JPS5844903B2 - 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 thought to be able to realize four or more gears by combining single pinion or double pinion simple planetary gear sets with 3 or 4 gears or more, and linking each element appropriately. It will be done.

Although a large number of combinations of transmissions can be considered, it is desirable that each of the following conditions be satisfied.

■ The output shaft must be connected to the same element for each gear.

■ Each element of the planetary gear set must have a low rotational speed to reduce the circumferential speed of the bearing.

■ Due to problems with the strength of the teeth of each gear, the tooth load or tangential force of each element must be small.

■ The number of teeth on each gear in each planetary gear set must satisfy the requirements, and the minimum diameter sun gear and planetary gear must also have the required number of teeth.

■ The connection of each element of each planetary gear set can be easily achieved with the shortest possible length.

- When shifting gears while driving, 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.

Taking these conditions into consideration, the present invention basically uses one set of single pinion type simple planetary gear sets and two double pinion type simple planetary gear sets, basically two as a clutch device and two as a brake device. Basically, three planetary gear sets are used, and the movable members of each planetary gear set are appropriately coupled, and the clutch device and the brake device are appropriately disengaged to provide a transmission having at least four forward gears and one reverse gear. purpose.

Embodiments of the present invention will be described below with reference to the accompanying drawings. A first embodiment of the present invention apparatus will be explained with reference to FIG. There is a two planetary gear set X2 and a third planetary gear set X3.

The first planetary gear set I-XI meshes with a first sun gear S1, a first planetary gear P1 that meshes with the first sun gear S1, a second planetary gear P2 that meshes with the first planetary gear P1, and a second planetary gear P2 that meshes with the second planetary gear P2. 1st
IJ Nguya RGI and the first. Both second planetary gears P1. and a first carrier C1 that pivotally supports P2.

The second planetary gear set l-I2 includes a second sun gear S2, a third planetary gear P3 that meshes with the second sun gear S2, a second ring gear RG2 that meshes with the third planetary gear P3, and the third planetary gear P3. It has a second carrier C2 that pivotally supports P3.

Similarly, the third planetary gear set l-I3 includes a third sun gear S3, a fourth planetary gear P4 that meshes with the third sun gear S3, a third ring gear RG3 that meshes with the fourth planetary gear P4, and a fourth planetary gear P4. and a third carrier C3 that pivotally supports the.

The first sun gear S1 and the second and third sun gears 52j
S3 are drivingly connected to each other.

The first cow wheel C1 and the second cow wheel C2 are drivingly connected.

The second ring gear RG2 and the third carrier C3 are drivingly connected.

The third + gear C3, the second ring gear RG2, and the output shaft are dynamically connected together.

A first clutch CL1 is disposed between the input shaft and the third ring gear RG3 to integrally connect or disconnect the input shaft and the third ring gear RG3.

The input shaft and the 1.2.3 sun gear 81.82.8
3 and the input shaft and the first 2.3 sun gear 81.
, 82, 83 are provided.

A first brake B1 is provided between the 1.2j3 sun gear 81°82.83 and the case, and when the brake is activated, the 1.2.3rd sun gear 81.82.8
3 can be fixed.

Between the first IJ Nguya RGI and the case, there is a second
A brake B2 is provided so that when the brake is activated, the 11th J gear RGI can be fixed.

A third brake B3 is provided between the first carrier C1 and the second carrier C2 and the case, and can lock the first carrier C1 and the second carrier C2 when the brake is activated. It looks like this.

And each planetary gear set X1. For X2°I3, the following formula (the same applies to all embodiments to be described later).

) holds true. However, NRGI, NHO2, NHO2; rotational speed of the 11th second and third ring gears NCI, NC2, NC3; rotational speed of the 11th second and third carriers N5IjNS2. NS3: Number of rotations of the 11th second and third sun gears is 11, I2. I3: Ratio of radius between 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, 11=0.344. I20.320. I
320.484 (The same applies to all the examples described below.

), and each clutch CLI, CL2 and brake B1, B2 . B3
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...) 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, the tangential force is expressed as a ratio with 1 assuming that the input shaft torque acts on the ring gear, and the tangential force of the planetary gear is the ratio of the sun gear and ring gear. is equivalent to

Note that the same symbols as in Table 1A above 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 tangential force. be.

In addition, since the reduction ratio of F4 (fourth forward speed) is 1:1.00, the rotational speed N of each sun gear, ring gear, and carrier is 1.00. Furthermore, the rotational speed N of each planetary gear is 0.00, and the tangential force W thereof is significantly smaller than the tangential force generated at other gears. When only one of the clutches is engaged, the torque of the input shaft is transmitted to each element only through the engaged clutch.
In F4 (fourth forward speed), at least two clutches are engaged so that the input shaft torque is shared by both clutches, and the shared input shaft torque is transmitted to each element. , it is obvious that the resulting tangential force of each element is smaller than when the torque of the input shaft is not shared by the engagement of only one clutch and is transmitted as is. The rotational speed N and tangential force W of each element in the gear stage, which is 1.00, 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 a fourth sun gear S.
4, a fifth planetary gear P5 that meshes with the fourth sun gear, a fourth ring gear RG4 that meshes with the fifth planetary gear, and a fourth carrier G that pivotally supports the fifth planetary gear P5.
4.

The fourth ring gear RG4 is drivingly connected to the second carrier C2, and when the third brake B3 is operated,
Similarly to the second carrier C2, the fourth ring carrier RG4 is fixed.

A fourth brake B4 is provided between the fourth carrier C4 and the case, and when the brake is operated, the fourth brake B4
The carrier C4 can be secured.

The fourth sun gear S4 is dynamically and integrally connected to the output shaft.

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

shall be.

Here, to give an example of specific numerical values for each gear stage of the transmission according to the present invention, l4=0.562, and each clutch CL1. CL2 and each brake Bl, B2. Table 2A summarizes the relationship between the operations of B3 and B4 and each gear stage.

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. A single pinion type fourth motor is connected between the set X3 and the output shaft.
It has a configuration with a planetary gear set X4 interposed,
The connection relationship with each element is as follows.

The fourth ring gear RG4 is the eleventh ring gear RG.
1, and when the second brake B2 is activated, the fourth ring gear RG4 is fixed in the same way as the eleventh ring gear RG1.

A fourth brake B4 is provided between the fourth carrier C4 and the case, and is configured to lock the fourth carrier C4 when the brake is activated.

The fourth sun gear S4 is dynamically and integrally connected to the output shaft.

Here, to give an example of a specific gear position value of the transmission according to the present invention, l4 = 0.562, 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 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 X3 and the output shaft in the first embodiment. It has a configuration in which a single pinion type fourth plane gear set 1-X4 is interposed between them, and the connection relationship with each element is as follows.

The fourth sun gear S4 is drivingly connected to the second carrier C2, and when the third brake B3 is operated, the fourth sun gear S4 is locked in the same way as the second carrier C2.

A fourth brake B4 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 dynamically and integrally connected to the output shaft.

Here, to give an example of a specific gear position value of the transmission according to the present invention, l4=0.562, and the operation of each clutch and each brake at each gear position of the transmission apparatus of the present invention and each gear position. 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 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 connected to the eleventh ring gear RG1 in a driving manner, and when the second brake B1 is operated, the fourth sun gear S4 is connected to the eleventh ring gear RG1 in the same manner as the first ring gear RGI.
is fixed.

A fourth brake B4 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 dynamically and integrally connected to the output shaft.

Here, to give an example of a specific gear position value of the transmission device according to the present invention, l4 = 0.562, and each clutch and each brake operation at each gear position of the transmission apparatus of the present invention and each gear position. The relationship between the reduction 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. 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 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 second carrier C2, and when the third brake B3 is operated, the fourth carrier C4 is locked in the same way as the second thousandth carrier C2.

A fourth brake B4 is provided between the fourth sun gear S4 and the case, so that when the brake is activated, the fourth sun gear S4 can be fixed.

The fourth ring gear RG4 is dynamically and integrally connected to the output shaft.

Here, the specific numerical values of the gears of the transmission according to the present invention are 420.562, and the operation of each clutch and each brake in each gear of the transmission 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 explained with reference to FIG. 7. Similar to the second embodiment, this embodiment is similar to the second embodiment in that the third planetary gear set X3 and the output shaft are connected to each other 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 carrier C4 is drivingly connected to the eleventh ring gear RG1, and when the second brake B2 is operated, the fourth carrier C4 is connected to the eleventh ring gear RG'l.
is fixed.

A fourth brake B4 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 dynamically and integrally 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, l4 = 0.280, 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.

The rotational speed and tangential force of each element of each planetary gear set at each gear stage are summarized as shown in Table 7B.

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. It has a configuration in which a single pinion type fourth plane gear set X4 is interposed between them, and the connection relationship with each element is as follows.

The fourth carrier C4 is drivingly connected to the second carrier C2, and when the third brake B3 is operated, the fourth carrier C4 is locked in the same manner as the second carrier C2.

A fourth ring gear is provided between the fourth ring gear RG4 and the case.
A brake R4 is provided, and is configured to lock the fourth ring carrier RC4 when the brake is activated.

The fourth sun gear S4 is dynamically and integrally connected to the output shaft.

Here, to give an example of a specific gear position value of the transmission according to the present invention, l4=0.562, and the operation of each clutch and each brake at each gear position of the transmission apparatus of the present invention and each gear position. 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 is similar to the second embodiment in that the third planetary gear set X3 and the output shaft are connected to each other in the first embodiment. It has a configuration in which a single pinion type fourth plane gear set 1-X4 is interposed between them, and the connection relationship with each element is as follows.

The fourth carrier C4 is drivingly connected to the eleventh J gear RC1, and when the second brake B2 is operated, the fourth carrier C4 is connected to the eleventh J gear RGI.
4 is fixed.

A fourth ring gear is provided between the fourth ring gear RC4 and the case.
A brake B4 is provided, and when the brake is activated, it can lock the fourth ring gear RG4.

The fourth sun gear S4 is dynamically and integrally connected to the output shaft.

Here, to give an example of a specific gear position value of the transmission device according to the present invention, l4 = 0.562, and each clutch and each brake operation at each gear position of the transmission apparatus of the present invention and each gear position. The relationship between the gear 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.

Next, a first embodiment of the device of the present invention will be explained with reference to FIG. It has a configuration in which a single pinion type fourth planetary gear set t-X4 is interposed between the two elements, and the connection relationship with each element is as follows.

The fourth sun gear S4 is drivingly connected to the second carrier C2, and when the third brake B3 is operated, the fourth sun gear S4 is locked in the same manner as the second carrier C2.

A fourth brake B4 is provided between the fourth ring gear RG4 and the case, and when the brake is operated, the fourth brake B4
The ring gear R84 can be fixed.

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

Here, to give an example of a specific gear position value of the transmission device according to the present invention, l4 = 0.437, and each clutch and each brake operation at each gear position of the transmission apparatus according to the present invention and each gear position. The relationship between the reduction ratios is summarized as shown in Table 10A.

Table 10B summarizes the rotational speed and tangential force of each element of each planetary gear set at each gear stage.

Next, an eleventh embodiment of the device of the present invention will be explained with reference to FIG. 11. In this embodiment, similar to the second embodiment, in the first embodiment, the third planetary gear set X3 and the output shaft are connected to each other. 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 first ring gear RG4, and when the second brake B2 is operated,
Similarly to the 11th J gear RG1, the 4th sun gear S
4 is fixed.

A fourth brake B4 is provided between the fourth ring gear RG4 and the case, and when the brake is operated, the fourth
Ring gear RG4 can be tightened.

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

Here, to give an example of the numerical value of a specific gear position of the transmission according to the present invention, l4=0.437, each clutch and each brake actuation at each gear position of the transmission according to the present invention, and deceleration at each gear position. The relationship between the ratios is summarized as shown in Table 11A.

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

Next, a twelfth embodiment of the apparatus of the present invention will be explained with reference to FIG. 12. In this embodiment, similar to the second embodiment, in the first embodiment, the third planetary gear set It has a configuration in which a single pinion type fourth planetary cartridge X4 is interposed between it and the output shaft, and the connection relationship with each element is as follows.

The fourth ring gear RG4 is drivingly connected to the second gear C2, and when the third brake B3 is operated,
Similarly to the second carrier C2, the fourth ring gear RG4
is fixed.

A fourth brake B4 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 dynamically and integrally connected to the output shaft.

Here, to give an example of the numerical value of the specific gear position of the transmission according to the present invention, l4=0.562, each clutch and each brake actuation at each gear position of the transmission according to the present invention, and the deceleration at each gear position. The relationship between the ratios is summarized as shown in Table 12A.

Table 12B summarizes the rotational speed and tangential force of each element of each planetary gear set at each gear stage.

Next, a thirteenth embodiment of the device of the present invention will be explained with reference to FIG. 13. 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 ring gear RG4 is drivingly connected to the first ring gear G1, and when the second brake B2 is operated, the fourth ring gear RG4 is locked in the same way as the first IJ gear RG1.

A fourth brake B4 is provided between the fourth sun gear S4 and the case, and when the brake is activated, the fourth sun gear S4 can be fixed.

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

Here, to give an example of a specific gear position value of the transmission according to the present invention, l4 = 0.320, each clutch and each brake operation at each gear position of the transmission according to the present invention, and deceleration at each gear position. Table 13A summarizes the ratio relationships.

Table 13B summarizes the rotational speed and tangential force of each element of each planetary gear set at each gear stage.

Next, a fourteenth embodiment of the device of the present invention will be explained with reference to FIG. 14. In this embodiment, similar to the second embodiment, in the first embodiment, the third planetary gear set hX3 and the output shaft It has a configuration in which a single pinion type fourth planetary cartridge 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 R, G.
3 in a one-drive manner.

A fourth brake B4 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 dynamically and integrally connected to the output shaft.

Here, to give an example of a specific gear position value of the transmission according to the present invention, l4=0.280, each clutch and each brake actuation at each gear position of the transmission apparatus according to the present invention, and the deceleration at each gear position. The ratios are summarized as shown in Table 14A.

Table 14B summarizes the rotational speed and tangential force of each element of each planetary gear set at each gear stage.

Next, a fifteenth embodiment of the device of the present invention will be explained with reference to FIG. 15. In this embodiment, similar to the second embodiment, in the first embodiment, the third planetary gear set X3 and the output shaft are connected to each other. A single pinion type fourth planetary gear set X4 is interposed between them, and the connection relationship with each element is as follows.

The fourth sun gear S4 is drivingly connected to the third ring gear RC3.

A fourth brake B4 is provided between the fourth ring gear RG4 and the case, and when the brake is activated, the fourth ring gear RG4 can be fixed.

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

Here, to give an example of a specific gear position value of the transmission according to the present invention, l4=0.280, each clutch and each brake operation at each gear position of the transmission apparatus according to the present invention, and the shift at each gear position. The ratios are summarized as shown in Table 15A.

Table 15B 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 the present invention achieves at least 4 forward speeds and 1 reverse speed, which is excellent in practical use.
It is possible to obtain multiple gears, which has great industrial effects.

[Brief explanation of drawings]

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 diagram in central longitudinal section showing a ninth embodiment of the transmission of the present invention, and FIG. FIG. 11 is a diagrammatically illustrated central vertical cross-sectional schematic view of an eleventh embodiment of the transmission of the present invention; FIG. FIG. 13 is a schematic center longitudinal cross-sectional view diagrammatically showing a thirteenth embodiment of the transmission of the present invention;
FIG. 14 is a schematic central longitudinal cross-sectional view diagrammatically showing a fourteenth embodiment of the transmission of the present invention, and FIG. 15 is a schematic central longitudinal cross-sectional diagram diagrammatically showing the fifteenth embodiment of the transmission of the present invention. It is a diagram. Xl: 1st planetary gear set, X2: 2nd planetary gear set, X3: 3rd planetary gear set, X4
: 4th plane 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: Fourth planetary gear, P5: Fifth planetary gear, RGl: 1st
Ring gear, RG2: 2nd ring gear, RG3: 3rd
Ring gear, RG4: 4th ring gear, C1: 1st gear rear, C2: 2nd gear rear, C3: 3rd gear rear, C
4: 4th gear rear, CLl: 1st clutch, CL2:
Second clutch, R1: first brake, B2: second brake, B3: third brake, B4: fourth brake.

Claims (1)

[Scope of 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 meshes meshing motion between the two gears, and a case that is a fixed member. The sun gears of a first planetary gear set of double pinion type, a second planetary gear set of single pinion type, and a third planetary gear set of single pinion type are drivingly connected, and both of the first and second planetary gear sets are connected in a driving manner. The carrier is drivingly connected, and the ring gear of the second planetary gear set and the gear of the third planetary gear set are drivingly connected to the output shaft, and the ring gear of the third planetary gear set is coupled or disengaged from the input shaft. The first clutch that causes
A second gear that connects or releases the connected sun gears of the first to third planetary gear sets to or from the input shaft.
a clutch, a first brake capable of securing the connected sun gears of the first to third planetary gear sets to the case, a second flake capable of securing the ring gear of the first planetary gear set to the case, and the first and third planetary gear sets. A transmission comprising a third brake capable of fixing a second plane gear set in which both carriers are connected to a case. 2. In the first invention described in the claims, one or 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 carriers of the first and second planetary gear sets are connected together, and the ring gear of the first planetary gear set and the ring gear of the third planetary gear set are drivingly connected to one of the three carriers. The transmission is further provided with a fourth brake capable of fixing the remaining members of the sun gear, ring gear, and carrier of the fourth planetary gear set to the case.