier C1 and the second carrier C2 are drivingly connected.

The second sun gear S2 and the third sun gear S3 are drivingly connected.

The second ring gear RG2 and the third carrier C3 are drivingly connected, and both are dynamically connected integrally to the output shaft.

Between the input shaft and the second sun gear S2 and the third sun gear S3, there is a first screw for integrally connecting and disconnecting the input shaft and the second sun gear S2 and third sun gear S3.
A clutch CL1 is provided.

Between the input shaft and the first carrier C1 and the second carrier C2, there is a second shaft for integrally connecting or disconnecting the input shaft and the first carrier C1 and the second carrier C2.
A clutch CL2 is provided.

A third clutch CL3 is disposed between the input shaft and the first ring gear RGI to integrally connect or disconnect the input shaft and the first ring gear RGI.

A first brake B1 is provided between the first and second carriers CI and C2 and the case, so that when the brake is actuated, the first and second carriers C1 and C2 can be fixed.

The first sun gear S1. A second brake B2 is provided between the third ring gear RG3 and the case, so that when the brake is activated, the first sun gear S1 and the third ring gear RG3 can be fixed.

and each planetary gear cella) xl. x2. x3 is expressed by the following formula (the same applies to all embodiments described below).

) holds true. However, NRG, , NRG2, NRG3; rotational speeds of the first, second and third ring gears NC1, NC2, NC3; rotational speeds of the first, second and third carriers NS1, NS2, NS3; first, second , rotation speed of third sun gear 11, I2, ■3: Radius ratio of each ring gear and each sun gear.

Here, to give an example of specific numerical values of each gear stage of the transmission according to the present invention, I,=0.320112-0.320,
I3. = 0.500 (the same applies to all the embodiments described below), and each clutch CL1, CL2, CL3 and each brake B at each gear stage of the transmission of the present invention
1. The relationship between the operation of B2 and the reduction ratio of each gear stage is summarized as shown in Table 1A.

However, Fn (n=1.2.3...) indicates the forward gear stage; for example, Fl is the first forward gear, F2 is the second forward gear, and Rn (n=1.2. ...) indicates a reverse gear, and R1 is the first reverse gear.

The rotational speed and tangential force of each element of each planetary gear set at each gear stage are summarized as shown in Table 1B.

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 Table 1B above refer to the same objects, and further, A indicates the gear stage, B indicates the planetary gear set, N indicates the rotation speed, and W indicates the tangential force. .

Note that F4 (fourth forward speed) has a reduction ratio of 1:1. OO, the number of rotations N of each sun gear, ring gear, and carrier is 100, and the number of rotations N of each planetary gear is 0.
．． 00, and the tangential force W is much smaller than the tangential force generated in other gears, that is, in other gears, only one of the clutches is activated. When F4 is engaged, the torque of the input shaft is transmitted to each element only through the engaged clutch.
In (4th speed), the torque of the input shaft is shared by both clutches by engaging at least two clutches, and the shared torque of the input shaft 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 by engagement of only one clutch. The rotational speeds N and W of each element in the gear position OO are omitted.

Next, a second embodiment of the device of the present invention will be explained with reference to FIG. 2. In the embodiment of FIG. 1, a single pinion type fourth planetary gear set is provided between the third planetary gear set X3 and the output shaft. The structure is formed by interposing X4, and the connection relationship with each element is as follows.

The fourth planetary gear set) X4 is the fourth sun gear S
4, a fourth planetary gear P4 that meshes with the fourth sun gear, a fourth ring gear RG4 that meshes with the fourth planetary gear, and a fourth carrier C4 that pivotally supports the fourth planetary gear.

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 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.

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

However, NRG is the rotational speed NC4 of the fourth ring gear; the rotational speed NS4 of the fourth carrier; the rotational speed I4 of the fourth sun gear; and the radius ratio of the fourth ring gear and the fourth sun gear.

Here, specific numerical values of each gear stage of the transmission according to the present invention are exemplified as follows.

= 0.562, and the relationship between the operation of each clutch CL1, CL2, CL3 and each brake B1, B2, B3 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 2A. It becomes like this.

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.
This embodiment is similar to the second embodiment shown in FIG. 2, and is similar to the second embodiment shown in FIG.
3 and the output shaft, a single pinion type fourth planetary gear set X4 is interposed, 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 of the transmission according to the present invention, 14=0.562, and the operation of each clutch and each brake at each gear of the transmission of the present invention and each gear The relationship between the reduction ratios 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 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 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, it is 14=0.562, and the operation of each clutch and each brake in each gear position of the transmission apparatus of the present invention and the operation of each gear position The relationship between the reduction ratios is summarized as shown 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.
Similar to the second embodiment, this embodiment has a configuration in which a single pinion type fourth planetary gear set X4 is interposed between the third planetary gear set X3 and the output shaft in the first embodiment. , 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 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, 14=0.562 is an example of a specific numerical value of the gear position of the transmission according to the present invention, and each clutch and each brake actuate at each gear position of the transmission apparatus of the present invention and deceleration at each gear position. The relationship between the ratios is summarized as shown in Table 5A.

Table 5B summarizes the rotational speed and tangential 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.
Similar to the second embodiment, this embodiment has a configuration in which a single-pinion fourth planetary gear set (X4) is interposed between the third planetary gear set (X3) and the output shaft in the first embodiment. 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 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 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 gear position value of the transmission according to the present invention, it is 14=0.437, and the operation of each clutch and each brake in each gear position of the transmission according to the present invention and the operation of each gear position The relationship between the reduction ratios 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 explained with reference to FIG.
Similar to the second embodiment, the present invention has a configuration in which a single pinion type fourth planetary gear set X4 is interposed between the third planetary gear set X3 and the output shaft in the first embodiment. 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 according to the present invention, 14=0.320, and the operation of each clutch and each brake at each gear stage of the transmission of the present invention and each gear stage. The relationship between the speed reduction ratios 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 explained 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. 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 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, it is 14=0.375, and the operation of each clutch and each brake in each gear of the transmission according to the present invention and the operation of each gear The relationship between the reduction ratios is summarized as shown in Table 8A.

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

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 coupled to the third sun gear S3 in a one-drive manner.

A third ring gear is provided between the fourth ring gear RG4 and the case.
A brake B3 is provided, and when the brake is activated, it can lock the fourth ring gear RG4.

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

Here, to give an example of the specific gear position values of the transmission according to the present invention, 14 = 0.280 and the operation of each clutch and each brake at each gear position of the transmission according to the present invention and the deceleration of each gear position tomorrow. The relationship between the ratios 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 vertical cross-sectional view diagrammatically showing a first embodiment of the transmission device of the present invention. FIG. 2 is a schematic central vertical cross-sectional view diagrammatically showing a second embodiment of the transmission of the present invention. FIG. 3 is a schematic central vertical cross-sectional view diagrammatically showing a third embodiment of the transmission of the present invention. FIG. 4 is a schematic central vertical cross-sectional view diagrammatically showing a fourth embodiment of the transmission of the present invention. FIG. 5 is a schematic central vertical cross-sectional view diagrammatically showing a fifth embodiment of the transmission of the present invention. FIG. 6 is a diagrammatic central vertical cross-sectional schematic view of a sixth embodiment of the transmission of the present invention. FIG. 7 is a schematic central vertical cross-sectional view diagrammatically showing a seventh embodiment of the transmission of the present invention. FIG. 8 is a schematic central vertical cross-sectional view diagrammatically showing an eighth embodiment of the transmission of the present invention. FIG. 9 is a schematic central vertical 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 set, B3...
3rd sun gear, B4... 4th sun gear, Pl.
...First planetary gear, P2...Second
Planetary gear, P3...Third planetary gear, P4...Fourth planetary gear, RGI... ...First ring gear, RG2...Second ring gear, RG3...Third ring gear, RG4...
...4th ring gear, C1...1st carrier, C2...2nd carrier, C3...
3rd carrier, C4...4th carrier, CLl
...First clutch, CL2...Second clutch, CL3...Third clutch, B1...
...First flake, B2...Second brake,
B3...Third brake.

Claims (1)

[Scope of Claims] 1 A human power shaft, an output shaft, several sets of planetary gears each consisting of 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. However, both the carriers of the first and second planetary gear sets are drivingly connected, the sun gear of the first planetary gear set and the ring gear of the third planetary gear set are drivingly connected, and both the sun gears of the second and third planetary gear sets are drivingly connected. are drivingly connected, the ring gear of the second planetary gear set and the carrier of the third planetary gear set are drivingly connected to the output shaft, and both the sun gears of the second and third planetary gear sets are connected. A first clutch that connects or releases the carriers of the first and second planetary gear sets to the input shaft, a second clutch that connects or releases the carriers of the first and second planetary gear sets, and a ring gear of the first planetary gear set that connects or releases the ring gear of the first planetary gear set to the input shaft. a third clutch capable of engaging or disengaging the carriers of the first and second planetary gear sets; a first brake capable of securing the carriers of the first and second planetary gear sets connected to the case;
A transmission comprising a second brake capable of fixing a planetary gear set connected to a ring gear to a 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. Either the sun gear of the first planetary gear set and the ring gear of the third planetary gear set are connected, or the sun gear of both the second and third planetary gear sets are connected. A transmission comprising a third brake that is drivingly coupled and capable of securing the remaining members of the sun gear, ring gear, and carrier of the fourth planetary gear set to the case.