JPS594574B2 - Douriyokuden Tatsuyou Hensokusouchi - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a power transmission transmission comprising a fluid transmission and a hydraulically controlled transmission.

A conventional power transmission device of this kind, for example, one with six forward speeds and one reverse speed, which is often used as a transmission for construction machinery, has a 7-way gear train as shown in Figure 1, and a four-row planetary gear train a +
b * C + d and 7 clutches L, Hs2nd
+R, 1st, +3rdsD, and requires a planetary gear train and clutch depending on the speed stage, and the combination of each clutch provides 6 forward speeds and 1 reverse speed, such as forward speed as shown in Fig. 2. 1st stage f□, 2nd stage f
2. It was possible to obtain the traction force of the 3rd stage f3, the 4th stage f4, the 5th stage f5, and the 6th stage f6, but as mentioned above, in this conventional example, the planetary gear train and the clutch speed stage Even if the transmission had six forward speeds and one reverse speed, it would be large and have a complicated configuration, making it expensive.Also, it would require shifting depending on the work conditions, making it difficult to operate the gears. There was a problem that it was troublesome.

The present invention was developed in consideration of the above-mentioned problems, and it is possible to obtain a wide range of traction force with one speed stage, reduce the number of speed stages, and simplify the gear shifting operation, and the overall structure is compact and lightweight. The present invention aims to provide a transmission for power transmission.

The configuration of the present invention will be explained below based on the embodiment shown in FIG.

In the figure, 1 is a fluid transmission connected to the engine 2, 3 is its pump, 4 is a turbine, 5 is a stator divided into two, a first stator 5a and a second stator 5b, and the pump 3 is connected to the engine 2. The turbine 4 is connected to an input shaft 6 , and the first stator 5 a of the stators 5 has a sleeve 8 fitted to the shaft 7 .
The second stator 5b is fixed to the machine frame side via the freewheel 9b.

On the other hand, 10 is a hydraulically controlled transmission, and this transmission 10 is equipped with two double-pinion planetary gear trains 11 and 12, one of which is planetary gear train 1.
1 is for reverse movement, and the externally powered planetary gear train 12 is for forward movement.

The sun gear 13 of the planetary gear train 11 for reverse movement is connected to the shaft 7 connected to the turbine 4, and the sun gear 13 is connected to the internal gear 16 via the first planetary gear 14 and the second planetary gear 15.
and the sun gear 1γ of the planetary gear train 12 for forward movement.
is connected to the sleeve 8 and meshes with the internal gear 24 via the sun gear 17, second planetary gear 18, and second planetary gear 19.

And the first planetary gear 14 of the planetary gear train 11 for reverse movement.
The second planetary gear 19 of the planetary gear train 12 for forward movement is an integral long pinion, and the carrier 2 is attached to its axis.
0 is inserted through it as a supporting shaft.

The second planetary gear 15 of the reverse planetary gear train 11 and the first planetary gear 18 of the forward planetary gear train 12 are supported by the same carrier 21, and both carriers 20 and 21 are integrally connected to the output shaft 22. is combined with

The sleeve 8 is connected to the machine frame side via a clutch 23, and is also connected to the internal gear 1 of the forward planetary gear train 11, 12 at the rear.
6.24 is connected to the machine frame side via clutches 25.26.

Further, the input shaft 6 extends through the shaft 7 to the output shaft 22 side, and a clutch 27 is provided between the input shaft 6 and the carrier 20.21.

In the power transmission device having the above configuration, first, in the case of the first forward speed, the clutch 26 is engaged.

In this way, the flow of power transmission becomes as shown by the sun in FIG. 4, and power is transmitted to the turbine 4 and first stator 5a of the fluid transmission 1 via the long pinion.

The reduction ratio ρF at this time is both long gear gears 14 and 19.
If the number of teeth dl and d2 are the same a2+b1 -, then the value is ρF1□ (Also, O2 of about 25 to 3.5 is easy to manipulate.

In addition, a2 is the number of teeth of the sun gear 13, and bl is the internal gear 1.
Indicates the number of teeth of 6.

The rotation freeze field of the first stator 5a in this case of forward movement, hq
During low speed ratios, the stator reversal torque is added to the output carrier to obtain a high torque ratio.

When the speed ratio becomes high, the stator torque is reversed and the freewheel 9 causes the stator to idle.

Note that al here indicates the number of teeth of the sun gear 17 of the forward gear train 12.

In the case of the second forward speed, the clutch 23 is engaged.

In this way, the power transmission flow becomes as shown by the thick line in FIG. Ru.

At this time, the reduction ratio ρR is ρRa when ci1=d2.
1+a2 2□, and this value is approximately 1.5 (ρR2 <2.0).

In this case, the first stator 5a is also fixed, exhibiting the performance of a normal torque converter, and idling in the high speed ratio region in the same way as when moving forward.

In the case of the third forward speed, the clutch 27 is engaged.

In this way, the input shaft 6 and the output shaft 22 are directly connected, and the engine output is directly transmitted to the output shaft 22.

At this time, the reduction ratio ρF3 becomes 1.0, and the first and second stators 5a and 5b idle, reducing the fluid resistance within the fluid transmission 1.

Therefore, the reduction ratio ρF1 at 1st forward speed is 3.0, the reduction ratio ρF3 at 3rd forward speed is 1.0, and the stall torque ratio is 7.
．． If it is around 0, the overall torque amplification ratio is about 20.
0, and the running performance in that case is shown in FIG. 7.

In FIG. 7, fl, f2. f3. f4. f5. f6
indicates the forward performance of each speed stage of the conventional 6-speed forward type, and F
1 s F 2 represents the forward performance of each speed stage of the three forward stage type transmission device according to the present invention.

As is clear from this Fig. 7, forward 1st speed, 2nd speed,
3rd speed F1sF21F3, conventional forward 1st to 6th speeds f1 to f
6 performance can be obtained.

When moving in reverse, clutch 25 is engaged.

In this way, the power flow becomes as shown in FIG. 8, and the torque of the first stator 5a is transmitted to the output shaft 22 in the same way as in the first forward speed, resulting in a high torque ratio.

The reduction ratio at this time is ρR Therefore, it is approximately 1.5 to 2.5.

Since the present invention is configured as described above, it is possible to obtain a wide range of traction force with one speed stage, reduce the number of speed stages, and simplify the speed change operation.

In addition, with a configuration consisting of only two planetary gear trains and four clutches, it is possible to obtain the same performance as a conventional one consisting of a four-row planetary gear train and seven clutches, and the overall structure is lightweight due to its combination. be able to.

Furthermore, since only one clutch operates in the first speed stage, hydraulic control to the clutch is easy and reliable, and since there is only one idling clutch, there is no drive torque loss.

[Brief explanation of drawings]

Figure 1 is a configuration explanatory diagram showing an example of a conventional transmission;
Figure 3 is a diagram showing the traction force, Figure 3 is a configuration explanatory diagram showing an embodiment of the transmission device according to the present invention, Figures 4 to 6 are power transmission state diagrams during forward movement, and Figure 7 is the traction force. The diagram and FIG. 8 are power transmission state diagrams during reverse movement. 1 is a fluid speed changer, 4 is a turbine, 5 is a stator, 9 is a freewheel, 11.12 is a planetary gear train, 13.17 is a sun gear, 14.18 is a first planetary gear, 15.19 is a second planetary gear Planetary gear, 16.24 is internal gear, 23.25.26.
27 is the clutch.

Claims (1)

[Claims] 1 Sun gear 13, first planetary gear 14, second planetary gear 1
5 and clutch 25 to engage and disengage the internal gear 1 from the machine frame side.
6, a sun gear 17 that can be freely engaged and disengaged from the machine frame side by a clutch 23, and supported on the same carrier 21 as the second planetary gear 15 of the first planetary gear 11. a second planetary gear 19 that forms a long pinion integral with the first planetary gear 14 of the first planetary gear train 11, and an internal gear that is engaged and disengaged from the machine frame side by a clutch 26. A first planetary gear train 1 consisting of 24
2, each carrier 20.21
is connected to the output shaft 22, the sun gear 13 of the first planetary gear train 11 is connected to the turbine 4 of the fluid transmission 1, and the round gear 17 of the second planetary gear train 12 is connected to the freewheel 9a'.
A power transmission transmission characterized in that the input shaft 6 and the output shaft 22 are connected to the stator 5 via a=a and are configured to be able to be engaged and disengaged by a clutch 27.