JPS5845616B2 - 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 vehicles, particularly automobiles.

As a transmission device for a large vehicle such as a truck or a bus, it is conceivable to realize at least four or more gear stages.

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 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 consideration, the present invention basically uses three sets of single pinion simple planetary gear sets, basically two clutch devices and three 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.

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, a second planetary gear set X2,
A third planetary gear set X3 is present.

The first planetary gear set X1 is a first sun gear S1.
and a first planetary gear P1 that meshes with the first sun gear, a first ring gear RGI that meshes with the first planetary gear, and a first carrier C1 that pivotally supports the first planetary gear P1.
and has.

Said second planetary gear set) X2 is the second sun gear R2
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 includes a third sun gear S3, a third ring gear RG3 that meshes with the third planetary gear that meshes with the third sun gear, and a third carrier C3 that pivotally supports the 37th planetary gear P3.

The input shaft and the third sun gear S3 are dynamically connected together.

The first carrier C1 and the third carrier C3 are drivingly connected.

The first sun gear S1 and the second sun gear S2 are drivingly connected.

The second ring gear RG2 and the third ring gear RG3
is 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 first ring gear RG1 for integrally connecting and disconnecting the input shaft and the first ring gear RG1.

The 1.2 sun gears SL, S2 and the 2.3 ring gear RG2. Between the RG3 and the 1.2 sun gear S
1. A second clutch CL that integrally connects and disconnects S2 and the second and third ring gears RG2 and RG3.
2 are arranged.

CL3 is a third clutch connected in parallel with the second clutch CL2, and is connected to the first and second sun gears S1. Only when the relative rotation between S2 and the 2.3rd ring gear RG2°RG3 is in one direction, the 1.2nd sun gear Sl, S2 and the 2.3rd ring gear RG2. This is a one-way clutch that connects or releases RG3.

A first brake B1 is provided between the first ring gear RG1 and the case, and is configured to clamp the first ring gear RG1 when the brake is activated.

A second brake B2 is provided between the 1.2 sun gears S1, 82 and the case, and is configured to lock the 1.2 sun gears 81, S2 when the brake is activated.

A third brake B3 is provided between the second carrier C2 and the case, and when the third brake B3 is operated, the second
It is designed so that the carrier C2 can be secured.

And each planetary gear set X1. X2.

In X3, the following equation (same in all embodiments described below) holds true.

However, NRG, , NRG2, NRG3... 1st, 2nd
, rotation speed of the third ring gear, NC1, NC2, NC3・
...Rotation speed of the first, second and third carriers, NS,
, NS2, NS3... The rotational speed of the first, second, third sun gear, 11, I2, I3... The radius ratio of each ring gear and each sun gear.

Here, to give an example of specific numerical values for each gear stage of the transmission according to the present invention, 11=0.531. I2-0.516
．． 13=0.406 (The same applies to all the examples described below.

), and each clutch CLI, CL2 at each gear stage of the transmission of the present invention.

CL3 and brakes B1, B2. Table 1 summarizes the operation of B3 and the reduction ratio of each gear stage.

However, Fn (n=1.2.3...) indicates the forward gear stage, for example, Fl indicates the first forward gear, F2 indicates the 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 like that.

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 drivingly connected to the second carrier 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 carrier C4 and the case, and when the brake is operated, the fourth brake B4
It is designed so that the carrier C4 can be secured.

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, NRG 4...Rotation speed of the 4th ring gear NC4
...4th carrier rotation speed NS4 ...
・Rotational speed I4 of the fourth sun gear is the radius ratio of the fourth ring gear and the fourth sun gear.

Here, to give an example of specific numerical values for each gear of the transmission according to the present invention, L4=0.5, and each clutch CLI, CL2, C at each gear of the transmission of the present invention.
L3 and each brake Bl.

B2. B3. Table 2 summarizes the relationship between the operation of B4 and the reduction ratio of each gear stage.

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. 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 like 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, 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 following explanation, according to the present invention, basically three
If the initial objective can be achieved using two planetary gear sets, and as shown below (1) the frictional engagement means is interposed between both planetary gear sets, so if the connection relationship is maintained, then the object is achieved. It can be placed at any position around the planetary gear set, and has a high degree of freedom in placement.

(2) Since the reverse brake, which requires a large torque transmission capacity, is not used when moving forward, automatic gear shift shock control is advantageous.

(3) Furthermore, when a friction engagement means and a one-way clutch are used together, torque transmission can be shared between both clutches,
The torque transmission capacity of the friction plates can be reduced, and the number of friction plates can be reduced.

At least 4 advances which have advantages such as
It is possible to obtain a gear stage of 1 reverse gear and 1 reverse gear, which 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, Xl...
...Second planetary gear set, X3...
3rd planetary gear set, SL...1st sun gear, B2...2nd sun gear, B3...
・Third sun gear, Pl...First planetary gear, Pl...Planetary gear, P3...
Third planetary gear, RGI...first ring gear, RG2...second ring gear, RG31.・
...Third ring gear, C1...First carrier, C2...Second carrier, C3...Third carrier, CLl...First clutch, CL2・・・
...Second clutch, CL3...Third clutch, B1...First brake, B2...
2nd brake, B3...Third brake.

Claims (1)

[Scope of Claims] 1. A case in which a human power shaft, an output shaft, and a fixed member are several sets of planetary gears, each of which is connected to a carrier that pivotally supports a sun gear, a ring gear, and a planetary gear forming a meshing interlock between the two gears. The sun gears of the first and second planetary gear sets are drivingly connected, the ring gears of the second and third planetary gear sets are drivingly connected, and the sun gear of the third planetary gear set is drivingly connected to the input shaft. both carriers of the first and third planetary gear sets are drivingly connected to the output shaft;
One clutch connects or releases the ring gear of the first planetary gear set from the input shaft, one clutch connects both the sun gears of the first and second planetary gear sets, and one clutch connects the ring gears of the second and third planetary gear sets. Another clutch that connects or disengages the gear, a first brake that can lock the ring gear of the first planetary gear set to the case, and a brake that connects the sun gear of the first and second planetary gear sets to the case. A transmission device comprising: a second brake capable of being secured to a case; and a third brake capable of securing a carrier of a second planetary gear set to a case. 2. 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 continues meshing and interlocking between the two gears, a case that is a fixed member, and Both sun gears of the two planetary gear sets are drivingly connected, both ring gears of the second and third planetary gear sets are drivingly connected, the sun gear of the third planetary gear set is drivingly connected to the input shaft, and the first and third planetary gear sets are drivingly connected. Both carriers of the third planetary gear set are drivingly connected to the output shaft,
One clutch for connecting or disengaging the ring gear of the first planetary gear set from the input shaft, one in which both the sun gears of the first and second planetary gear sets are connected, and one in which both the ring gears of the second and third planetary gear sets are connected. a first brake capable of securing the ring gear of the first planetary gear set to the case; and a first brake capable of securing the ring gear of the first planetary gear set to the case; and a first brake capable of securing the ring gear of the first planetary gear set to the case; a second brake capable of fixing the carrier of the second planetary gear set to the case, and a third brake capable of fixing the carrier of the second planetary gear set to the case, and either one of the sun gear, ring gear, and carrier of the fourth planetary gear set One shaft is drivingly connected, the other is drivingly connected to the carrier of the second planetary gear set, and the fourth
A transmission comprising a fourth brake capable of fixing the remaining members of the sun gear, ring gear, and carrier of the planetary gear set to the case.