JPS5845615B2 - transmission - Google Patents

Description

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

It is desirable for a transmission device for a large vehicle such as a truck or bus to have at least four or more gear stages.

For this reason, a single pinion planetary gear set is used.
It is conceivable to realize four or more gear stages by combining a set or four or more sets and linking 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) The number of teeth of each gear in each planetary gear set must satisfy the meshing conditions, and the sun gear and planetary gear with the minimum diameter must also have the required number of teeth or more.

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

(4) 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 two sets as brake devices, and each planetary gear 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 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.

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. 2nd planetary gear set X2,
A third planetary gear set X3 is present.

The first planetary gear set) Xl is the first sun gear S1
A first planetary gear P1 that meshes with the first sun gear, a first ring gear RG1 that meshes with the first planetary gear, and a first carrier that pivotally supports the first planetary gear P1.

Said second planetary gear set) X2 is the second sun gear S2
and a second planetary gear P2 that meshes with the second sun gear, 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.
and has.

Similarly, the third planetary gear set (X3) is the third sun gear S3 and the 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 input shaft and the first carrier C1 are dynamically coupled together.

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

The second carrier C2 and the third carrier C3 are drivingly connected.

The second sun gear S2 and the third ring gear RG3 are drivingly connected.

The third carrier C3 and the output shaft are dynamically connected together.

A first clutch CL1 is disposed between the input shaft and the 1.3 sun gears S1 and S3, and the first clutch CL1 integrally connects and disconnects the input shaft and the 1.3 sun gears S1 and S3. ing.

The 11th ring gear RG1 and the second ring gear RG
A second clutch CL2 is disposed between the first ring gear RG1 and the second ring gear RG2 for integrally engaging and disengaging the first ring gear RG1 and the second ring gear RG2.

A third clutch CL is provided between the first carrier C1 and the second ring gear RG2 to integrally connect or disconnect the first carrier C1 and the second ring gear RG2.
3 are arranged.

CL4 is a fourth clutch connected in parallel with the first clutch CL1, and is connected to the input shaft and the 1.3 sun gear S1,
83, only when the relative rotation is in one direction, the input shaft and the first
．． 3 sun gear S1. This is a one-way clutch that connects or releases S3.

A first brake B1 is provided between the second ring gear RG2 and the case, so that when the brake is actuated, the second ring gear RG2 can be fixed.

A second brake B2 is provided between the second sun gear S2, the third ring gear RG3, and the case, so that when the brake is activated, the second sun gear S2 and the third ring gear RG3 can be fixed. It has become.

The following equation (the same applies to all embodiments to be described later) holds true for each planetary gear set Xi, X2°X3.

However, NRGl, NRG2, NRG3...first, second
, the rotational speed of the third ring gear NC1, NC2, NC3...first, second, third
Carrier rotational speeds NS1, NS2, NS3...Rotational speeds of the 1st, 2nd, and 3rd sun gear ■1, ■2, ■3......Radius ratio of each ring gear and each sun gear shall be.

Here, to give an example of specific numerical values of each gear stage of the transmission according to the present invention, 11=0.406.12=0.531.1
3=0.391 (the same applies to all embodiments described below), and each clutch CLI, CL2, CL3 at each gear stage of the transmission of the present invention.

Table 1 summarizes the relationship between the operation of CL4 and brakes B1 and B2 and the reduction ratio of each gear stage.

However, Fn (n-1, 2, 3, . . . ) indicates a forward gear stage; for example, Fl indicates first forward gear, F2 indicates second forward gear, and R indicates reverse gear.

Next, a second embodiment of the device of the present invention will be explained with reference to FIG.
In the embodiment shown in FIG. 1, a single pinion type fourth planetary gear set X4 is interposed between the third planetary gear set X3 and the output shaft, and the connection relationship with each element is as follows. It is.

Said fourth planetary gear set) X4 is the fourth sun gear S4
and 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 P4.
and has.

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 to be able to secure the carrier.

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

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

However, NRG4: rotational speed of the fourth ring gear NC4; rotational speed of the fourth carrier NS4; rotational speed of the fourth ring gear ■4: radius ratio of the fourth ring gear and the fourth sun gear.

Here, a specific numerical value of each gear stage of the transmission according to the present invention is 14=0.5, and each clutch CL 1 at each gear stage of the transmission according to the present invention.

CL2, CL3, CL4 and each brake Bl, B2
The relationship between the operation of B3 and the reduction ratio of each gear stage is summarized in Table 2.

Next, a third embodiment of the device of the present invention will be explained with reference to FIG.
Similar to the second embodiment shown in FIG. 2, this embodiment has a single pinion type fourth planetary gear set X4 between the third planetary gear set X3 and the output shaft in the first embodiment shown in FIG. It is a configuration that consists of intervening, and each element,
Which connection relationships are 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 dynamically and integrally connected to the output shaft.

Here, 14=0.548 is given as an example of the numerical value of the specific gear position of the transmission according to the present invention, and the operation of each clutch and each brake at each gear position of the transmission apparatus of the present invention and the deceleration of each gear position are as follows. Table 3 summarizes the relationship between the ratios.

As is clear from the above description, according to the present invention, the initial objective can be basically achieved using three sets of planetary gear sets, and as shown below, (1) frictional engagement means is provided between the two planetary gear sets. Since it is interposed in the gear set, it can be placed at any position around the target planetary gear set while maintaining its connection relationship, providing a great degree of freedom in placement.

(2) Since the reverse brake, which requires a large torque transmission capacity, is not used during forward movement, it is advantageous to use automatic gear shift shock control.

(3) In addition, when the friction engagement means and the one-way clutch are used together, the torque transmission can be shared between both clutches.
It also has the advantage that the torque transmission capacity of the friction plates can be reduced and the number of friction plates can be reduced, and it is possible to obtain a gear stage of at least 4 forward gears and 1 reverse gear which is excellent in practical use. 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 schematic central vertical sectional view diagrammatically showing a third embodiment of the transmission of the present invention. Xl...1st planetary gear set, X2...
...Second planetary gear set, X3...
Third planetary gear set, Sl...Second sun gear, B2...Second sun gear, B3...
・Third sun gear, Pl...First planetary gear, Pl...Second planetary gear, P3...
...Third planetary gear, RGl...First ring gear, RG2...Second ring gear, RG3...
...3rd ring gear, C1...1st carrier, C2...2nd carrier, C3...
...Third carrier, CLl...First clutch,
CL2...Second clutch, CL3...
3rd clutch, CL4...4th clutch, B1
...First flake, B2...Second 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. The carrier of the first planetary gear set is drivingly connected to the input shaft, the sun gear of the second planetary gear set and the ring gear of the third planetary gear set are drivingly connected, and both the sun gears of the first and third planetary gear sets are connected in a driving manner. drivingly coupled to the second
and the carriers of the third planetary gear set are drivingly connected to the output shaft, one clutch for coupling or disengaging both sun gears of the first and third planetary gear sets with respect to the input shaft, a ring gear of the first planetary gear set, and a ring gear of the first planetary gear set. Another clutch that connects or disengages the ring gear of the second planetary gear set, another clutch that connects or disengages the ring gear of the second planetary gear set with respect to the input shaft, and a first clutch that connects or disengages the ring gear of the second planetary gear set to the case. A transmission device comprising: a brake; and a second brake capable of securing a sun gear of a second planetary gear set and a ring gear of a third planetary gear set to a case. 2 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 connects the two gears, and a case that is a fixed member, and a first planetary gear set. a carrier is drivingly connected to the input shaft, a sun gear of the second planetary gear set and a ring gear of the third planetary gear set are drivingly connected, and both sun gears of the first and third planetary gear sets are drivingly connected, Second
and the carriers of the third planetary gear set are drivingly connected to the output shaft, one clutch for coupling or disengaging both sun gears of the first and third planetary gear sets with respect to the input shaft, a ring gear of the first planetary gear set, and a ring gear of the first planetary gear set. Another clutch that connects or disengages the ring gear of the second planetary gear set, another clutch that connects or disengages the ring gear of the second planetary gear set with respect to the input shaft, and a first clutch that connects or disengages the ring gear of the second planetary gear set to the case. A brake, and a second brake capable of fixing the sun gear of the second planetary gear set and the ring gear of the third planetary gear set to the case, and any two of the sun gear, ring gear, and carrier of the fourth planetary gear set. One is drivingly connected to the output shaft, the other is drivingly connected to the sun gear of the second planetary gear set and the ring gear of the third planetary gear set, and one of the sun gear, ring gear, and carrier of the fourth planetary gear set. A transmission comprising a third brake capable of securing the remaining members to the case.